JP5390287B2 - Vibration control device - Google Patents

Description

  The present invention relates to a structure damping device.

  Conventionally, a TMD (Tuned Mass Damper) having no drive device has been used as a vibration control device for reducing vibration of a structure. As a TMD structure, a structure including a weight suspended by an arm on the top floor of a structure is known.

  By the way, the vibration generated in a structure such as a skyscraper has a long period. In order to reduce long-period vibration by TMD, it is necessary to lengthen the length of the arm that suspends the weight and lengthen the TMD period. However, since the installation space for the structure is limited, it is required to keep the overall height of the vibration damping device low.

  Patent Document 1 discloses a vibration damping device for a TMD structure having a reduced height by using an inverted pendulum sub-mass in addition to a movable mass. This realizes a longer period without lengthening the arm.

JP-A-3-113143

  However, in the vibration damping device as in Patent Document 1, since the secondary mass is supported by one arm, when the vibration in the direction in which the secondary mass cannot move is added, the arm is excessively large. There was a possibility that a load might act.

  Accordingly, an object of the present invention is to provide a vibration damping device having excellent strength.

The present invention is inverted by a pendulum-shaped main mass that is suspended and swingable on a structure, and a support that is provided above the main mass and has a base end rotatably fixed to the structure. And a pendulum-shaped submass that can be swung in the same direction as the main mass, and a link portion that allows the main mass and the submass to be swung in synchronization with each other. Then, the main mass and the sub mass are swung in a long cycle in synchronization with the link portion, and thereby the vibration damping device capable of reducing the vibration of the structure, the support body and the sub mass Is characterized in that a gate-shaped swing frame is formed so as to cross the main mass in a direction perpendicular to the swingable direction of the main mass.

  In the present invention, the sub mass is supported by being inverted by a support body whose base end is rotatably fixed to the structure, and the support body and the sub mass intersect with the swingable direction of the main mass. A portal-type swing frame to be provided is formed. Therefore, when vibration in a direction incapable of moving is applied to the sub mass, the portal-type swing frame is difficult to deform, and therefore it is possible to prevent an excessive load from acting on the support.

  Therefore, a vibration damping device with excellent strength can be obtained.

It is a front view of the damping device concerning a 1st embodiment of the present invention. It is a side view in FIG. It is a front view of the vibration damping device which concerns on the modification of 1st Embodiment. It is a front view of the damping device concerning a 2nd embodiment of the present invention. It is a side view in FIG. It is a front view of the damping device concerning a 3rd embodiment of the present invention. It is a side view in FIG. FIG. 7 is a detailed view of the parallel link mechanism in FIG. 6.

(First embodiment)
Hereinafter, a vibration damping device 100 according to a first embodiment of the present invention will be described with reference to FIGS. 1 and 2.

  The damping device 100 includes a main mass 10 that is swingably suspended from a rectangular frame-shaped main body 1, an inverted pendulum sub-mass 20 that can swing in the same direction as the main mass 10, and a main mass 10. A link portion 30 for rocking the sub mass 20 in synchronization is provided. The vibration damping device 100 reduces the vibration of the structure using the force acting on the structure due to the vibration of the main mass 10 and the sub mass 20.

  The structure is, for example, a high-rise building, and the vibration control device 100 is installed at a high position of the structure such as the top floor or the roof of the high-rise building.

  The vibration damping device 100 is provided inside the main body 1, but is not limited to this mode. For example, without providing the main body 1, the main mass 10 is suspended from the upper floor and the sub mass 20 is moved from the lower floor. What is necessary is just to be fixed to a structure, such as making it invert.

  The main body 1 is provided with four columns 2 standing upright, four beams 3 that connect the upper ends of the four columns 2 in a rectangular shape, and two pairs of beams 3 that are opposed to each other. It is a rigid body provided with the beam 4.

  The four pillars 2 have the same length. Therefore, the beam 3 and the beam 4 are provided in parallel with the floor surface 5.

  The beam 4 is provided to suspend the main mass 10. The beam 4 is provided on the near side and the far side in FIG. 1 so as to be parallel to the near beam 3 appearing in FIG.

  In addition to providing the beam 4 to suspend the main mass 10, a top surface that fills a rectangular frame formed by the four beams 3 may be formed. Moreover, the aspect which suspends the main mass 10 from the beam 3 which comprises the main body 1 may be sufficient.

  The main body 1 is firmly fixed to the horizontal floor 5 of the structure. This is because the force by the vibration damping device 100 for reducing vibrations is transmitted from the fixing portion between the main body 1 and the floor surface 5 to the structure.

  The main mass 10 is a parallel pendulum-shaped rectangular parallelepiped weight suspended from the beam 4 by four arms 11 having the same length. The main mass 10 can swing in the longitudinal direction (left-right direction as viewed in FIG. 1). Hereinafter, this direction is referred to as a swingable direction.

  When the main mass 10 is installed in a high-rise building, for example, the mass ranges from about several tens tons to over 100 tons. The main mass 10 is composed of a large number of stacked iron plates, but may be made of reinforced concrete, or may be a tank filled with a liquid such as water.

  Attenuating means (not shown) for attenuating vibration of the main mass 10 is provided between the main mass 10 and the structure. The damping means is a damper when the damping device 100 is a TMD, and an actuator for controlling vibration when the damping device 100 is an AMD (Active Mass Damper). The actuator is, for example, a cylinder such as a hydraulic cylinder or an electric cylinder.

  When a cylinder is provided between the main mass 10 and the structure, the structure is provided with an acceleration sensor for detecting acceleration or a displacement sensor for detecting displacement. The cylinder is provided with a stroke sensor for detecting a stroke, and the cylinder is controlled by a signal from an acceleration sensor or a displacement sensor and a signal from the stroke sensor. Thereby, the vibration of the main mass 10 can be controlled.

  The arm 11 is rotatably fixed at the upper end to the beam 4 via a joint 12 and is rotatably fixed at the lower end to the main mass 10 via a joint 13. Two arms 11 are provided for each beam 4.

  The arm 11 is fixed at the same position by the beam 4 on the near side and the back side in FIG. 1, and is also fixed at the same position on the near side and the deep side on the upper side of the main mass 10. The main mass 10 is a parallel pendulum, and the main mass 10 does not tilt even when vibration is applied, and swings while maintaining parallel to the floor surface 5.

  When the main mass 10 swings, the rectangle formed by the beam 4, the two arms 11 and the main mass 10 in FIG. 1 is deformed into a parallelogram. At this time, the parallelogram formed by the beam 4 on the front side and the two arms 11 and the main mass 10 is the parallelogram formed by the beam 4 on the back side and the two arms 11 and the main mass 10. Always congruent.

  The joint 12 and the joint 13 are pin joints that allow the arm 11 to rotate only in the swingable direction of the main mass 10 around the pin. By providing the joints 12 and 13, the main mass 10 swings in the swingable direction, and cannot swing from the front to the back as viewed in FIG. 1.

  The auxiliary mass 20 is an inverted pendulum type weight provided so as to overlap the upper side of the main mass 10 and inverted from the floor surface 5. The sub mass 20 can swing in the same direction as the main mass 10. That is, the sub mass 20 can swing in the swingable direction of the main mass 10.

  The sub mass 20 has a mass of, for example, several tens of tons, and is formed with a mass smaller than that of the main mass 10. The sub mass 20 is composed of a large number of iron plates stacked in the same manner as the main mass 10. The sub mass 20 is supported to be swingable with respect to the floor surface 5 by two pillars 21 as a support.

  Although the two pillars 21 are provided as the support, the present invention is not limited to this mode. For example, a gate-type support may be formed and the sub mass 20 may be supported on the top. Good.

  The column 21 is fixed to the floor surface 5 via a joint 23 so as to be rotatable. The joint 23 is a pin joint that enables the column 21 to rotate only in a swingable direction around the pin. Thus, when vibration is applied, the sub mass 20 swings in the swingable direction with the pin of the joint 23 as a fulcrum.

  The auxiliary mass 20 forms a swing frame 25 having a portal ramen structure integrally with the two pillars 21.

  The swing frame 25 is provided so as to cross the main mass 10 in a swingable direction and straddle the main mass 10. That is, the swing frame 25 is provided perpendicular to the swingable direction of the main mass 10 and the sub mass 20. Therefore, the swing frame 25 swings in the same direction as the swingable direction of the main mass 10 and the sub mass 20 so as to collapse while maintaining the gate shape. The swing frame 25 has a structure that is not easily deformed when the upper end of the column 21 is firmly fixed by the sub mass 20.

  The sub mass 20 is provided so as to be parallel to the main mass 10 in a state where the column 21 is perpendicular to the floor surface 5. The auxiliary mass 20 is horizontal when it stands upright perpendicular to the floor surface 5, but it tilts when it is shaken by vibration. This is because the secondary mass 20 is provided integrally with the column 21 that rotates about the joint 23, so that the inclination angle of the column 21 becomes the inclination angle of the secondary mass 20.

  The inclination angle of the sub mass 20 is larger when the movement amount is larger than when the movement amount is small. Thus, since the secondary mass 20 swings and tilts, the distance between the main mass 10 and the secondary mass 20 is larger than the distance that does not collide with the primary mass 10 even when the secondary mass 20 moves to the maximum extent. It is also necessary to keep a large distance.

  The sub mass 20 is linked to the main mass 10 via the link portion 30 and swings in a swingable direction in synchronization with the main mass 10.

  The link part 30 is provided in the upper part of the main mass 10 and in the lower part of the sub mass 20. The link portion 30 includes a transmission beam 22 that connects the pair of columns 21 that support the sub mass 20, a pair of clamping portions 14 that are formed on the main mass 10 so as to sandwich the transmission beam 22, and a clamping portion 14 And a pair of rollers 31 provided so as to always come into contact with both of the transmission beams 22.

  The transmission beam 22 is provided so as to connect the two columns 21 that support the sub mass 20. The transmission beam 22 is formed integrally with the swing frame 25 so as to be positioned between the main mass 10 and the sub mass 20. Therefore, since the transmission beam 22 fixes the column 21, the strength of the swing frame 25 is further increased. The transmission beam 22 is formed perpendicular to the swingable direction of the main mass 10 and the sub mass 20 and parallel to the floor surface 5. This transmission beam 22 corresponds to a transmission part.

  When the sub mass 20 swings in the swingable direction, the transmission beam 22 moves up and down along with the swing. This is because the transmission beam 22 is integral with the column 21 and rotates around the joint 23.

  A pair of sandwiching portions 14 are formed in a convex shape at the upper center of the main mass 10. The two sandwiching portions 14 are arranged in series in the swingable direction of the main mass 10. The clamping unit 14 is provided so as to clamp the transmission beam 22, and is provided to transmit a force to and from the transmission beam 22.

  The clamping part 14 is a rectangular parallelepiped protrusion, and is formed so that the longitudinal direction is perpendicular to the swingable direction of the main mass 10 and the sub mass 20. Instead of forming the sandwiching portion 14 in a convex shape, a recess corresponding to the inner surface between the sandwiching portions 14 may be formed in the upper portion of the main mass 10.

  When the main mass 10 swings in the swingable direction, the clamping unit 14 moves up and down with the swing. This is because the main mass 10 is fixed to the arm 11 that rotates around the joint 12.

  The roller 31 is provided to ensure slidability between the transmission beam 22 and the sandwiching portion 14. The roller 31 is provided so as to rotatably contact both the transmission beam 22 and the sandwiching portion 14. Specifically, the roller 31 is provided between the pair of sandwiching portions 14 and the transmission beam 22 and is rotatably fixed to the transmission beam 22. Instead of fixing the roller 31 to the transmission beam 22, the roller 31 may be rotatably fixed to the clamping unit 14.

  The roller 31 is provided so that a pair of clamping part 14 and an outer peripheral surface contact | abut. The roller 31 rotates following the relative vertical movement of the main mass 10 and the sub mass 20 accompanying the swing.

  Since the roller 31 only needs to ensure the slidability between the sandwiching portion 14 and the transmission beam 22, the roller 31 may be a universal joint that couples the sandwiching portion 14 and the transmission beam 22, for example. Further, without providing the roller 31, surface processing for improving slidability such as resin processing may be performed on the surfaces of the sandwiching portion 14 and the transmission beam 22 that are in contact with each other.

  The position where the link portion 30 is provided is not limited to the upper portion of the main mass 10, and may be a side portion or a lower portion of the main mass 10.

  Hereinafter, the operation of the vibration damping device 100 will be described.

  When an external force is applied, such as when a strong wind hits the structure, the structure vibrates. Vibration is also applied to the vibration damping device 100, and the main mass 10 swings integrally with the sub mass 20 linked via the link portion 30. The vibration of the structure can be reduced by the swinging of the main mass 10 and the sub mass 20.

  Here, due to the inertial force of the secondary mass 20, the equivalent mass of the vibration damping device 100 is increased and the equivalent rigidity is reduced. Therefore, the total natural period of the primary mass 10 and the secondary mass 20 is the same as that of the primary mass 10 alone. It becomes longer than the natural period. Therefore, the natural period of the vibration damping device 100 is lengthened, and long-period vibration of the structure can be reduced.

  Hereinafter, a specific operation when vibration is applied to the vibration damping device 100 will be described. Here, the case where the main mass 10 and the sub mass 20 swing rightward as viewed in FIG. 1 will be described. The same operation is performed when the main mass 10 and the sub mass 20 swing leftward.

  The main mass 10 moves in the right direction and moves upward as the arm 11 rotates around the joint 12.

  The sub mass 20 moves in the right direction in synchronization with the main mass 10, and the sub mass 20 moves in the right direction and moves downward along with the rotation of the column 21 around the joint 23. The sub mass 20 and the column 21 constitute a gate-shaped swing frame 25 provided to intersect the swingable direction of the main mass 10 and the sub mass 20, and thus the gate shape of the swing frame 25 is maintained. Swing as if falling down.

  As described above, the clamping portion 14 formed in the main mass 10 and the transmission beam 22 provided integrally with the sub mass 20 relatively move up and down. Specifically, in the state shown in FIG. 1 in which the arm 11 and the column 21 are perpendicular to the floor surface 5, the distance between the sandwiching portion 14 and the transmission beam 22 is the maximum, and the main mass 10 and the sub mass The distance between the holding portion 14 and the transmission beam 22 decreases as the position 20 swings greatly.

  Thus, since the clamping part 14 and the transmission beam 22 move up and down relatively, they are in contact with each other via the pair of rollers 31. By providing the roller 31, slidability can be ensured even when the sandwiching portion 14 and the transmission beam 22 move up and down relatively.

  The clamping part 14 needs to be formed higher than the height at which the roller 31 moves in accordance with the relative vertical movement of the clamping part 14 and the transmission beam 22. Further, the distance between the main mass 10 and the sub mass 20 needs to be separated from the distance by which the transmission beam 22 does not collide with the main mass 10 due to the relative vertical movement of the main mass 10 and the sub mass 20. There is.

  Conventionally, the secondary mass was an inverted pendulum supported by a single column. Therefore, when a force in a direction in which the secondary mass cannot move is applied, an excessive force due to the mass of the secondary mass acts on the column. There was a risk.

  On the other hand, in the vibration damping device 100, the secondary mass 20 is supported by the two columns 21. Further, the sub mass 20 and the two columns 21 form a swing frame 25 having a portal ramen structure that intersects the swingable direction of the main mass 10 and the sub mass 20.

  Here, when the vibration acts in the direction in which the secondary mass 20 cannot move, and the secondary mass 20 tries to move in the direction in which the secondary mass 20 cannot move, the swing frame 25 tries to deform the portal shape. Force to act. However, the swing frame 25 having a portal ramen structure is not easily deformed because the upper end of the column 21 is firmly fixed by the sub mass 20, and the rigidity against the force in the direction in which the sub mass 20 cannot move is ensured. it can.

  Conventionally, a through hole is formed in the main mass, and a pillar supporting the sub mass is passed through the through hole. Therefore, when trying to make the mass equivalent to that of the vibration damping device 100, it is necessary to form the outer shape of the main mass as much as the through hole.

  On the other hand, in the vibration damping device 100, since the column 21 that supports the sub mass 20 is installed so as to surround the outside of the main mass 10, it is not necessary to form a through hole in the main mass 10. Therefore, the processing cost of the through hole can be suppressed, and the main mass 10 can be made smaller by the amount not forming the through hole.

  Further, in the conventional structure, it is difficult to assemble the sub mass held by one column alone, and one column supporting the sub mass passes through a through hole formed in the main mass. Therefore, it was necessary to assemble the secondary mass at the same time as the main mass.

  On the other hand, in the vibration damping device 100, the main mass 10 and the sub mass 20 can be assembled separately in advance, and the assemblability is improved.

  According to the above embodiment, the following effects are obtained.

  In the present invention, the secondary mass 20 is supported by two columns 21, and the column 21 and the secondary mass 20 have a swing frame with a portal ramen structure that intersects the main mass 10 and the movable direction of the secondary mass 20. 25 is formed. Therefore, even when a force in a direction in which the secondary mass 20 cannot move is applied due to an earthquake or the like, the portal-type swing frame 25 has the upper end of the column 21 firmly fixed by the secondary mass 20. Therefore, an excessive load can be prevented from acting on the column 21. Therefore, it is possible to obtain the vibration damping device 100 having excellent strength.

  Here, the vibration damping device 100 can reduce the vibration only with respect to the vibration of the main mass 10 and the sub mass 20 in the swingable direction (left-right direction as viewed in FIG. 1). However, the joints 12 and 13 that support the main mass 10 are changed to universal joints, and the sub mass that can swing in the direction perpendicular to the direction in which the sub mass 20 can swing (the front-rear direction in FIG. 1). Further, it is possible to reduce the roll acting on the structure from any lateral direction.

  Hereinafter, a vibration damping device 150 that is a modification of the vibration damping device 100 according to the first embodiment of the present invention will be described with reference to FIG.

  The vibration damping device 150 is different from the vibration damping device 100 in that it includes a plurality of sub masses 60 and 61 arranged in the longitudinal direction of the main mass 50. In the vibration damping device 150, the two sub masses 60 and 61 are provided, but three or more sub masses may be provided.

  When the number of the sub masses 60 and 61 increases, the installation area of the vibration damping device 150 needs to be increased. However, since the heights of the sub masses 60 and 61 can be suppressed, the height of the vibration damping device 150 can be reduced.

  Like the main mass 10, the main mass 50 is a parallel pendulum-shaped rectangular parallelepiped weight suspended from the beam 4 by four arms 11 having the same length.

  Similar to the sub mass 20, the sub masses 60, 61 are inverted from the floor surface 5 by the pillars 62, 63 as supports that are rotatably fixed to the floor surface 5 through the joints 64, 65. It is a supported inverted pendulum type weight. A pair of pillars 62 and 63 are provided.

  The sub masses 60 and 61 and the pillars 62 and 63 form swing frames 68 and 69 that are frames of a portal ramen structure, respectively, similarly to the swing frame 25.

  The joints 64 and 65 are pin joints that allow the columns 62 and 63 to be rotated only in a swingable direction around the pin. Thus, when vibration is added, the sub masses 60 and 61 swing in the swingable direction using the pins of the joints 64 and 65 as fulcrums, respectively.

  The sub masses 60 and 61 are provided in parallel with the main mass 50 in a state where the columns 62 and 63 are perpendicular to the floor surface 5. The sub masses 60 and 61 are horizontal when they stand upright perpendicular to the floor surface 5, but are inclined when they are swung with vibrations applied.

  The sub masses 60 and 61 swing in the swingable direction in synchronization with the main mass 50 while being linked to the main mass 50 via the link portions 70 and 71.

  The link portions 70 and 71 are provided above the main mass 50 and below the sub masses 60 and 61. The link portions 70 and 71 are formed on the main mass 50 so as to sandwich the transmission beams 66 and 67 connecting the pair of columns 62 and 63 supporting the sub masses 60 and 61 and the transmission beams 66 and 67. Parts 54 and 55, and a pair of rollers 31 rotatably fixed to the transmission beam so as to always contact the holding parts 54 and 55.

  The transmission beams 66 and 67 are provided so as to connect the two pillars 62 and 63 constituting the swing frames 68 and 69, respectively. The transmission beams 66 and 67 are provided integrally with the swing frames 68 and 69 so as to be positioned between the main mass 50 and the sub masses 60 and 61. The transmission beams 66 and 67 are formed perpendicular to the swingable direction of the main mass 10 and the sub mass 20 and parallel to the floor surface 5. The transmission beams 66 and 67 correspond to the transmission unit.

  The sandwiching portions 54 and 55 are formed in a convex shape on the top of the main mass 50. The clamping parts 54 and 55 are formed in series in the swingable direction of the main mass 50. The sandwiching portions 54 and 55 are provided so as to sandwich the transmission beams 66 and 67, respectively, and are provided to transmit force between the transmission beams 66 and 67.

As described above, the vibration damping device 150 includes the plurality of sub masses 60 and 61. As a result, it is possible to obtain a vibration damping effect equivalent to the case where a sub mass having a large sum of the masses of the sub masses 60 and 61 is provided. Moreover, the height of the submass 60, 61 can be suppressed by providing the submass 60, 61 separately.
(Second Embodiment)
Hereinafter, a vibration damping device 200 according to a second embodiment of the present invention will be described with reference to FIGS. 4 and 5. In the following embodiments, the same reference numerals are given to the same components as those in the above-described embodiments, and the overlapping description will be omitted as appropriate.

  The second embodiment is different from the first embodiment in which the sub mass 20 is a single pendulum type in that the sub mass 220 is a parallel pendulum type.

  The sub mass 220 is a parallel pendulum type weight provided by being inverted from the floor surface 5. The sub mass 220 is supported by four columns 221 having the same length.

  Two columns 221 are provided at both ends in the longitudinal direction of the sub mass 220 (left and right ends as viewed in FIG. 4) so as to overlap with the front side and the back side, respectively. The column 221 is rotatably fixed to the sub mass 220 via the joint 224 and is rotatably fixed to the floor surface 5 via the joint 223. As a result, even if vibration is applied, the sub mass 220 does not tilt around the fulcrum and swings while maintaining parallel to the floor surface 5.

  The joint 223 and the joint 224 are pin joints that allow the column 221 to rotate only in a swingable direction around the pin. By the joints 223 and 224, the sub mass 220 swings in the swingable direction (left and right direction as viewed in FIG. 4). Since the auxiliary mass 220 is supported by the column 221 so as to be swingable, it moves up and down in addition to translational movement in the longitudinal direction.

  The sub mass 220 forms two gate-shaped swing frames 225 by combining two of the four columns 221 each. In the present embodiment, there are two swing frames 225, but there may be three or more.

  The swing frame 225 is provided so as to intersect with the main mass 10 and cross the main mass 10. That is, the swing frame 225 is provided perpendicular to the swingable direction of the main mass 10 and the sub mass 220. Therefore, the swing frame 225 swings in the same direction as the swingable direction of the main mass 10 and the sub mass 220 so as to collapse while maintaining the gate shape. The swing frame 225 has a structure that is difficult to deform when the upper end of the column 221 is fixed by the sub mass 220.

  The link part 230 is provided in the upper part of the main mass 10 and in the lower part of the sub mass 220. The link portion 230 includes a transmission protrusion 222 formed at a lower portion of the sub mass 220, a pair of clamping portions 14 formed on the main mass 10 so as to sandwich the transmission projection 222, and the clamping portion 14 and the transmission projection 222. And a pair of rollers 231 provided so as to always come into contact with both.

  The transmission protrusion 222 is formed in a convex shape toward the main mass 10 in the lower center of the sub mass 220. The transmission protrusion 222 is formed perpendicular to the movable direction of the main mass 10 and the sub mass 220. The transmission protrusion 222 transmits a force between the main mass 10 and the sub mass 220. This transmission protrusion 222 corresponds to a transmission part.

  The roller 231 is provided in order to ensure slidability between the transmission protrusion 222 and the sandwiching portion 14. The roller 231 is provided between the pair of sandwiching portions 14 and the transmission protrusion 222 and is rotatably fixed to the transmission protrusion 222. The outer peripheral surface of the roller 231 is always in contact with the clamping unit 14. The roller 231 rotates following the relative vertical movement of the main mass 10 and the sub mass 220 accompanying the swing.

  Hereinafter, the operation of the vibration damping device 200 will be described.

  When an external force is applied, such as when a strong wind hits the structure, the structure vibrates. Vibration is also applied to the vibration damping device 200, and the main mass 10 swings integrally with the sub mass 220 in synchronization. The vibration of the structure can be reduced by the swinging of the main mass 10 and the sub mass 220.

  Here, due to the inertial force of the secondary mass 220, the equivalent mass of the vibration damping device 200 is increased and the equivalent rigidity is reduced. Therefore, the total natural period of the main mass 10 and the secondary mass 220 is that of the main mass 10 alone. It becomes longer than the natural period. Therefore, the natural period of the vibration damping device 200 is lengthened, and the long-period vibration of the structure can be reduced.

  Here, the secondary mass 220 in the vibration damping device 200 is a parallel pendulum type. Therefore, the sub mass 220 swings in the swingable direction while maintaining a state parallel to the floor surface 5. As described above, the sub mass 220 swings while maintaining parallel without being inclined, and therefore the vertical range in which the sub mass 220 moves in parallel is smaller than that of the vibration damping device 100 in which the sub mass 20 is inclined. . Therefore, the height of the vibration damping device 200 can be reduced.

  According to the above embodiment, the following effects are obtained.

Since the secondary mass 220 is a parallel pendulum type, the secondary mass 220 translates without being inclined. Therefore, the range in the vertical direction in which the secondary mass 220 moves in parallel is smaller than that of the vibration damping device 100 in which the secondary mass 20 is inclined. Therefore, it is possible to reduce the height of the vibration damping device 200.
(Third embodiment)
Hereinafter, a vibration damping device 300 according to a third embodiment of the present invention will be described with reference to FIGS.

  In the third embodiment, the sub mass 320 is a parallel pendulum as in the second embodiment, but differs from the first and second embodiments in that the link portion 330 is a parallel link mechanism. .

  First, the overall configuration of the link unit 330 will be described with reference to FIGS. 6 and 7.

  A pair of link portions 330 are provided symmetrically across the main mass 310, but only one link portion 330 shown in FIG. 6 will be described here.

  The link part 330 is provided so as to connect the two joints 319 provided in the link attachment part 318 formed in the main mass 310 and the two joints 329 provided in the sub mass 320. The link part 330 transmits force between the main mass 310 and the sub mass 320.

  The main mass 310 includes a link attachment portion 318 formed in a convex shape laterally from the lower portion, and two joints 319 fixed to the link attachment portion 318.

  The link attachment portion 318 is a portion that becomes a base on which the link portion 330 is attached. The link attachment portion 318 is formed integrally with the main mass 310 and transmits force to the sub mass 320.

  The joint 319 is a pin joint that is capable of rotational movement with one degree of freedom around the pin.

  The joint 329 is fixed to the lower surface of the sub mass 320. The joint 329 is provided inside a joint 224 that is rotatably connected to the column 21. This is because the column 221 needs to pass outside the link portion 330. The joint 329 is also a pin joint capable of rotating motion with one degree of freedom around the pin.

  The link unit 330 includes a pair of parallel links 338 that are rotatably connected to the main mass 310 via a joint 319, and a pair of parallel links 339 that are rotatably connected to the sub mass 320 via a joint 329. A pair of central joints 336 that connect the free ends of the parallel links 338 and 339 and a central link 337 that connects the pair of central joints 336 are provided. These parallel links 338 and 339 correspond to a first parallel link and a second parallel link, respectively.

  Two parallel links 338 and 339 are provided, and the free ends of the parallel links 338 and 339 are connected to the central joint 336, respectively. Since the parallel links 338 and 339 are formed with the same length, the parallel links 338 and 339 are symmetrical with respect to the central link 337.

  The central link 337 is movable in the longitudinal direction while maintaining the level with the main mass 310 and the sub mass 320. A central link 337 is provided between the two central joints 336.

  As shown in FIG. 6, the first parallelogram A is formed above the central link 337 by the pair of joints 329 and the pair of central joints 336. The pair of joints 319 and the pair of central joints 336 form a second parallelogram B below the central link 337.

  The first parallelogram A and the second parallelogram B are symmetrical with respect to the central link 337 as the axis of symmetry because the parallel links 338 and 339 have the same length. The two parallelograms A and B always maintain symmetry with the central link 337 as the axis of symmetry even when the main mass 310 and the sub mass 320 swing. For this reason, the amount of movement of the main mass 310 and the sub mass 320 is always the same. As described above, the vibration damping device 300 can be used only when the ratio of the swinging movement amount of the main mass 310 and the sub mass 320 is 1: 1.

  Next, a detailed configuration of the parallel link mechanism will be described with reference to FIG.

  The pair of central joints 336 are respectively one central joint 336a and the other central joint 336b. The central joints 336a and 336b are firmly fixed to both ends of the central link 337 by welding or the like. Therefore, the distance between the central joints 336a and 336b is always constant.

  One central joint 336a is a gear box that internally includes a gear 336c provided at the end of the parallel link 339 and a gear 336d provided at the end of the parallel link 338. The gear 336c and the gear 336d are engaged with each other. Since the gear 336c and the gear 336d rotate in opposite directions while being synchronized, the angle between the central link 337 and the parallel link 338 is equal to the angle between the central link 337 and the parallel link 339.

  The other central joint 336 b includes a joint 336 e provided at the end of the parallel link 339 and a joint 336 f provided at the end of the parallel link 338. The joint 335e and the joint 336f are both pin joints that can rotate around the pin. The parallel links 338 and 339 that are swingably fixed to the central joint 336b swing so as to always maintain parallelism with the parallel links 338 and 339 that are swingably fixed to the central joint 336a. Thus, two parallelograms A and B that are symmetrical in the vertical direction with the central link 337 as the axis of symmetry are formed.

  As described above, when the parallel link 339 is swung by the inertial force of the sub mass 320, the force is transmitted to the parallel link 338 via the gears 336c and 336d. The parallel link 338 swings symmetrically with the parallel link 339 with the central link 337 as an axis of symmetry, and the force transmitted to the parallel link 338 is transmitted to the main mass 310. Therefore, a shearing force (a horizontal force) can be transmitted between the main mass 310 and the submass 320, and the inertial force of the submass 320 is transmitted to the main mass 310.

  Hereinafter, the operation of the vibration damping device 300 will be described.

  When an external force is applied, such as when a strong wind hits the structure, the structure vibrates. Vibration is also applied to the vibration damping device 300, and the main mass 310 swings integrally with the sub mass 320 via the link portion 330. By swinging the main mass 310 and the sub mass 320, the vibration of the structure can be reduced.

  Here, due to the inertial force of the secondary mass 320, the equivalent mass of the vibration damping device 300 is increased and the equivalent stiffness is reduced. Therefore, the total natural period of the primary mass 310 and the secondary mass 320 is the same as that of the primary mass 310 alone. It becomes longer than the natural period. Therefore, the natural period of the vibration damping device 300 is lengthened, and the long-period vibration of the structure can be reduced.

  Here, in the vibration damping device 300, transmission of force between the main mass 310 and the sub mass 320 is performed via the link portion 330 that is a parallel link mechanism. Therefore, as compared with the first and second embodiments in which force is transmitted via a roller, it is possible to make the operation smooth because there is no friction part.

  According to the above embodiment, the following effects are obtained.

  Since the transmission of force between the main mass 310 and the sub mass 320 is performed via the link portion 330 that is a parallel link mechanism, the operation can be smoothed because there is no friction portion.

  The present invention is not limited to the above-described embodiment, and it is obvious that various modifications can be made within the scope of the technical idea.

  For example, it is sufficient that at least one submass is provided, and a plurality of submasses may be provided from various viewpoints such as ease of manufacture, accommodation of a damping device, and improvement of damping effect.

  The vibration damping device according to the present invention can be used as a vibration damping device for suppressing vibrations in structures such as high-rise buildings and bridges.

DESCRIPTION OF SYMBOLS 100 Damping device 1 Main body 2 Column 3 Beam 4 Beam 5 Floor 10 Main mass 11 Arm 12 Joint 13 Joint 14 Clamping part 20 Submass 21 Column 22 Transmission beam 23 Joint 25 Swing frame 30 Link part 31 Roller

Claims (7)

A pendulum-shaped main mass suspended and swingable on a structure;
A pendulum-shaped submass provided above the main mass and supported by being inverted by a support body whose base end is rotatably fixed to the structure; and swingable in the same direction as the main mass;
A link part for synchronizing and swinging the main mass and the sub mass,
When vibration is added, the main mass and the sub mass are oscillated in a long cycle in synchronization with the link portion, thereby being able to reduce the vibration of the structure,
The damping device according to claim 1, wherein the support body and the sub mass form a gate-shaped swing frame that crosses the main mass in a direction perpendicular to a swingable direction of the main mass.   The damping device according to claim 1, wherein the damper is a TMD (tuned mass damper) in which a damper for attenuating vibration of the main mass is installed between the main mass and the structure. .   2. The vibration damping device according to claim 1, wherein the vibration damping device is an AMD (active mass damper) in which an actuator for controlling vibration of the main mass is installed between the main mass and the structure. . The link part is
A transmission unit provided integrally with the sub mass;
A pair of clamping parts formed on the main mass so as to clamp the transmission part;
4. The vibration damping device according to claim 1, further comprising: a roller that is provided so as to rotatably contact both of the transmission unit and the clamping unit. 5. Comprising a plurality of said supports,
The said support body and the said submass form the said some rocking | fluctuation frame, The parallel pendulum which rocks | fluctuates keeping the parallel with the said main mass is any one of Claim 1 to 4 characterized by the above-mentioned. The vibration damping device according to one. Comprising a plurality of said supports,
The support and the sub mass are a parallel pendulum that forms a plurality of the swing frames and swings while maintaining parallel with the main mass,
The link part is
A plurality of first parallel links whose ends are rotatably fixed to the main mass;
A plurality of second parallel links whose ends are rotatably fixed to the submass,
4. The vibration damping device according to claim 1, wherein a parallel link mechanism is formed by connecting a free end of the first parallel link and a free end of the second parallel link. 5. . A pendulum-shaped main mass suspended and swingable on a structure;
A pendulum-shaped submass provided above the main mass and supported by being inverted by a support body whose base end is rotatably fixed to the structure; and swingable in the same direction as the main mass;
A link part for synchronizing and swinging the main mass and the sub mass,
When vibration is added, the main mass and the sub mass are oscillated in a long cycle in synchronization with the link portion, thereby being able to reduce the vibration of the structure,
The support and the sub mass form a gate-shaped swing frame that crosses the main mass and intersects the swingable direction of the main mass,
The support is two pillars supporting the submass,
The vibration control device according to claim 1, wherein the swing frame has a ramen structure formed by the two columns and the sub mass.

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