JP6689130B2 - Vibration reduction device - Google Patents

Description

  Embodiments of the present invention relate to a swing reduction technique using a pendulum type magnetic damper.

  A suspended structure such as a ropeway or a structure floating on the water surface such as a ship oscillates or reciprocates in an arc due to factors such as wind and waves. 2. Description of the Related Art Conventionally, various rocking reducing devices have been developed for the purpose of improving the riding comfort of a structure against rocking or protecting the structure from damage due to shock. In recent years, there has been an increasing demand for seismic isolation technology for vertical seismic isolation, that is, vertical seismic isolation. When seismically isolating in the vertical direction, the issue is to reduce rocking called rocking.

  Rocking is a phenomenon in which the center of gravity shifts from the line of action of an external force during pitching, the pitching is absorbed and rolls, and the structure tends to fall. As a technique for preventing rocking, for example, a pendulum type rocking reducing device including a bogie type weight body that reciprocates with wheels on a rail attached to a vehicle body of a ropeway is known. A magnetic damper is provided on a wheel of the swing reducing device.

The magnetic damper is a damper that includes a conductor and a magnet and that damps vibration of a structure by using the principle of eddy current braking.
The eddy current braking is a phenomenon in which the relative displacement is braked by an induced current generated in the conductor when the magnetic flux penetrating the conductor is relatively displaced with respect to the conductor. An apparatus in which a magnetic damper is applied to a reciprocating weight body has a long reciprocating stroke and, in addition, a simple structure does not require frequent maintenance.

It is desired that the swing reducing device be as small and lightweight as possible and have a high damping force against swing.
Further, it is desired that the natural frequency can be easily adjusted in accordance with the natural frequency of the structure whose swing is to be reduced.

  By the way, in order to increase the damping force of the magnetic damper, it is necessary to increase the magnetic flux penetrating the conductor. Conventionally, there is known a technique of changing the magnetic flux density by adjusting the distance between magnets.

JP, 7-222428, A

  However, in the above-mentioned conventional technique, there is a problem that the mass must be increased in order to reduce the natural frequency because the natural vibration frequency adjusting means of the vibration reduction device is scarce.

  When the mass is increased, the volume is usually increased, the swing reducing device becomes large, and it is necessary to relocate or change the design of surrounding members. It is known that when the weight body is configured to be capable of rotating in addition to reciprocating motion, the rotating motion contributes to a reduction in the natural frequency of the device. However, in the conventional technique including the weight body that rotates, the arrangement of the magnets causes the magnetic flux to diverge, and there is a problem that a sufficient damping force cannot be obtained.

  The present invention has been made in consideration of such circumstances, and it is an object of the present invention to provide a swing reducing device capable of generating a high damping force, keeping the entire device compact, and realizing a low natural frequency. To aim.

The swing reducing device according to the present embodiment includes a base member installed on a structure having an arcuate curved surface and swinging so that the convex shape of the curved surface is directed vertically downward, and the above-mentioned curved surface. A rotating plate that constitutes both ends in the direction of the rotation axis of the weight body that rolls along an arc, a conductor plate disposed in a gap between the rotating plates, and a side surface of the rotating plate that faces the conductor plate. A magnet that is arranged to allow magnetic flux to penetrate through the conductor plate .

  According to the present invention, there is provided a swing reducing device capable of generating a high damping force, keeping the entire device compact, and realizing a low natural frequency.

(A) is a diagram when the swing reduction device according to the first embodiment and the structure to be subjected to the swing reduction are horizontal, and (B) is a swing reduction device and the swing reduction according to the first embodiment. The figure when the target structure is tilted. FIG. 3A is a side view of the swing reducing device according to the first embodiment, and FIG. 2B is a cross-sectional view taken along the line I-I shown in FIG. 3A is a schematic perspective view of the weight body according to the first embodiment, and FIG. 3B is an enlarged cross-sectional view of a Ω portion in FIG. FIG. 4A is a side view of a modification of the swing reducing device according to the first embodiment, and FIG. 4B is a cross-sectional view taken along the line II-II shown in FIG. FIG. 7A is a diagram showing a modified example of a structure targeted by the swing reduction device according to the first embodiment when the structure is horizontal, and FIG. 6B is a swing reduction device according to the first embodiment. FIG. 6 is a modified example of the target structure, in which the building is tilted. FIG. 6A is a cross-sectional view taken along the rotation axis direction of the weight body of the swing reducing device according to the second embodiment, and FIG. 6B is a modified example of FIG. 6A in which two flat plates are inserted. Sectional drawing along the rotating shaft direction of a weight body. FIG. 7A is a cross-sectional view taken along the rotation axis direction showing a modified example of the weight body of the swing reducing device according to the second embodiment, and FIG. 7B is the case where the shaft portion 17 is the longest in FIG. 7A. Sectional drawing, (C) is sectional drawing when the extension part of FIG. 7 (B) is fixed by a fixing ring. 8A is a view of the rotary plate of the swing reducing device according to the third embodiment as seen from a shaft portion, FIG. 8B is a cross-sectional view showing a III-III cross section of FIG. 8A, and FIG. Sectional drawing which shows the IV-IV cross section of (B). FIG. 9A is a view of the rotary plate of the swing reducing device according to the fourth embodiment as seen from the shaft portion, in which the magnet is arranged away from the center, and FIG. 9B is centered on the magnet in FIG. 9A. Figure placed close to. FIG. 10A is a view of a rotary plate of a modified example of the swing reducing device according to the fourth embodiment as seen from the shaft portion, in which the magnets are arranged away from the center, and FIG. The figure which arranged the magnet close to the center. The schematic diagram of the rotation board of the rocking reduction device concerning a 5th embodiment. FIG. 12A is a configuration diagram of the diameter changing member of the swing reducing device according to the sixth embodiment before the diameter changing member is attached, and FIG. 12B is a diagram after the diameter changing member is attached in FIG. Diagram. FIG. 13A is a configuration diagram of a modified example of the diameter changing member of the swing reducing device according to the sixth embodiment before the diameter changing member is mounted, and FIG. Configuration diagram after mounting. (A) is a side view of the rocking | fluctuation reduction apparatus concerning 7th Embodiment, (B) is sectional drawing of the VV cross section shown to FIG. 14 (A). (A) is a side view of the rocking | fluctuation reduction apparatus concerning 8th Embodiment, (B) is sectional drawing of the VI-VI cross section shown to FIG. 15 (A). FIG. 16A is a side view of a modification of the swing reducing device according to the eighth embodiment, and FIG. 16B is a cross-sectional view taken along the line VII-VII shown in FIG. FIG. 12A is a schematic perspective view of the swing reducing device according to the ninth embodiment, and FIG. 12B is a cross-sectional view taken along the line VIII-VIII of FIG. (A) is a diagram when the swing reduction device according to the ninth embodiment and the structure to be subjected to the swing reduction are horizontal, and (B) is a swing reduction device and swing reduction according to the ninth embodiment. The figure when the target structure is tilted. FIG. 9A is a diagram showing a modified example of the swing reduction device and the structure according to the ninth embodiment when the structure is horizontal, and FIG. 9B is a swing reduction device and the structure according to the ninth embodiment. FIG. 10 is a diagram showing a modified example of the structure when the structure is tilted. Sectional drawing of a weight in the case of integrally forming a base member.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

(First embodiment)
A swing reduction device 1A according to the first embodiment will be described with reference to FIGS. 1 to 5.
1A and 1B are schematic diagrams showing a swing reduction device 1A according to the first embodiment and a structure 5 to be reduced in swing.

The structure 5 in FIGS. 1A and 1B is, for example, a vehicle body 5 a (5) of a ropeway that is suspended from a fixed point 6 and swings.
FIG. 1B shows a state in which the structure 5 in FIG. 1A is tilted about the fixed point 6.
Further, FIG. 2A is a side view of the swing reduction device 1A according to the first embodiment, and FIG. 2B is a cross-sectional view taken along the line I-I shown in FIG. 2A.

Swing reduction apparatus 1A according to a first embodiment, FIG. 2 (A), the as shown (B), the which has an arcuate rail surface (curved surface) 10 _1, the rail surface 10 to the structure 5 two base member 10A _{which one} convex are juxtaposed directed vertically downward, and the two rotating plates 11 which are mounted on two rail surfaces 10 ₁ rolls on the rail surfaces 10 _1, two rotary a shaft portion 17 which forms a pyramidal 2 by connecting the plate 11 to roll along the arc of the rail surface 10 _1, the conductive plate 7 disposed in a gap between the rotating plate 11, facing the conductive plate 7 And a magnet 3 arranged on a side surface of the rotating plate 11.

As shown in FIGS. 1 (A) and 1 (B), two base members 10A are arranged in parallel in the rotation axis direction of the weight body 2 and fixed to the ceiling portion of the swinging structure 5 or the like. Any of base member 10A also has the convex shape of the rail surface 10 ₁ directed vertically downward, the rail surface 10 ₁ is the rail surface 10 ₁ which roll weight member 2.

The basic body of the weight 2 is composed of two rotary plates 11 in which a center O of the rotary plate 11 is connected by a shaft portion 17. In the first embodiment, the rail surface 10 ₁ supports a rotating plate 11. As the rotating plate 11 rolls on the rail surface 10 ₁ by inertial force and its own weight, the entire weight 2 rolls along the arc of the rail surface 10 ₁ as shown in FIG. 1 (B).

Conductive plate 7, for example, has a curved surface 7a of the small arc-shape slightly with rail surface 10 ₁ and concentric base member 10A, it is placed in the gap between the two basic members 10A. With this installation, when the weight 2 is placed on the base member 10A, part of the conductor plate 7 is placed in the gap between the two rotary plates 11. A magnet 3 such as a neodymium magnet is arranged on the surface of the rotating plate 11 that faces the conductor plate 7 among the side surfaces.

  Here, FIG. 3A is a schematic perspective view of the weight body 2 according to the first embodiment, and FIG. 3B is an enlarged cross-sectional view of the Ω portion of FIG. 3A. In addition, in FIG. 3B, the conductor plate 7 is also included. As shown in FIGS. 3A and 3B, the magnets 3 are arranged in a circle so that the magnetic poles have alternating directions.

  Further, the magnets 3 arranged on the facing surfaces of the two rotary plates 11 are arranged so that the magnets 3 (3a, 3b) having different magnetic poles face each other or intentionally shifted slightly. Since the conductor plate 7 is arranged in the gap between the magnets 3 (3a, 3b) facing each other, the magnetic flux Φ toward the magnets 3 facing each other penetrates the conductor plate 7.

  The outer peripheral portion of the rotary plate 11 is preferably made of a magnetic material such as JIS SS400. Since the magnet 3 is fixed to this magnetic material portion, this magnetic material has the function of the yoke 11a. The magnetic flux Φ diverging from the magnet 3 toward the yoke 11a is converged inside the yoke 11a, diverges from the end of the yoke 11a, and converges at the opposing yoke 11a of the rotary plate 11. That is, by making the yoke 11a a magnetic material, the magnetic flux Φ that originally diffuses and does not penetrate through the conductor plate 7 is captured and penetrated into the conductor plate 7, which can contribute to the generation of an eddy current.

  The magnet 3 to be arranged may be arranged only on one of the facing surfaces. When the magnets 3 are arranged only on one side of the facing surface, the magnetic flux Φ converges on the adjacent magnets 3. If the magnetic flux Φ enters the conductor plate 7, the function of the eddy current brake is exhibited even if the magnetic flux Φ does not penetrate the conductor plate 7.

With the above arrangement, the translational and rotational motion along the rail surface 10 ₁ of the weight element 2, the magnetic flux Φ is displaced relative to the conductive plate 7. Therefore, as a reaction of the movement of the weight 2 with the damping force generated by the generation of the eddy current, the damping force is also generated when the structure 5 swings. Further, the kinetic energy of the weight element 2, the reaction force is generated against the rocking of the weight member 2 and the rail surface 10 ₁ is transmitted to the structure 5 is the frictional force between the structure 5, the reaction force attenuation helpful.

Next, a modified example of the swing reduction device 1A according to the first embodiment will be described with reference to FIGS. 4 (A) and 4 (B).
FIG. 4 (A) is a side view of a variation of the swing reduction device 1A according to the first embodiment, and FIG. 4 (B) is a sectional view taken along line II-II shown in FIG. 4 (A).

Rail surface 10 _1, a material having high hardness such as iron to prevent wear it is desirable to be used. When the rail surface 10 ₁ in contact with the yoke 11a is a magnetic material such as iron, rail surface 10 ₁ is captured flux Φ flowing out of the yoke 11a, miss flux Φ to the rail surface 10 _1.

In other words, in addition to the magnetic flux Φ passing through the conductive plate 7 is reduced, the rail surface 10 ₁ will with sucking the yoke 11a.
Therefore, as shown in FIG. 4 (B), of the rotating plate 11, and the inner peripheral portion protrudes in the rotational axis direction outwardly than in the yoke 11a, are brought into contact with the projecting surface 16 on the rail surface 10 ₁ placed Te, yoke 11a is magnetically in contact with the rail surface 10 ₁ is prevented from escaping into the rail surfaces 10 _1.

Next, with reference to FIGS. 5A and 5B, a modified example of the structure 5 targeted by the swing reduction device 1A according to the first embodiment will be described.
In FIGS. 5A and 5B, the structure 5 is, for example, a building 5b (5). 5A is a diagram when the building 5b is horizontal, and FIG. 5B is a diagram when the building 5b is tilted.

The building 5b is provided with a vertical seismic isolation device 4 between the building 5b and the ground in order to suppress the impact of the earthquake. At the time of such vertical seismic isolation, the aforementioned locking may occur. Therefore, in order to suppress the impact due to rocking and prevent the collision with surrounding equipment, the swing reducing device 1A is also suitably used for such a building 5b.
Moreover, many such ships and trains correspond to such a building 5b. In addition to buildings and structures, it may be used in the case of vertically isolating control panels, works of art, and the like. The oscillation reducing device 1A can be suitably used for any of these.

Next, the natural frequency of the oscillation reducing device 1A will be described.
The following formula (1) is the natural frequency ω ₀ when the weight 2 translates along the rail surface 10 ₁ , and the following formula (2) is the natural vibration when the weight 2 rotates in addition to the translational motion. It is a figure which shows the number (omega) ₀ .

ここで、Ｉは錘体２の回転中心に対する慣性モーメント、ｍは錘体２の質量、ｇは重力加速度、Ｌはレール面１０_１の半径、ｒ_０は軸部１７の半径である。

Here, I is the moment of inertia with respect to the rotation center of the weight member 2, m is the mass of the weight member 2, g is the gravitational acceleration, L is the rail surface 10 ₁ of the radius, r ₀ is the radius of the shaft portion 17.

From equations (1) and (2), it can be seen that the natural frequency ω ₀ can be reduced by the inertia moment I regarding the rotation of the weight body 2. In other words, even the small swing reduction device 1A having a small mass can be used for the structure 5 having a small natural frequency.

As described above, according to the swing reduction device 1A according to the first embodiment, the magnets 3 are opposed to each other with the conductor plate 7 interposed therebetween, so that a high damping force can be generated with a small amount of the magnets 3.
In addition, since the weight 2 makes a rotational movement in addition to the translational movement, it can be applied to the structure 5 having a low natural frequency in the compact swing reduction device 1A.

  Further, compared with the case of only the translational movement, the moving speed of the magnetic flux Φ is increased, and the impact of the external force is also absorbed as the kinetic energy of the rotation movement of the weight body 2, so that a small amount of the magnet 3 A high damping force can be generated at.

  That is, according to the swing reduction device 1A of the first embodiment, it is possible to generate a high damping force and maintain the entire device 2 compact to realize a low natural frequency.

(Second embodiment)
6 (A) and 6 (B) are cross-sectional views taken along the rotational axis direction of the weight body 2 of the swing reduction device 1A according to the second embodiment.

  As shown in FIG. 6, the swing reduction device 1A according to the second embodiment includes a length adjusting mechanism 12 that adjusts the length of the shaft portion 17 in the rotation axis direction.

  The length adjusting mechanism 12 is composed of, for example, a plurality of flat plates 12a inserted into both ends of the shaft portion 17 as shown in FIGS. 6 (A) and 6 (B). The rotary plate 11, the flat plate 12a, and the shaft portion 17 are integrally fixed by a bolt 12b from the rotary plate 11 toward the center O of the shaft portion 17. By changing the number of inserted flat plates 12a, the distance between the facing magnets 3 can be easily changed.

  7 (A), (B), and (C) are cross-sectional views along a rotation axis direction showing a modified example of the weight body 2 of the swing reducing device 1A according to the second embodiment. 7A is a diagram when the shaft portion 17 is shortest, FIG. 7B is a diagram when the shaft core 12g is slid to maximize the shaft portion 17, and FIG. 7C is FIG. It is a figure when the extension part of B) is fixed by the fixing ring 12f.

  As shown in FIGS. 7A and 7B, the length adjusting mechanism 12 includes a shaft core 12g inside the shaft portion 17, a slide handle 12d for sliding the shaft core 12g in the rotation axis direction, and a slide handle. It may be constituted by an elongated hole 12c for sliding 12d.

  By the way, the movement period of the weight body 2 strongly depends on the magnitude of the magnetic flux Φ penetrating the conductor plate 7. Therefore, the distance between the magnets 3, that is, the distance between the rotating plates 11 must be adjusted with strictness, and it is necessary to prevent the length of the shaft portion 17 from changing due to an impact during rolling. is there.

Therefore, it is preferable to provide a stopper groove in the elongated hole 12c to adjust the shaft portion 17 after adjusting it to an appropriate length, and then to fix the shaft portion 17 with a fixing means such as a fixing rod 12e.
Further, in order to fix it to a more strict length, as shown in FIG. 7 (C), a fixing ring 12f may be fitted into the extension portion of the shaft core 12g.

  Note that the second embodiment has the same structure as the first embodiment except that the length of the shaft portion 17 in the rotation axis direction is adjusted, and thus duplicated description will be omitted. Also in the drawings, portions having the same configuration or function are denoted by the same reference numerals, and overlapping description will be omitted.

  As described above, according to the swing reducing device 1A of the second embodiment, in addition to the effects of the first embodiment, the distance between the facing magnets 3 can be easily adjusted. The natural vibration of can be easily adjusted to the optimum value.

(Third Embodiment)
8 (A), (B), and (C) are schematic configuration diagrams of the swing reduction device 1A according to the third embodiment. FIG. 8A is a view of the rotary plate 11 of the swing reducing device 1A according to the third embodiment as seen from the shaft portion 17, and FIG. 8B is a cross-sectional view showing a III-III cross section of FIG. 8A. 8C is a cross-sectional view showing the IV-IV cross section of FIG. 8B.

  As shown in FIGS. 8A, 8B, and 8C, a swing reduction device 1A according to the third embodiment is a magnet fixing plate that fixes the magnet 3 and is detachably provided on the rotating plate 11. 18 is provided.

  As described above, the amount of the magnetic flux Φ penetrating the conductor plate 7 affects the damping force of oscillation. Therefore, in the third embodiment, as shown in FIGS. 8A and 8C, the amount of the magnetic flux Φ is changed by changing the number of the magnets 3 mounted on the rotating plate 11.

  For example, by fixing the magnet fixing plate 18 with the bolts 18a, the magnet fixing plate 18 can be appropriately attached and detached. A plurality of magnets 3 may be arranged on one magnet fixing plate 18 as shown in FIGS. 8A and 8C, or may be arranged one by one. A variety of well-known techniques can be used for attaching / detaching the magnet 3, and the attaching / detaching means is not limited to the above example.

  The number of magnets 3 can be changed independently of the adjustment of the length of the shaft portion 17 shown in the third embodiment. Therefore, when the change of the damping force is not sufficient only by adjusting the distance between the magnets 3 by changing the length of the shaft portion 17, the number of the magnets 3 is also changed to adjust the optimum damping force. be able to.

  The third embodiment has the same structure as that of the first embodiment except that the magnet 3 is detachable, and thus the duplicate description will be omitted. Also in the drawings, portions having the same configuration or function are denoted by the same reference numerals, and overlapping description will be omitted.

  As described above, according to the swing reducing device 1A of the third embodiment, in addition to the effects of the first embodiment, the damping force can be adjusted without changing the distance between the facing magnets 3. That is, the damping force can be adjusted without rearranging the peripheral members or changing the design due to the change in the dimension of the weight body 2.

(Fourth Embodiment)
9A and 9B are schematic configuration diagrams of the weight body 2 of the swing reduction device 1A according to the fourth embodiment. 9 (A) and 9 (B) are views of the rotary plate 11 seen from the shaft portion 17, FIG. 9 (A) is a view in which the magnet 3 is arranged away from the center O, and FIG. 9 (B) is a magnet. 3 is a diagram in which 3 is arranged close to the center O. FIG.

  As shown in FIG. 9, the swing reducing device 1A according to the fourth embodiment includes a position adjusting mechanism 13 that fixes the magnet 3 so as to be movable in the radial direction of the rotary plate 11.

  The amount of eddy current generated in the conductor plate 7 is proportional to the moving speed of the magnetic flux Φ in the conductor plate 7. Therefore, in the fourth embodiment, the rotation radius of the magnet 3 on the rotating plate 11 is changed to adjust the moving speed of the magnetic flux Φ with respect to the moving speed of the weight body 2.

  For example, as shown in FIG. 9, the magnet fixing plate 13a having the magnet 3 fitted therein is fitted into the groove portion 13b having the same width as the magnet fixing plate 13a and extending in the radial direction. The magnet 3 can be moved along the groove 13b together with the magnet fixing plate 13a by loosening the fastening of the bolt 13d of the retaining plate 13c that bridges the groove 13b. Since the magnet fixing plate 13a is moved along the groove 13b, only the radial position can be changed without the magnet fixing plate 13a tilting or shifting in the circumferential direction.

10 (A) and 10 (B) are diagrams showing a modification of the swing reduction device 1A according to the fourth embodiment.
10A and 10B are views of the rotary plate 11 viewed from the shaft portion 17 as in FIGS. 9A and 9B. FIG. 10A shows the magnet 3 arranged away from the center O, and FIG. 10B shows the magnet 3 arranged close to the center O.

  As shown in FIGS. 10A and 10B, the position adjusting mechanism 13 may be a rail 13e with a stopper or the like instead of the groove 13b. The rail 13e with a stopper has a ladder shape, and the magnet fixing plate 13a can be slid stepwise and fixed. Note that various other well-known techniques can be used for the position adjusting mechanism 13, and the position adjusting mechanism 13 is not limited to the above example.

  The fourth embodiment has the same structure as that of the first embodiment except that the magnet 3 is movable in the radial direction of the rotary plate 11, and thus duplicated description will be omitted. Also in the drawings, portions having the same configuration or function are denoted by the same reference numerals, and overlapping description will be omitted.

  As described above, according to the swing reduction device 1A of the fourth embodiment, by adjusting the moving speed of the magnetic flux Φ by changing the radius of gyration of the magnet 3, in addition to the effects of the first embodiment, The swing damping force can be changed without changing the dimension of 2.

(Fifth Embodiment)
FIG. 11 is a schematic diagram of the rotary plate 11 of the swing reduction device 1A according to the fifth embodiment.

  As shown in FIG. 11, in the swing reducing device 1A according to the fifth embodiment, the rotating plate 11 is provided with a thinned portion 19 having a thickness smaller than that of the outermost peripheral portion. Here, the "thinning portion 19" also includes a cavity formed by boring the rotary plate 11 in the rotation axis direction. Hereinafter, it is assumed that the thinned portion 19 has a hollow hole.

Hereinafter, the moment of inertia of the weight 2 will be described using the rotary plate 11 in which the inner circular portion 21 and the outer circumferential circular portion 22 of the cavity in FIG. 16 are connected in the radial direction and integrated.
As described in the first embodiment, the magnitude of the reaction force due to the rolling of the weight 2 depends on the natural frequency ω of the weight 2, and therefore depends on the moment of inertia I of the weight 2. At the same time, as can be seen from the equation (1), the natural frequency ω also depends on the mass m.

  Therefore, in order to maintain the inertia moment I and reduce the weight, a hole near the center of the rotary plate 11 that has a small contribution to the inertia moment I is punched. From the same viewpoint, it is preferable to make the inside of the shaft portion 17 having a low contribution to the moment of inertia a cavity.

  The fifth embodiment has the same structure as that of the first embodiment except that the thickness near the center of the rotary plate 11 is reduced, and thus the duplicated description will be omitted. Also in the drawings, portions having the same configuration or function are denoted by the same reference numerals, and overlapping description will be omitted.

  As described above, according to the swing reducing device 1A of the fifth embodiment, in addition to the effects of the first embodiment, it is possible to fix the device to the ceiling surface from below.

(Sixth Embodiment)
12A and 12B are configuration diagrams of the diameter changing member 23 of the swing reducing device 1A according to the sixth embodiment.
12A shows a state before the diameter changing member 23 is attached, and FIG. 12B shows a state after the diameter changing member 23 is attached.

  As shown in FIGS. 12 (A) and 12 (B), the swing reduction device 1A according to the sixth embodiment has a hollow cylindrical shape that is detachably attached to the shaft portion 17 to change the diameter of the shaft portion 17. The diameter changing member 23 is provided.

  Normally, the conductor plate 7 only needs to be arranged so as to cross the magnetic flux Φ of the facing magnet 3, is not in contact with the shaft portion 17 of the weight body 2, and does not need to be extremely close to the shaft portion 17. . That is, there is a spatial margin around the shaft 17 that allows the diameter of the shaft 17 to be changed.

  Therefore, as shown in FIGS. 12A and 12B, a diameter changing member 23 is attached to the shaft portion 17 to change the inertia moment of the weight body 2. As shown in FIGS. 12 (A) and 12 (B), if the diameter-changing members 23 that have been divided in half are fastened with bolts 23a after being fastened, they can be easily fastened. By adjusting the moment of inertia, the natural vibration of the oscillation reducing device 1A can be adapted to the natural vibration of the structure 5 as in the fifth embodiment and the like.

  13A and 13B are configuration diagrams of a modification of the diameter changing member 23 of the swing reducing device 1A according to the sixth embodiment. FIG. 13A shows a state before the diameter changing member 23 is attached, and FIG. 13B shows a state after the diameter changing member 23 is attached.

  As shown in FIGS. 13A and 13B, the diameter changing member 23 may be an elastic ring whose one part is cut. In this case, after the cut portion is widened and mounted on the shaft portion 17, the cut portion is fixed by being fastened with the bolt 23a.

  The sixth embodiment has the same structure as the fifth embodiment and the like except that the radius of the shaft portion 17 is changed, and thus duplicated description will be omitted. Also in the drawings, portions having the same configuration or function are denoted by the same reference numerals, and overlapping description will be omitted.

  As described above, according to the swing reducing device 1A of the sixth embodiment, by changing the amount of the magnetic flux Φ penetrating the conductor plate 7, the swing can be performed without changing the distance between the rotating plates 11. The damping force can be adjusted.

(Seventh embodiment)
14A and 14B are schematic configuration diagrams of a swing reduction device 1A according to the seventh embodiment. FIG. 14 (A) is a side view of the swing reduction device 1A according to the seventh embodiment, and FIG. 14 (B) is a sectional view taken along line VV shown in FIG. 14 (A).

  As shown in FIGS. 14 (A) and 14 (B), the swing reduction device 1A according to the seventh embodiment faces a guide 15 provided on the base member 10A along a circular arc and a rotating plate 11 of the guide 15. And a roller 14 provided on the side surface of the roller.

  Usually, when an external force acts in the rotation axis direction when the weight body 2 rolls, the weight body 2 shifts in the rotation axis direction. If the weight 2 is displaced, the planned movement may be hindered due to the contact between the magnet 3 and the conductor plate 7 or the contact between the weight 2 and another member adjacent to the weight 2. When the displacement becomes large, it is expected that the rotary plate 11 will be released from the base member 10A.

Therefore, as shown in FIGS. 14 (A) and 14 (B), a guide 15 is provided along the rolling direction of the weight body 2 to prevent the rotating plate 11 from deviating from the rated track and maintain a stable posture. . For example, a ball 14a which rotates upon contact with the rotating plate 11 is a roller 14 provided at the distal end, arranged along the arc of the rail surface 10 _1.

  Even if the weight 2 rolls, one of the balls 14a is arranged on the rotating plate 11 so as to keep contacting with the rotating plate 11, thereby guiding the rolling of the weight 2 without causing friction. You can The ball 14a may be elastically pressed against the rotating plate 11 by a spring or the like.

  The seventh embodiment has the same structure as that of the first embodiment except that the weight 2 is guided, and thus the duplicated description will be omitted. Also in the drawings, portions having the same configuration or function are denoted by the same reference numerals, and overlapping description will be omitted.

  As described above, according to the swing reduction device 1A of the seventh embodiment, in addition to the effects of the first embodiment, it is possible to stabilize the rolling motion of the weight 2 and maintain the rated motion.

(Eighth Embodiment)
FIG. 15 (A) is a side view of the swing reduction device 1A according to the eighth embodiment, and FIG. 15 (B) is a sectional view taken along line VI-VI shown in FIG. 15 (A).

Swing reduction apparatus 1A according to the eighth embodiment, FIG. 15 (A), the as shown (B), the rotating plate 11, a flange 24 for derailment on a peripheral surface in contact with the rail surface 10 ₁ Prepare

As described in the seventh embodiment, when an external force acts in the rotation axis direction when the weight body 2 rolls, the weight body 2 may be displaced in the rotation axis direction and may derail. Therefore, in the eighth embodiment, the flange 24 is provided on the rotary plate 11. Flange 24 is preferably from rail surface 10 ₁ is provided on the inner side of the rotation axis direction.

  Further, this peripheral surface may be provided with a taper 25 in a direction in which the radius of the rotary plate 11 becomes smaller toward the outside in the rotation axis direction. By the flange 24 and the taper 25, when the weight body 2 is displaced or tilted in the rotation axis direction, the weight body 2 is returned to the rated track and the stable posture, and derailment is easily prevented.

  16 (A) and 16 (B) are diagrams showing a modification of the swing reduction device 1A according to the eighth embodiment. As shown in FIGS. 16A and 16B, the flange 24 and the taper 25 may be provided on the protruding surface 16 described in the first embodiment.

  The eighth embodiment has the same structure as that of the first embodiment except that the rotary plate 11 is provided with the flange 24 or the taper 25, and thus duplicated description will be omitted. Also in the drawings, portions having the same configuration or function are denoted by the same reference numerals, and overlapping description will be omitted.

  As described above, according to the swing reduction device 1A of the eighth embodiment, as in the seventh embodiment, it is possible to stabilize the rolling of the weight 2 and maintain the rated motion.

(9th Embodiment)
FIG. 17 (A) is a schematic perspective view of the swing reduction device 1B according to the ninth embodiment, and FIG. 17 (B) is a sectional view taken along the line VIII-VIII of FIG. 17 (A).

18 (A), (B) and FIGS. 19 (A), (B) are schematic views illustrating the structure 5 that is the object of swing reduction of the swing reduction device 1B according to the ninth embodiment. .
In FIGS. 18 (A) and 18 (B), it is installed in the same manner as the swing reduction device 1B shown in the first embodiment.
In FIGS. 19A and 19B, the swing reduction device 1B is fixed to the point upper surface from below with the floor surface of the vehicle body 5a as the ceiling surface.

In the swing reducing device 1B according to the ninth embodiment, as shown in FIGS. 12 (A), (B) to FIGS. 19 (A), (B), the base member 10 has a convex shape directed vertically downward. The two conductor rails 10B (10B ₁ , 10B ₂ ) having different diameters are arranged on the concentric circles.
The weight 2 is arranged in a gap between the outer peripheral surface of the inner conductor rail 10B ₁ and the inner peripheral surface of the outer conductor rail 10B ₂ facing the outer peripheral surface.

By shank 17 which connects the rotation plate 11 is placed on the rail surface 10 ₁ of the outer conductor rails 10B _2, the outer conductor rails 10B ₂ Role of conductive plate 7 shown in such the first embodiment I will also serve. That is, the magnetic flux Φ of the magnet 3 penetrates the conductor rail 10B that is the base member 10 to generate an eddy current in the conductor rail 10B. Since the gap width between the inner conductor rail 10B ₁ and the outer conductor rail 10B ₂ is narrower than the diameter of the rotary plate 11, the rotary plate 11 has a function of a flange for preventing the weight body 2 from coming off.

  The ninth embodiment has the same structure as that of the first embodiment except for the above-described configuration, and thus the duplicate description will be omitted. Also in the drawings, portions having the same configuration or function are denoted by the same reference numerals, and overlapping description will be omitted.

  As described above, according to the swing reducing device 1B of the ninth embodiment, in addition to the effects of the first embodiment, it is possible to fix the device to the ceiling surface from below.

  According to the swing reduction device 1 of at least one embodiment described above, it is possible to generate a high damping force and keep the swing reduction device 1A compact to realize a low natural frequency.

  Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These embodiments can be implemented in various other forms, and various omissions, replacements, changes, and combinations can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the invention described in the claims and the equivalents thereof as well as included in the scope and the gist of the invention.

  Although the base member 10 and the rotary plate 11 are both two in the example, the same effect can be obtained even if the number is 3 or more. Further, in each of the embodiments, the two base members 10 have been described as being provided separately in the structure 5 and the like, but the base member 10 is integrally formed as shown in FIG. 20, and the conductor plate 7 is used as the base member. It may be a structure to be fixed on 10. With such a configuration, the work can be shortened as compared with individually fixing the plurality of base members 10 and the conductor plate 7. Alternatively, the conductor plate 7 may be directly sandwiched between the two base members 10 and integrally formed.

1 (1A, 1B) ... Swing reduction device, 2 ... Weight body, 3 ... Magnet, 4 ... Vertical seismic isolation device, 5 (5a, 5b) ... Structure (ropeway vehicle body, building), 6 ... Fixed point, 7 (7a) ... Conductor plate (curved surface), 10 (10A, 10B) ... Base member (conductor rail), 10 ₁ (10) ... Rail surface, 11 (11a) ... Rotating plate (yoke), 12 (12a-12g) ) ... Length adjusting mechanism (flat plate, bolt, long hole, slide handle, fixing rod, fixing ring, shaft core), 13 (13a to 13e) ... Position adjusting mechanism (magnet fixing plate, groove, retaining plate, bolt, stopper) Attached rail), 14 (14a) ... Roller (ball), 15 ... Guide, 16 ... Projecting surface, 17 ... Shaft part, 18 (18a) ... Magnet fixing plate (bolt), 19 ... Thinned part, 21 ... Inner circle Part, 22 ... Peripheral circle part, 23 (23a) ... Diameter changing member (bolt), 24 ... Lunge, 25 ... taper, O ... center, Φ ... magnetic flux.

Claims (11)

A base member installed so that the convex shape of the curved surface is oriented vertically downward in a structure having an arcuate curved surface and swinging,
A rotary plate that constitutes both ends in the rotation axis direction of the weight body that rolls along the arc on the curved surface,
A conductor plate arranged in the gap between the rotating plates,
A swing reduction device comprising: a magnet that is disposed on a side surface of the rotating plate that faces the conductor plate and that allows a magnetic flux to penetrate through the conductor plate . The swing reduction device according to claim 1, wherein the rotating plate is placed on the curved surface and rolls. The swing reduction device according to claim 1 or 2, further comprising a length adjustment mechanism that adjusts a length of a shaft portion that connects the rotary plates to each other in a rotation axis direction. The swing reduction device according to any one of claims 1 to 3, wherein an outer peripheral portion of the rotary plate is made of a magnetic material, and the magnet is provided on the magnetic material. The swing reduction device according to any one of claims 1 to 4, wherein the magnet is removable. The swing reduction device according to claim 1, further comprising a position adjusting mechanism that fixes the magnet so as to be movable in a radial direction of the rotating plate. The swing reduction device according to any one of claims 1 to 6, wherein the rotary plate is provided with a thinned portion having a thickness smaller than that of an outermost peripheral portion. The swing reduction device according to claim 3, further comprising a hollow cylindrical diameter changing member that is detachably attached to the shaft portion to change a diameter of the shaft portion. A guide provided on the base member along the arc,
The swing reduction device according to claim 1, further comprising a roller provided on a side surface of the guide that faces the rotating plate. The swing reduction device according to any one of claims 1 to 9, wherein the rotating plate includes a flange that projects outward in the radial direction from a peripheral surface that contacts the curved surface. The base member is two conductor rails having different diameters and arranged on a concentric circle with a convex shape directed vertically downward,
The weight body is arranged in a gap between the outer peripheral surface of the inner conductor rail and the inner peripheral surface of the outer conductor rail facing the outer peripheral surface,
The swing reduction device according to claim 1, wherein the shaft portion that connects the rotating plate is placed on the curved surface of the outer conductor rail so that the outer conductor rail serves as the conductor plate.

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