JP2018128134A - Vibration suppression device for structures - Google Patents

Abstract

PROBLEM TO BE SOLVED: To appropriately control the inertial mass of a variable rotation inertial mass damper according to the occasional vibration input to a structure, whereby the inertial mass above the predetermined layer of the structure provided with the variable rotation inertial mass damper. Provided is a structure vibration suppression device capable of appropriately suppressing the vibration of the layer. An interlayer displacement of a predetermined layer transmitted with vibration of a structure is converted into a rotational motion of a rotating mass, and a variable rotational inertial mass damper generates an inertial mass generated with the rotation of the rotating mass. It is configured to be continuously changeable. The predominant frequency fcp, which is the frequency of the predominant frequency component of the vibration input to the structure, is obtained (step 2), and during the vibration of the structure, the rigidity of the predetermined layer and the inertial mass of the variable rotational inertia mass damper The inertial mass of the variable rotary inertial mass damper is controlled so that the determined breaking frequency is tuned to the acquired dominant frequency fcp (steps 3 to 6). [Selection diagram] FIG. 9

Description

  The present invention relates to a vibration suppressing device for a structure that has a plurality of layers and suppresses vibrations of the structure standing on the foundation.

  Conventionally, for example, a device disclosed in Patent Document 1 is known as a vibration suppressing device for this type of structure. This vibration suppression device is applied to a high-rise building erected on the foundation, and includes an additional vibration system (TMD mechanism) provided at the upper layer of the building and a lower layer below the upper layer of the building. Provided with a vibration isolating mechanism provided with a rotary inertia mass damper. The additional vibration system has a rotary inertia mass damper and an additional spring provided in series with each other, and the natural frequency thereof is set so as to be synchronized with the primary natural frequency of the building.

  In addition, the rotary inertia mass damper of the vibration isolating mechanism is configured to convert the interlayer displacement of the lower layer part due to the vibration of the building into the rotary motion of the rotary mass, and is generated with the rotation of the rotary mass. The natural frequency determined by the inertial mass of the rotary inertia mass damper and the rigidity of the lower layer (hereinafter referred to as the “natural frequency of the vibration isolation mechanism”) is tuned to a predetermined cutoff frequency, for example, the secondary natural frequency of the building It is set to be. As a result, during the vibration of the building, by concentrating the deformation due to the vibration of the cutoff frequency to the lower layer, the vibration of the building is suppressed by blocking the transmission of the earthquake vibration of the cutoff frequency to the upper layer. I have to.

Patent No. 5316849

  The characteristics of the vibration (earthquake) input to the building from the foundation side are not constant, and the frequency of the dominant frequency component (hereinafter referred to as “excellent frequency”) tends to be different from time to time. On the other hand, in the conventional vibration suppression device described above, the inertial mass of the rotary inertia mass damper of the additional vibration system and the vibration isolation mechanism cannot be controlled, and the natural frequency of the additional vibration system is always set to the primary natural vibration of the building. The natural frequency of the vibration isolating mechanism is always tuned to the secondary natural frequency of the building. For this reason, when the dominant frequency of the vibrations input to the building is higher than the primary and secondary natural frequencies of the building, the vibration of the building cannot be appropriately suppressed by the additional vibration system and the vibration isolating mechanism. There is a fear. Such a problem becomes more prominent when the dominant frequency is close to the natural frequency of the third or higher order of the building.

  The present invention has been made to solve the above-described problems, and can appropriately control the inertial mass of the variable rotational inertial mass damper according to the current vibration input to the structure from the foundation side, Accordingly, an object of the present invention is to provide a vibration suppressing device for a structure that can appropriately suppress vibration of a layer above a predetermined layer of the structure provided with the variable rotational inertia mass damper.

  In order to achieve the above object, an invention according to claim 1 is a structure vibration suppressing device for suppressing vibration of a structure that has a plurality of layers and is erected on a foundation, wherein the rotating mass is It is provided in a predetermined layer of the structure, and the interlayer displacement of the predetermined layer transmitted along with the vibration of the structure is converted into the rotational motion of the rotating mass, and is generated as the rotating mass rotates. A variable rotation inertial mass damper configured to be able to continuously change the inertial mass, and a dominant frequency acquisition means for acquiring a dominant frequency which is a frequency of a dominant frequency component of vibrations input to the structure from the foundation side; Control that controls the inertial mass of the variable rotational inertial mass damper so that the cutoff frequency determined by the rigidity of the predetermined layer and the inertial mass of the variable rotational inertial mass damper is synchronized with the acquired dominant frequency during vibration of the structure hand Characterized in that it comprises a and.

  According to this configuration, the variable rotation inertia mass damper having the rotation mass is provided in the predetermined layer of the structure, and the displacement of the structure transmitted to the variable rotation inertia mass damper due to the vibration of the structure is rotated. It is converted into mass rotation. Further, in the variable rotation inertial mass damper, the inertial mass generated with the rotation of the rotation mass can be continuously changed.

  Furthermore, the dominant frequency, which is the frequency of the dominant frequency component of the vibration input to the structure from the foundation side, is acquired by the dominant frequency acquisition means, and during the vibration of the structure, the rigidity of the predetermined layer and the variable rotational inertial mass The inertial mass of the variable rotary inertial mass damper is controlled by the control means so that the cutoff frequency determined by the inertial mass of the damper is tuned to the acquired dominant frequency. As a result, during the vibration of the structure, the cutoff frequency is tuned to the dominant frequency of the input vibration from the foundation side, thereby increasing the deformation of the predetermined layer due to the vibration of the dominant frequency, and above the predetermined layer of the structure. Transmission of vibrations of the dominant frequency to the layer can be cut off, and thus vibrations of the upper layer can be appropriately suppressed.

  As described above, according to the present invention, it is possible to appropriately control the inertial mass of the variable rotation inertial mass damper according to the current vibration input to the structure from the foundation side. The vibration of the layer above the predetermined layer of the provided structure can be suppressed appropriately. Note that “tuning” in the present invention includes adjusting the cut-off frequency to be substantially the same as the dominant frequency in addition to adjusting the cutoff frequency to be the same as the dominant frequency.

  In order to achieve the above object, an invention according to claim 2 is a structure vibration suppressing device for suppressing vibration of a structure having a plurality of layers and standing on a foundation, wherein the rotating mass is It is provided in a predetermined layer of the structure, and the interlayer displacement of the predetermined layer transmitted along with the vibration of the structure is converted into the rotational motion of the rotating mass, and is generated as the rotating mass rotates. A variable rotational inertial mass damper configured to be able to change the inertial mass, a superior frequency acquisition means for acquiring a dominant frequency which is a frequency of a dominant frequency component of vibration input to the structure from the foundation side, and the structure Among the predetermined natural frequencies of the structure, the cutoff natural frequency determined by the rigidity of the predetermined layer and the inertial mass of the variable rotating inertial mass damper to the nearest natural frequency that is closest to the acquired dominant frequency Synchronize Sea urchin, characterized in that it comprises a control means for controlling the inertial mass of the variable rotational inertia mass damper, a.

  According to this configuration, the variable rotation inertia mass damper having the rotation mass is provided in the predetermined layer of the structure, and the displacement of the structure transmitted to the variable rotation inertia mass damper due to the vibration of the structure is rotated. It is converted into mass rotation. In the variable rotational inertia mass damper, the inertial mass generated with the rotation of the rotational mass can be changed.

  Furthermore, the dominant frequency, which is the frequency of the dominant frequency component of the vibrations input to the structure from the foundation side, is acquired by the dominant frequency acquisition means, and during the vibration of the structure, a plurality of predetermined natural vibrations of the structure. The inertia of the variable rotational inertial mass damper is such that the cutoff frequency determined by the stiffness of the predetermined layer and the inertial mass of the variable rotational inertial mass damper is synchronized with the nearby natural frequency closest to the acquired dominant frequency. The mass is controlled by the control means. Thus, during the vibration of the structure, among the plurality of natural frequencies of the structure, the cutoff frequency is tuned to the nearby natural frequency closest to the dominant frequency of the input vibration from the base side, The deformation of the predetermined layer due to the vibration of the nearby natural frequency can be increased, and the transmission of the vibration of the nearby natural frequency to the layer above the predetermined layer of the structure can be cut off. Can be suppressed appropriately.

  As described above, according to the present invention, it is possible to appropriately control the inertial mass of the variable rotation inertial mass damper according to the current vibration input to the structure from the foundation side. The vibration of the layer above the predetermined layer of the provided structure can be suppressed appropriately. Note that “tuning” in the present invention includes adjusting the cutoff frequency to be substantially the same as the nearby natural frequency in addition to adjusting the cutoff frequency to be the same as the nearby natural frequency.

  According to a third aspect of the present invention, there is provided the vibration suppressing device for a structure according to the first or second aspect, wherein the variable rotation inertial mass damper includes a cylinder to which an interlayer displacement of a predetermined layer accompanying vibration of the structure is transmitted, The interior is partitioned into a first fluid chamber and a second fluid chamber filled with a working fluid, and an interlayer displacement of a predetermined layer accompanying the vibration of the structure is transmitted to slide in the cylinder in the axial direction. The first and second fluid chambers that bypass the piston and communicate with the first and second fluid chambers, are filled in the working fluid, and are provided in the first communication passage. A flow conversion mechanism that converts the flow of the working fluid into a rotary motion of the rotary mass and a first communication passage are provided in parallel, bypass the piston, communicate with the first and second fluid chambers, and are filled with the working fluid. The second communication path and the second communication path And a flow rate adjusting mechanism for adjusting the flow rate of the working fluid flowing through the second communication path, and the control means controls the inertial mass of the variable rotary inertial mass damper during the vibration of the structure. It is characterized by adjusting the flow rate of the working fluid flowing through the second communication path via the flow rate adjusting mechanism.

  According to this configuration, the displacement of the predetermined layer accompanying the vibration of the structure is transmitted to the cylinder and the piston, so that the piston slides in the cylinder and moves to one side of the first and second fluid chambers. Then, the working fluid in one of the fluid chambers is pushed out by the piston to the first communication passage, so that the working fluid flows toward the other fluid chamber in the first communication passage. The flow of the working fluid is converted into a rotary motion of the rotary mass by the flow conversion mechanism. The second communication path is provided in parallel with the first communication path, and the flow rate of the working fluid flowing through the second communication path is adjusted by the flow rate adjusting mechanism.

  Since the second communication passage bypasses the piston and is provided in parallel with the first communication passage, when the flow rate of the working fluid in the second communication passage changes, the first communication passage moves accordingly. The flow rate of the working fluid in the communication path changes. Therefore, by adjusting the flow rate of the working fluid in the second communication path via the flow rate adjusting mechanism, the flow rate of the working fluid in the first communication path can be changed, and the rotation amount of the rotary mass can be changed. Thereby, the inertial mass of the variable rotational inertial mass damper generated along with the rotation of the rotary mass can be changed. Further, according to the above-described configuration, during the vibration of the structure, the control of the inertial mass of the variable rotation inertial mass damper by the control unit adjusts the flow rate of the working fluid flowing through the second communication path via the flow rate adjusting mechanism. Therefore, it is possible to appropriately control the inertial mass of the variable rotational inertial mass damper in accordance with the effect of the invention according to claim 1 or 2, that is, the instantaneous vibration input to the structure. The effect that the vibration of the layer above the predetermined layer of the structure provided with the mass damper can be appropriately suppressed can be effectively obtained.

  According to a fourth aspect of the present invention, in the vibration suppressing device for a structure according to the third aspect, the flow rate adjusting mechanism has an electric pump for sending the working fluid in the second communication path.

  According to this configuration, the flow of the working fluid can be forcibly generated in the second communication path by driving the electric pump. Further, by controlling the electric pump, the flow rate of the working fluid in the second communication path is directly adjusted, and the flow rate of the working fluid in the first communication path changes accordingly, so that the variable rotation inertia mass damper The inertial mass can be appropriately changed.

  According to a fifth aspect of the present invention, in the vibration suppressing device for a structure according to the third or fourth aspect, the piston is opened when the pressure of the working fluid in the first fluid chamber reaches the first predetermined pressure. A first relief valve that causes the first and second fluid chambers to communicate with each other, and a valve that is opened when the pressure of the working fluid in the second fluid chamber reaches a second predetermined pressure, and the second and first fluid chambers are connected to each other. A second relief valve for communication is provided.

  According to this configuration, the piston is provided with the first and second relief valves, and the first relief valve opens when the pressure of the working fluid in the first fluid chamber reaches the first predetermined pressure, The second relief valve is opened when the pressure of the working fluid in the second fluid chamber reaches the second predetermined pressure, and the first and second fluid chambers are mutually connected by opening the first or second relief valve. Communicated. Accordingly, it is possible to prevent the pressure of the working fluid in the first and second fluid chambers from being excessively increased and appropriately limit the axial force acting on the cylinder and the piston.

  According to a sixth aspect of the present invention, in the vibration suppression device for a structure according to the first or second aspect, the variable rotational inertia mass damper includes a cylinder to which an interlayer displacement of a predetermined layer accompanying vibration of the structure is transmitted, The interior is partitioned into a first fluid chamber and a second fluid chamber filled with a working fluid, and an interlayer displacement of a predetermined layer accompanying the vibration of the structure is transmitted to slide in the cylinder in the axial direction. The piston configured as above, bypassing the piston, communicating with the first and second fluid chambers, and converting the pressure energy of the working fluid flowing in the communicating passage and the working fluid flowing in the communicating passage into rotational energy In addition, a variable displacement fluid pressure motor configured to be able to change the displacement volume, an actuator for changing the displacement volume of the fluid pressure motor, and a rotary energy converted by the fluid pressure motor The control means controls the inertial mass of the variable rotary inertial mass damper during the vibration of the structure, and adjusts the displacement volume of the fluid pressure motor via the actuator. It is characterized by performing by doing.

  According to this configuration, the displacement of the predetermined layer accompanying the vibration of the structure is transmitted to the cylinder and the piston, so that the piston slides in the cylinder and moves to one side of the first and second fluid chambers. Then, the working fluid in the one fluid chamber is pushed out to the communication passage by the piston, so that the working fluid flows toward the other fluid chamber in the communication passage. The pressure energy of the working fluid is converted into rotational energy by a variable displacement type fluid pressure motor, and the rotational mass is rotated by transmitting the converted rotational energy to the rotational mass. Accordingly, an inertial mass corresponding to the rotational inertial mass of the rotary mass is generated. In this case, by changing the displacement volume of the fluid pressure motor (geometric volume displaced per rotation of the fluid pressure motor), the amount of rotation of the rotating mass with respect to the pressure energy of the same working fluid can be changed. Thus, the inertial mass of the variable rotational inertial mass damper generated with the rotation of the rotary mass can be changed.

  Further, according to the above-described configuration, during the vibration of the structure, the control of the inertial mass of the variable rotation inertial mass damper by the control unit is performed by adjusting the displacement volume of the fluid pressure motor via the actuator. The variable rotational inertial mass damper is provided by appropriately controlling the inertial mass of the variable rotational inertial mass damper according to the effect of the invention according to claim 1 or 2, that is, according to the current vibration input to the structure. The effect that the vibration of the layer above the predetermined layer of the structure can be appropriately suppressed can be effectively obtained.

  According to a seventh aspect of the present invention, in the vibration suppression device for a structure according to the first or second aspect, the variable rotational inertia mass damper uses the interlayer displacement of the predetermined layer transmitted along with the vibration of the structure as the rotational power. A conversion mechanism for conversion, and a continuously variable transmission mechanism configured to transmit the rotational power converted by the conversion mechanism to the rotary mass in a shifted state and to change the transmission gear ratio steplessly, The control means controls the inertial mass of the variable rotation inertial mass damper by setting the transmission ratio of the transmission mechanism during the vibration of the structure.

  According to this configuration, the interlayer displacement of the predetermined layer transmitted along with the vibration of the structure is converted into a rotational motion by the conversion mechanism. The converted rotational power is transmitted to the rotary mass while being shifted by the continuously variable transmission mechanism, whereby the rotary mass rotates. The speed ratio of the speed change mechanism can be changed steplessly. In this way, the rotational power from the conversion mechanism is transmitted to the rotary mass in a state of stepless shifting, and the rotational mass of the rotary mass is changed by changing the rotation amount of the rotary mass by setting the gear ratio of the transmission mechanism. It is possible to continuously change the inertial mass of the variable rotational inertial mass damper that is generated as the motor rotates.

  Further, during the vibration of the structure, the control unit controls the inertial mass of the variable rotation inertial mass damper by setting the transmission ratio of the transmission mechanism. As described above, the effect of the invention according to claim 1 or 2, that is, the inertial mass of the variable rotation inertial mass damper can be appropriately controlled according to the current vibration input to the structure, so that the variable rotation inertial mass damper can be controlled. The effect that the vibration of the layer above the predetermined layer of the provided structure can be appropriately suppressed can be effectively obtained.

  According to an eighth aspect of the present invention, in the vibration suppression device for a structure according to the second aspect, the variable rotation inertial mass damper converts the interlayer displacement of the predetermined layer transmitted along with the vibration of the structure into rotational power. A conversion mechanism, and a stepped transmission mechanism that transmits the rotational power converted by the conversion mechanism to the rotary mass in a state where the rotational power is changed at one transmission ratio selected from a plurality of predetermined transmission ratios. The transmission ratio of the plurality of cutoff frequencies obtained corresponding to each of the plurality of transmission ratios when each of the plurality of transmission ratios is selected during vibration of the structure, The control means is cut off by selecting a gear ratio corresponding to the natural frequency near the structure from a plurality of gear ratios of the transmission mechanism. So that the frequency tunes to the nearby natural frequency And controlling the inertial mass of the variable rotational inertial mass damper.

  According to this configuration, the interlayer displacement of the predetermined layer transmitted along with the vibration of the structure is converted into a rotational motion by the conversion mechanism. The converted rotational power is transmitted to the rotating mass by a stepped transmission mechanism in a state of shifting with one gear ratio selected from a plurality of predetermined gear ratios, whereby the rotating mass rotates. As described above, the rotational power from the conversion mechanism is transmitted to the rotary mass while being shifted at one of the plurality of gear ratios, and the rotation amount of the rotary mass is reduced by selecting the gear ratio of the transmission mechanism. By changing it, the inertial mass of the variable rotary inertial mass damper generated with the rotation of the rotary mass can be changed.

  In this case, the plurality of transmission ratios have a plurality of cutoff frequencies obtained corresponding to each of the plurality of transmission ratios when each of the plurality of transmission ratios is selected during vibration of the structure. Are set so as to be tuned corresponding to a plurality of predetermined natural frequencies. Further, the control means selects a gear ratio corresponding to the near natural frequency of the structure from a plurality of gear ratios, so that the cutoff frequency is synchronized with the near natural frequency. The inertial mass is controlled. As described above, the variable rotational inertial mass damper can be provided by appropriately controlling the inertial mass of the variable rotational inertial mass damper according to the effect of the invention according to the second aspect, that is, the instantaneous vibration input to the structure. In addition, it is possible to effectively obtain an effect that vibrations of layers above the predetermined layer of the structure can be appropriately suppressed.

  The invention according to claim 9 is the vibration suppression device for a structure according to claim 7 or 8, wherein the speed change mechanism has a rotating shaft to which the rotational power converted by the conversion mechanism is transmitted in a shifted state, The rotating mass is further provided with a friction material formed between the rotating shaft and the inner peripheral surface of the fitting hole, and the rotating mass is connected to the rotating shaft via the friction material. It is characterized by being.

  According to this configuration, the rotational power converted by the conversion mechanism is transmitted to the rotating shaft of the speed change mechanism in a shifted state, and the rotating mass has a friction material fitted between the fitting hole and the rotating shaft. Via the rotary shaft. For this reason, the friction coefficient of the friction material is set so that the rotation mass and / or the rotation shaft slide against the friction material when the rotational torque of the rotation mass becomes very large due to the vibration of the structure being very large. By setting, the inertial force due to the inertial mass generated with the rotation of the rotary mass can be limited.

It is sectional drawing which shows the variable rotation inertial mass damper of the vibration suppression apparatus by 1st Embodiment of this invention. It is sectional drawing which follows the II-II line of FIG. It is sectional drawing which follows the III-III line of FIG. It is a block diagram which shows the control apparatus etc. of the vibration suppression apparatus by 1st Embodiment. It is a figure which shows schematically the variable rotation inertial mass damper of FIG. 1 with a part of building which applied this. It is a model figure which shows the variable rotation inertia mass damper and building of FIG. It is sectional drawing which shows the operation | movement condition in the 1st operation mode of a variable rotation inertial mass damper. It is sectional drawing which shows the operation | movement condition in the 2nd operation mode of a variable rotation inertial mass damper. It is a flowchart which shows the tuning control process performed by the control apparatus of FIG. (A) The relationship between the frequency of seismic motion input to the building to which the vibration suppression device of the present invention is applied and the acceleration response magnification of the building with respect to the input, (b) The relationship between the frequency of seismic motion and the Fourier amplitude spectrum of the seismic motion , (C) The relationship between the frequency of seismic motion and the Fourier amplitude spectrum of the building response, for each case where the dominant frequency of seismic motion is equal to the secondary natural frequency of the building before installation of the vibration suppression device, (D) The relationship between the frequency of the earthquake motion and the acceleration response magnification of the building to the input, (e) the relationship between the frequency of the earthquake motion and the Fourier amplitude spectrum of the earthquake motion, and (f) the frequency of the earthquake motion and the Fourier amplitude spectrum of the building response. For the case where the prevailing frequency of ground motion is a predetermined frequency greater than the secondary natural frequency of the building before installation of the vibration suppression device, It is to figure. (A) The relationship between the frequency of seismic motion input to the building to which the conventional vibration suppression device is applied and the acceleration response magnification of the building to the input, (b) The relationship between the frequency of seismic motion and the Fourier amplitude spectrum of the seismic motion, (C) The relationship between the frequency of seismic motion and the Fourier amplitude spectrum of the building response is shown for each case where the prevailing frequency of seismic motion is a predetermined frequency greater than the secondary natural frequency of the building before installation of the vibration suppression device. It is a figure, (d) The frequency of the earthquake motion input into the building to which the conventional vibration suppression device which tuned the natural frequency of the vibration isolation mechanism to the tertiary natural frequency of the building is applied, and the acceleration response of the building to the input The relationship between the magnification, (e) the relationship between the frequency of the ground motion and the Fourier amplitude spectrum of the ground motion, and (f) the relationship between the frequency of the ground motion and the Fourier amplitude spectrum of the building response. And for when the frequency of dominant seismic motion equal to the secondary natural frequency of the pre-installation building vibration suppression device and illustrates respectively. It is a flowchart which shows the tuning control process performed with the control apparatus of the vibration suppression apparatus by 2nd Embodiment of this invention. It is sectional drawing which shows the variable rotation inertial mass damper of the vibration suppression apparatus by 3rd Embodiment of this invention. It is a block diagram which shows the control apparatus etc. of the vibration suppression apparatus by 3rd Embodiment. It is a figure which shows schematically the variable rotation inertial mass damper of FIG. 13 with a part of building which applied this. It is a flowchart which shows the tuning control process performed by the control apparatus of FIG. It is sectional drawing which shows the variable rotation inertia mass damper of the vibration suppression apparatus by 4th Embodiment of this invention. It is sectional drawing which shows the variable rotation inertial mass damper of the vibration suppression apparatus by 5th Embodiment of this invention. It is a block diagram which shows the control apparatus etc. of the vibration suppression apparatus by 5th Embodiment. It is a figure which shows schematically the variable rotation inertial mass damper of FIG. 18 with a part of building which applied this. It is a flowchart which shows the tuning control process performed with the control apparatus of FIG. It is a flowchart which shows the tuning control process performed with the control apparatus of the vibration suppression apparatus by 6th Embodiment of this invention. It is sectional drawing which shows the variable rotation inertial mass damper of the vibration suppression apparatus by 7th Embodiment of this invention. It is a block diagram which shows the control apparatus etc. of the vibration suppression apparatus by 7th Embodiment. It is a figure which shows schematically the variable rotation inertial mass damper of FIG. 23 with a part of building which applied this. It is a flowchart which shows the tuning control process performed with the control apparatus of FIG. It is a flowchart which shows the tuning control process performed with the control apparatus of the vibration suppression apparatus by 8th Embodiment of this invention. It is a model figure which shows a variable rotation inertia mass damper and a building in the case where two layers consisting of one layer and two layers of a building are set as predetermined layers.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. The vibration suppression device according to the first embodiment of the present invention includes the variable rotational inertia mass damper 1 shown in FIG. 1 and is applied to a high-rise building B (see FIG. 5) having a plurality of layers. This building B has a ramen structure in which a plurality of columns and beams are combined in a cross beam shape, and is erected on a foundation (not shown). The variable rotary inertia mass damper 1 is configured to be able to continuously change an inertia mass generated as a rotary mass 21 (described later) rotates. As shown in FIG. The piston 3 is slidably provided in the axial direction, the piston rod 4 is integral with the piston 3, and the first communication path 5 and the second communication path 6 are connected to the cylinder 2.

  The cylinder 2 integrally includes a cylindrical peripheral wall 2a and disk-shaped first end walls 2b and second end walls 2c provided at both ends in the axial direction of the peripheral wall 2a. A space defined by the peripheral wall 2a, the first and second end walls 2b, 2c is partitioned by the piston 3 into a first fluid chamber 2d and a second fluid chamber 2e. The first and second fluid chambers 2d and 2e are filled with a viscous fluid HF. The viscous fluid HF is composed of a suitable fluid having viscosity, for example, silicone oil.

  Further, the first end wall 2b of the cylinder 2 is integrally provided with a convex portion 2f that protrudes outward in the axial direction, and the convex portion 2f is provided with a first joint via a universal joint. A fixture FL1 is provided. Further, a rod guide hole 2g is formed at the center of the second end wall 2c. The piston rod 4 is integrally connected to the piston 3 at one end, extends in the axial direction into the cylinder 2, and is liquid-tightly inserted into the rod guide hole 2g via a seal, and is externally attached to the second end wall 2c. It extends toward. The other end of the piston rod 4 is provided with a second fixture FL2 via a universal joint.

  Further, the outer peripheral surface of the piston 3 is in fluid-tight contact with the inner peripheral surface of the peripheral wall 2a of the cylinder 2 through a seal, and a plurality of axially penetrating outer end portions of the piston 3 penetrates in the axial direction. A first communication hole 3a and a second communication hole 3b (only one is shown) are formed. A first relief valve 11 is provided in the first communication hole 3a, and a second relief valve 12 is provided in the second communication hole 3b.

  The first relief valve 11 includes a valve body and a spring that biases the valve body in the valve closing direction. When the pressure of the viscous fluid HF in the first fluid chamber 2d is smaller than a predetermined upper limit value, When the first communication hole 3a is closed and the upper limit is reached, the first communication hole 3a is opened. As a result, the first and second fluid chambers 2d and 2e communicate with each other via the first communication hole 3a, and the pressure in the first fluid chamber 2d is released to the second fluid chamber 2e side.

  Similarly, the second relief valve 12 is configured by a valve body and a spring that biases the valve body in the valve closing direction, and the pressure of the viscous fluid HF in the second fluid chamber 2e is higher than the above upper limit value. When it is small, the second communication hole 3b is closed, and when the upper limit is reached, the second communication hole 3b is opened. Thereby, the first and second fluid chambers 2d and 2e communicate with each other through the second communication hole 3b, and the pressure in the second fluid chamber 2e is released to the first fluid chamber 2d side. In addition, you may set the upper limit of the 1st and 2nd relief valves 11 and 12 to a mutually different value.

  The first and second communication passages 5 and 6 are connected to the cylinder 2 so as to bypass the piston 3 and communicate with the first and second fluid chambers 2d and 2e, respectively, and are provided in parallel to each other. Yes. Moreover, the cross-sectional area of both 5 and 6 is set to a value smaller than the cross-sectional area of the cylinder 2, and the first and second fluid passages 2d and 2e are provided in the first and second communication passages 5 and 6, respectively. Similarly, the viscous fluid HF is filled. In FIG. 1, for convenience, the reference numerals of the viscous fluid HF in the first and second communication passages 5 and 6 are omitted.

  The variable rotary inertia mass damper 1 includes a gear motor M that converts the flow of the viscous fluid HF in the first communication path 5 into a rotational motion, a rotary mass 21 that is connected to the gear motor M, and a second communication path 6. Is further provided with a gear pump P for adjusting the flow rate of the viscous fluid HF flowing through the. The gear motor M is of a circumscribed gear type, and has a casing 22 and a first gear 23 and a second gear 24 accommodated in the casing 22. The gear motor M may be an internal gear type.

  The casing 22 is integrally provided in the central portion of the first communication path 5 and communicates with the first communication path 5 via two entrances 22a and 22b facing each other. The first and second gears 23 and 24 are each formed of a spur gear, are integrally provided on the first and second rotating shafts 25 and 26, and mesh with each other. Each of the first and second rotating shafts 25 and 26 extends horizontally in a direction orthogonal to the first communication path 5 and is rotatably supported by the casing 22. The first rotating shaft 25 protrudes outside the casing 22. (See FIG. 2). Further, the meshing portions of the first and second gears 23, 24 face the entrances 22 a, 22 b of the casing 22. Furthermore, the rotating mass 21 is coaxially and integrally provided at the portion of the first rotating shaft 25 protruding from the casing 22. The rotary mass 21 is made of a material having a relatively large specific gravity, such as iron, and is formed in a disk shape.

  The gear pump P is of the external gear type, and has a flow rate adjusting motor 31 that is a power source, a casing 32, and a first gear 33 and a second gear 34 that are accommodated in the casing 32. The gear pump P may be an internal gear type. The casing 32 is integrally provided in the central portion of the second communication path 6 and communicates with the second communication path 6 through two entrances 32a and 32b facing each other. Each of the first and second gears 33 and 34 is a spur gear, and is provided integrally with the first and second rotating shafts 35 and 36 and meshes with each other. Each of the first and second rotating shafts 35 and 36 extends horizontally in a direction orthogonal to the second communication path 6 and is rotatably supported by the casing 32, and the first rotating shaft 35 projects outside the casing 32. (See FIG. 3). Further, the meshing portions of the first and second gears 33 and 34 face the entrances 32 a and 32 b of the casing 32.

  The flow rate adjustment motor 31 is constituted by a DC motor that can rotate forward and backward, for example. The rotor (not shown) of the flow rate adjusting motor 31 is coaxially connected to the portion of the first rotating shaft 35 protruding from the casing 32, and rotates the first rotating shaft 35 and the first gear 33 integrally. The flow rate adjusting motor 31 is connected to a power source 52 via a control device 51 (see FIG. 4) described later, and its operation is controlled by the control device 51. The power source 52 is constituted by a battery, for example.

  Further, as shown in FIG. 5, the first fixture FL1 and the second fixture FL2 of the variable rotation inertia mass damper 1 are respectively attached to the first coupling member EN1 and the second coupling member EN2. These first and second connecting members EN1 and EN2 are made of steel material having rigidity much higher than the rigidity of each layer of the building B, and support the lower beam BD (the predetermined layer PF) of the predetermined layer PF of the building B. Beam) and an upper beam BU (a beam that supports a layer one layer above the predetermined layer PF), and extends upward from the lower beam BD and downward from the upper beam BU.

  With the above configuration, the cylinder 2 and the piston rod 4 of the variable rotation inertial mass damper 1 are connected to the lower beam BD and the upper beam BU via the first and second connection members EN1 and EN2, respectively. The inertia mass damper 1 is provided in a predetermined layer PF of the building B and extends horizontally between the upper and lower beams BU and BD. In FIG. 5, illustration of some components such as the first and second communication passages 5 and 6 is omitted for convenience. FIG. 6 is a model diagram showing the building B and the variable rotary inertia mass damper 1. As shown in the figure, in the present embodiment, the predetermined layer PF is, for example, the lowermost layer (one layer) of the building B.

  Next, the operation of the variable rotation inertia mass damper 1 will be described. As the building B vibrates, when a horizontal relative displacement (interlayer displacement of the predetermined layer PF) occurs between the upper and lower beams BU, BD, this relative displacement is caused by the first and second connecting members EN1, EN2. , The cylinder 2 and the piston rod 4 are moved relative to each other in the axial direction, and the piston 3 slides in the cylinder 2.

  In this case, when the piston 3 moves to the first fluid chamber 2d side (left side in FIG. 1), a part of the viscous fluid HF in the first fluid chamber 2d is pushed out by the piston 3 to the first communication path 5. Thus, the viscous fluid HF flows in the first communication passage 5 toward the second fluid chamber 2e (right side). On the contrary, when the piston 3 moves to the second fluid chamber 2e side (right side), a part of the viscous fluid HF in the second fluid chamber 2e is pushed out to the first communication passage 5 by the piston 3. As a result, the viscous fluid HF flows in the first communication passage 5 toward the first fluid chamber 2d (left side).

  The flow of the viscous fluid HF is converted into a rotational motion by the gear motor M, the first and second gears 23 and 24 rotate, and the first rotary shaft 25 and the rotary mass 21 integrated with the first gear 23 rotate. To do.

  Further, as described above, as the rotary mass 21 rotates, the inertial mass Md of the variable rotary inertial mass damper 1 is generated. The inertial mass Md is an inertial mass in the axial direction with respect to an external force caused by vibration input to the cylinder 2 and the piston 3, and is an inertial mass by the rotating mass 21 (an inertial mass (equivalent mass) based on the rotating inertial mass of the rotating mass 21). Mr and inertia mass Mh due to the viscous fluid HF in the first communication path 5 are included. As will be described below, the inertial mass Mr by the rotating mass 21 at this time controls the operation of the gear pump P via the flow rate adjusting motor 31 to adjust the flow rate of the viscous fluid HF in the second communication path 6. Is changed continuously. FIG. 7 shows that when the piston 3 moves toward the first fluid chamber 2d, the flow rate adjusting motor 31 is rotationally driven in the clockwise direction in FIG. The situation (hereinafter referred to as “first operation mode”) is flowing to the same first fluid chamber 2d side. In FIG. 7, for the sake of convenience, reference numerals of some components are omitted.

  In the first operation mode, the volume (flow rate) V1 of the viscous fluid HF that flows along with the movement of the piston 3 and the volume (flow rate) of the viscous fluid HF that is sent by the gear pump P and flows in the second communication path 6 are flown. ) Since the sum with V2 becomes the volume (flow rate) V of the viscous fluid HF that flows in the first communication passage 5 and flows into the gear motor M, the rotation amount of the rotary mass 21 increases.

Moreover, the inertial mass Mr by the rotating mass 21 at this time is calculated | required as follows. First, from the above relationship, the following equation (1) is established.
V = V1 + V2 (1)
In the following, V1 is referred to as “piston volume”, V2 is referred to as “pump volume”, and V is referred to as “motor volume”. The piston volume V1 is expressed by the following formula (2), and the pump volume V2 is expressed by the following formula (3).
V1 = Ap · X (2)
V2 = vmd · n (3)
Here, Ap is the pressure receiving area of the piston 3 with respect to the viscous fluid HF, and when the piston 3 is moving toward the first fluid chamber 2d, it is the cross-sectional area of the piston 3, and the piston 3 is in the second fluid chamber 2e. When moving to the side, the cross-sectional area of the piston 3 is subtracted from the cross-sectional area of the piston 3. The pressure receiving area Ap of the piston 3 may be set to the cross sectional area of the piston 3 regardless of the moving direction of the piston 3, or to a value obtained by subtracting the cross sectional area of the piston rod 4 from the cross sectional area of the piston 3. . X is the amount of movement of the piston 3, vmd is the delivery volume (displacement volume) per rotation of the flow rate adjustment motor 31, and n is the number of rotations of the flow rate adjustment motor 31.

From the above equations (1) and (2), the movement amount X of the piston 3 in the first operation mode is expressed by the following equation (4).
X = V1 / Ap = (V−V2) / Ap (4)

Further, assuming that the gear motor M rotates once, assuming that the motor volume V required for one rotation is vm (displacement volume), and the pump volume V2 at this time is vm2, these vm and vm2 are expressed by the formula (4). By substituting in V and V2, the movement amount Xm of the piston 3 at this time is expressed by the following equation (5).
Xm = (vm−vm2) / Ap (5)

The movement amount Xm of the piston 3 corresponds to the lead length (Ld) of the ball screw in the mass damper using the ball screw mechanism. Therefore, the inertial mass (equivalent mass) Mr by the rotating mass 21 in the first operation mode is expressed by the following equation (6).
^{Mr = (2π / Xm) 2} · md · D 2/8
= {(2π · Ap) / (vm-vm2)} 2 · md · D 2/8 ...... (6)
Here, md is a substantial amount of the rotating mass 21, and D is an outer diameter of the rotating mass 21.

  As is apparent from the equation (6), the inertial mass Mr in the first operation mode increases by an amount corresponding to the pump volume V2 (= vm2). Therefore, the inertial mass Mr can be changed by changing the pump volume V2 by adjusting the rotation speed of the flow rate adjusting motor 31.

On the other hand, with respect to the first operation mode described above, FIG. 8 shows that the second flow rate adjustment motor 31 is rotated counterclockwise in FIG. 8 when the piston 3 moves toward the first fluid chamber 2d. The situation is shown in which the viscous fluid HF in the communication path 6 flows toward the second fluid chamber 2e, opposite to the piston 3 (hereinafter referred to as “second operation mode”). In FIG. 8, for the sake of convenience, the reference numerals of some components are omitted. In the second operation mode, the difference between the piston volume V1 and the pump volume V2 becomes the motor volume V (the following equation (1) ′), and thus the rotation amount of the rotary mass 21 is reduced.
V = V1-V2 (1) '
From this relationship, the movement amount X of the piston 3 in the second operation mode is expressed by the following equation (4) ′ by replacing (V−V2) in the equation (4) with (V + V2).
X = V1 / Ap = (V + V2) / Ap (4) ′

Further, the movement amount Xm of the piston 3 when the gear motor M makes one rotation is expressed by the following equation (5) ′ by replacing (vm−vm2) in the equation (5) with (vm + vm2).
Xm = (vm + vm2) / Ap (5) ′

Therefore, the inertial mass Mr by the rotating mass 21 in the second operation mode is expressed by the following equation (6) ′.
^{Mr = (2π / Xm) 2} · md · D 2/8
= {(2π · Ap) / (vm + vm2)} 2 · md · D 2/8
...... (6) '

  As is clear from this equation (6) ', the inertial mass Mr by the rotating mass 21 in the second operation mode decreases by an amount corresponding to the pump volume V2 (= vm2). Therefore, the inertial mass Mr can be changed by changing the pump volume V2 by adjusting the rotation speed of the flow rate adjusting motor 31.

It should be noted that the pump volume vm2 is positive or negative, and the case where the flow direction of the viscous fluid HF in the second communication passage 6 is the same as the movement direction of the piston 3 (first operation mode) is negative, and the opposite case (second operation) When the mode) is a positive value, the above formulas (6) and (6) ′ are integrated into the formula (6) ′. Further, when Expression (6) ′ is expressed with respect to the pump volume vm2, the following Expression (7) is obtained.
vm2 = {(2π · Ap) / sqrt [8 Mr / (md · D ² )]} − vm
...... (7)

Further, the rotational speed n of the flow rate adjusting motor 31 necessary for causing the viscous fluid HF having the pump volume vm2 to flow is expressed by the following equation (8) from the equation (3).
n = vm2 / vmd (8)

  As described above, in the variable rotation inertial mass damper 1, by operating the gear pump P, the flow of the viscous fluid HF is forcibly generated in the second communication path 6, and the rotational speed n of the flow rate adjusting motor 31 is increased. Is controlled to adjust the pump volume V2 (the flow rate of the viscous fluid HF in the second communication path 6). Then, the motor volume V (the flow rate of the viscous fluid HF in the first communication path 5) is changed by the pump volume V2 with respect to the piston volume V1 (the flow rate of the viscous fluid HF accompanying the movement of the piston 3). In response to this, the amount of rotation of the rotating mass 21 is changed, whereby the inertial mass Mr by the rotating mass 21 is changed, and consequently, the inertial mass Md of the variable rotating inertial mass damper 1 including the inertial mass Mr is changed.

The inertial mass Mh due to the viscous fluid HF in the first communication path 5 is expressed by Mh = ρ · Ae1 · l1 · α1 ² , and tends to be very small compared to the inertial mass Mr due to the rotating mass 21. . Here, ρ is the density of the viscous fluid HF, Ae1 and l1 are the cross-sectional area and length of the first communication path 5, and α1 is the pressure receiving area of the piston 3 with respect to the cross-sectional area Ae1 of the first communication path 5, respectively. It is the ratio of Ap.

  Further, by switching the rotation direction of the flow rate adjusting motor 31, the flow direction of the viscous fluid HF in the second communication path 6 is the same direction (first operation mode) as the movement direction of the piston 3 or the opposite direction (second operation). By switching to (mode), the motor volume V can be increased or decreased with respect to the piston volume V1. Thereby, the change range of the inertial mass Mr by the rotation mass 21 is expanded.

  Further, as the piston 3 slides in the cylinder 2 due to the vibration of the building B, a pressure difference of the viscous fluid HF is generated between the first and second fluid chambers 2d and 2e. 3 acts as a resistance force, and acts to attenuate the relative displacement between the upper and lower beams BU, BD via the first and second connecting members EN1, EN2. This damping force becomes larger as the inertial mass Mr by the rotating mass 21 is increased by the above control.

  The vibration suppression device further includes a control device 51, a power source 52, and a seismometer 53 shown in FIG. The control device 51 is configured by a combination of a CPU, a RAM, a ROM, an I / O interface, a DC / DC converter, and the like. The seismometer 53 is composed of, for example, an acceleration sensor, and is provided on a foundation (not shown) on which the building B is erected. The seismometer 53 measures vibrations (earthquake) input to the building B from the foundation side. A measurement signal is input to the control device 51.

Further, the control device 51 repeatedly executes the tuning control process shown in FIG. 9 at predetermined time intervals in accordance with the input measurement signal and in accordance with the control program stored in the ROM. In this tuning control process, the inertial mass Md is controlled such that the cutoff frequency fcu determined by the inertial mass Md of the variable rotary inertial mass damper 1 and the rigidity θs of the predetermined layer PF of the building B is synchronized with a dominant frequency fcp described later. Therefore, the operation of the flow rate adjusting motor 31 is controlled. Here, the rigidity θs of the predetermined layer PF is the rigidity against the horizontal interlayer displacement of the building B, corresponds to the spring constant, and is set to a predetermined value. The cutoff frequency fcu is expressed by the following equation (9). expressed. Hereinafter, the tuning control process will be described with reference to FIG.
fcu = sqrt (θs / Md) / 2π (9)

  As described above, the inertial mass Mh due to the viscous fluid HF contained in the inertial mass Md of the variable rotational inertial mass damper 1 tends to be very small as compared with the inertial mass Mr due to the rotational mass 21. Then, the inertial mass Mh is ignored, and the inertial mass Mr of the rotating mass 21 is regarded as the inertial mass Md of the variable rotating inertial mass damper 1 so that the operation of the flow rate adjusting motor 31 is controlled.

  First, in step 1 of FIG. 9 (illustrated as “S1”, the same applies hereinafter), it is determined whether or not the building B is vibrating. This determination is based on the measurement signal of the seismometer 53, and it is determined that the building B is oscillating when the earthquake motion represented by the measurement signal is greater than a predetermined value. If the answer is NO and the building B is not vibrating, the current process is terminated.

  On the other hand, if the answer to step 1 is YES and the building B is oscillating, the dominant frequency fcp, which is the frequency of the dominant frequency component of the vibrations input to the building B from the foundation side, is calculated (step 2). ). The calculation of the dominant frequency fcp is performed as follows, for example. That is, the seismic motion measured by the seismometer 53 is subjected to frequency analysis by fast Fourier transform, whereby the Fourier amplitude spectrum of the seismic motion is calculated for each seismic motion frequency (frequency). Then, the calculated plurality of Fourier amplitude spectra are compared with each other, and the frequency corresponding to the largest Fourier amplitude spectrum among them is set (calculated) as the dominant frequency fcp. The predetermined time, which is the execution cycle of the tuning control process, is set to a time sufficient to execute this frequency analysis. The Fourier amplitude spectrum calculation method described above is well known and will not be described here. For example, it is disclosed in “Introduction to new ground motion spectrum analysis author: Nobuhiko Osaki Kashima Press”.

Next, using the calculated dominant frequency fcp and the rigidity θs of the predetermined layer PF, the inertial mass Mds for this control is calculated by the following equation (10) (step 3). This formula (10) expands the formula (9) (fcu = sqrt (θs / Md) / 2π) representing the cutoff frequency fcu with respect to the inertial mass Md of the variable rotational inertial mass damper 1, and Md is expressed as Mds. And fcu is replaced with fcp. The rigidity θs of the predetermined layer PF is stored in the ROM of the control device 51, and is read from the ROM in the calculation in step 3.
Mds = θs / (fcp · 2π) ² (10)

  Next, by substituting the calculated inertial mass Mds into Mr in the equation (7), the pump volume vm2 that is the flow rate of the viscous fluid HF in the second communication path 6 is calculated (step 4). In this equation (7), the pressure receiving area Ap of the piston 3, the substantial amount md of the rotary mass 21, the outer diameter D of the rotary mass 21, and the motor volume vm required for one rotation of the gear motor M are all predetermined values. , Stored in the ROM, and read from the ROM in the calculation in step 4. Next, the rotational speed n of the flow rate adjusting motor 31 is calculated according to the equation (8) according to the calculated pump volume vm2 (step 5). The delivery volume vmd per rotation of the flow rate adjusting motor 31 in the equation (8) is a predetermined value, stored in the ROM, and read from the ROM in the calculation of step 5. Next, by outputting a drive signal based on the calculated rotation speed n, the flow rate adjustment motor 31 is driven (step 6), and the current process is terminated.

  By driving the flow rate adjusting motor 31 in this way, the inertia mass Mr by the rotary mass 21 regarded as the inertia mass Md of the variable rotary inertia mass damper 1 is controlled to the inertia mass Mds calculated in step 3. As a result, the cutoff frequency fcu determined by the inertial mass Md and the rigidity θs of the predetermined layer PF is controlled to be the same as the dominant frequency fcp. The drive signal is obtained in advance by experiments or the like so as to obtain the rotational speed n of the flow rate adjusting motor 31, and is stored in the ROM. Further, the tuning control process including steps 1 to 6 is repeatedly executed at predetermined time intervals as described above.

  Next, an operation example of the tuning control process described above will be described with reference to FIG. FIG. 10A shows the relationship between the frequency of seismic motion input to the building B (hereinafter referred to as “earthquake frequency”) fe and the acceleration response magnification (hereinafter referred to as “response magnification”) RM of the building B with respect to the input. (B) shows the relationship between the seismic motion frequency fe and the Fourier amplitude spectrum (hereinafter referred to as “seismic motion spectrum”) SE of the seismic motion, and FIG. 10 (c) shows the seismic motion frequency fe and The relationship with the Fourier amplitude spectrum (hereinafter referred to as “building vibration spectrum”) SB of the response is shown for each case where the dominant frequency fcp is equal to the secondary natural frequency of the building B before installation of the vibration suppression device. In FIG. 10, fe2 is a frequency equal to the secondary natural frequency of the building B before installation of the vibration suppressing device.

  10 (d) shows the relationship between the seismic motion frequency fe and the response magnification RM, FIG. 10 (e) shows the relationship between the seismic motion frequency fe and the seismic motion spectrum SE, and FIG. 10 (f) shows the seismic motion frequency fe. The relationship with the building vibration spectrum SB is shown for each case where the dominant frequency fcp is a predetermined frequency feA that is greater than the frequency fe2.

  As described with reference to FIG. 9, in the tuning control process, the dominant frequency fcp (frequency of the frequency component of the seismic motion input to the building B) is calculated (step 2), and the cutoff frequency fcu is calculated. The inertial mass Md of the variable rotary inertial mass damper 1 including the inertial mass Mr by the rotary mass 21 is controlled so as to be the same as the dominant frequency fcp (steps 3 to 6).

  When the prevailing frequency fcp is equal to the secondary natural frequency of the building B before installation of the vibration suppression device, and the seismic motion spectrum SB of the frequency fe2 equal to the secondary natural frequency as shown in FIG. By executing the tuning control process described above, the response magnification RM at fe = fe2 becomes almost 0 as shown in FIG. 10A, and the building vibration at fe = fe2 as shown in FIG. 10C. The spectrum SB becomes almost 0, and the building vibration spectrum SB is small at any other frequency of the seismic vibration frequency fe.

  Further, when the dominant frequency fcp is equal to the predetermined frequency feA and the seismic motion spectrum SB of the predetermined frequency feA is relatively large as shown in FIG. 10E, the tuning control process described above is executed, so that FIG. As shown in FIG. 10, the response magnification RM at fe = feA becomes almost 0, and the building vibration spectrum SB at fe = feA becomes almost 0 as shown in FIG. As in the case of, the building vibration spectrum SB is small at any other frequency of the seismic vibration frequency fe.

  On the other hand, FIG. 11A to FIG. 11C show an operation example of the above-described conventional vibration suppression device. In these drawings, feC, feC2, feCA, RMC, SEC, and SBC are shown in FIG. Are parameters corresponding to fe, fe2, feA, RM, SE, and SB, respectively. As described above, in the conventional vibration suppression device, the inertial mass of the rotary inertia mass damper cannot be controlled, and the natural frequency of the vibration isolation mechanism compared with the cutoff frequency of the present embodiment is always installed in the vibration suppression device. Tune to the secondary natural frequency of the previous building.

  As a result, as shown in FIG. 11A, the acceleration response magnification RMC of the building at the frequency feC2 equal to the secondary natural frequency is substantially zero, whereas the predetermined frequency greater than the frequency feC2. The acceleration response magnification RMC of the building at feCA is relatively large. In this case, when the prevailing frequency of the ground motion input to the building is the predetermined frequency feCA, and the Fourier amplitude spectrum SEC of the ground motion at the predetermined frequency feCA is relatively large as shown in FIG. ), The Fourier amplitude spectrum SBC of the building at feC = feCA is relatively large, and it can be seen that the vibration of the frequency component of the predetermined frequency feCA of the building cannot be appropriately suppressed.

  11 (d) to 11 (f) show the operation when the natural frequency of the vibration isolation mechanism of the conventional vibration suppression device is synchronized with the tertiary natural frequency of the building before the vibration suppression device is installed. Examples are shown, and in these drawings, fec, fec2, RMc, SEc, and SBc are parameters corresponding to fe, fe2, RM, SE, and SB, respectively, in FIG. Further, fec3 is a frequency equal to the tertiary natural frequency of the building before the vibration suppressing device is installed. As shown in FIG. 11 (d) to FIG. 11 (f), the natural frequency of the vibration isolating mechanism of the conventional vibration suppressing device is always tuned to the third natural frequency of the building before the vibration suppressing device is installed. In this case, when the dominant frequency of the ground motion input to the building is equal to the secondary natural frequency of the building, the Fourier amplitude spectrum SBc of the building at fec = fec2 is relatively large, and before the vibration suppression device is installed. It can be seen that the vibration of the secondary natural frequency of the building cannot be appropriately suppressed.

  As described above, in the comparative example shown in FIG. 11, since the inertial mass of the rotary inertial mass damper cannot be controlled (variable), the natural frequency of the vibration isolation mechanism compared with the cutoff frequency of the present embodiment is always fixed. Therefore, it can be seen that the vibration of the building cannot be appropriately suppressed according to the current earthquake motion input to the building.

  On the other hand, in the first embodiment described above, by executing the tuning control process using the variable rotation inertial mass damper 1, the variable rotation inertial mass damper is changed according to the current earthquake motion input to the building B. It can be seen that the inertial mass Md of 1 can be appropriately controlled, and by extension, the vibration of the layer above the predetermined layer PF of the building B can be appropriately suppressed.

  As described above, according to the first embodiment, as described with reference to FIGS. 1 to 8, the variable rotation inertia mass damper 1 is provided in the predetermined layer PF of the building B, and the vibration of the building B is The relative displacement between the upper and lower beams BU and BD, that is, the interlayer displacement of the predetermined layer PF is transmitted to the variable rotation inertia mass damper 1. The transmitted interlayer displacement is converted into the rotational motion of the rotary mass 21 by the cylinder 2, the piston 3, the viscous fluid HF, the first communication path 5 and the gear motor M of the variable rotary inertia mass damper 1, whereby the rotary mass 21 is Rotate. The inertial mass Md of the variable rotary inertial mass damper 1 generated with the rotation of the rotary mass 21 is continuously changed by adjusting the flow rate of the viscous fluid HF in the second communication path 6 via the gear pump P. Is done.

  Further, as described with reference to FIG. 9, the dominant frequency fcp which is the frequency of the dominant frequency component of the vibrations input to the building B from the foundation side is calculated (step 2). Further, during vibration of the building B, more specifically, fcu is the same as fcp so that the cutoff frequency fcu determined by the rigidity θs of the predetermined layer PF and the inertial mass Md is synchronized with the calculated dominant frequency fcp. Thus, by adjusting the flow rate of the viscous fluid HF in the second communication passage 6 via the gear pump P, the inertial mass Md including the inertial mass Mr by the rotating mass 21 is controlled (steps 3 to 6). . Thus, by synchronizing the cutoff frequency fcu with the dominant frequency fcp, the deformation of the predetermined layer PF due to the vibration of the fcp is increased, and the transmission of the vibration of the fcp to the upper layer of the predetermined layer PF of the building B is cut off. As a result, the vibration of the upper layer can be appropriately suppressed. In this case, since the predetermined layer PF is set as the lowermost layer of the building B, it is possible to effectively obtain an effect that the vibration of the layer above the predetermined layer PF can be appropriately suppressed.

  When the pressure in the first fluid chamber 2d reaches the upper limit value, the first relief valve 11 is opened, and when the pressure in the second fluid chamber 2e reaches the upper limit value, the second relief valve 11 is opened. When the valve 12 is opened, the increased pressure of one of the first and second fluid chambers 2d, 2e is released to the other, so that the excessive pressure is prevented and the cylinder 2 and the piston 3 of the variable rotary inertia mass damper 1 are prevented. It is possible to appropriately limit the axial force acting on the.

  Further, the variable rotational inertia mass damper 1 basically includes a cylinder 2, a piston 3, first and second communication passages 5 and 6, a gear motor M is provided in the first communication passage 5, and a gear pump P is provided. Compared with the conventional variable rotational inertia mass damper disclosed in Japanese Patent Laid-Open No. 2016-151287 which requires a ball screw mechanism and a weight holding mechanism made up of a large number of members, because it has a structure provided in the two-way passage 6. Thus, the configuration is simple. For the same reason, the ball screw mechanism, the weight holding mechanism, and the actuator can all be easily assembled and adjusted and maintained as compared with the conventional variable rotational inertia mass damper accommodated in the casing. The workability at the time can be improved.

  In the first embodiment, the inertial mass Md of the variable rotation inertial mass damper 1 is controlled so that the cutoff frequency fcu is the same as the dominant frequency fcp, but the fcu is substantially the same as the fcp. In addition, it may be controlled. In that case, a value obtained by adding or subtracting a very small predetermined value to fcp is used instead of the dominant frequency fcp in the equation (10).

  Next, a vibration suppressing device according to a second embodiment of the present invention will be described. Compared with the first embodiment, this vibration suppressing device has the same hardware configuration as the variable rotation inertial mass damper 1 and the only difference is that the tuning control process shown in FIG. 12 is executed. In the tuning control process according to the second embodiment, unlike the case of the first embodiment, the inertial mass Md of the variable rotary inertial mass damper 1 is set so that the cutoff frequency fcu is synchronized with a nearby natural frequency fn of the building B described later. In order to control this, the operation of the flow rate adjusting motor 31 is controlled. In FIG. 12, the same step number is attached | subjected about the same execution content as the tuning control process (FIG. 9) of 1st Embodiment. Hereinafter, while referring to FIG. 12, the tuning control process will be described with a focus on differences from the first embodiment with reference to the hardware configuration of the first embodiment.

  In the tuning control process, as in the first embodiment, the inertial mass Mh due to the viscous fluid HF is ignored, the inertial mass Mr due to the rotating mass 21 is regarded as the inertial mass Md of the variable rotating inertial mass damper 1, and the flow rate is determined. The operation of the adjustment motor 31 is controlled.

  In FIG. 12, in step 11 following step 2, the neighborhood natural frequency fn is set based on the relationship between the calculated dominant frequency fcp and a plurality of predetermined natural frequencies of the building B. Specifically, the dominant frequency fcp is compared with a plurality of predetermined natural frequencies (the natural frequencies of the first to x-order modes) of the building B stored in the ROM of the control device 51, and the plurality of these frequencies are compared. Of the natural frequencies, the natural frequency closest to the dominant frequency fcp is set as the neighborhood natural frequency fn.

  For example, when the dominant frequency fcp is in the first predetermined frequency range including the natural frequency of the predetermined primary mode of the building B (hereinafter referred to as “primary natural frequency”), the nearby natural frequency fn is the primary natural frequency. Fcp is within a second predetermined frequency range (> first predetermined frequency range) including a natural frequency of a predetermined secondary mode of the building B (hereinafter referred to as “secondary natural frequency”). Sometimes fn is set to a secondary natural frequency. Such setting of the neighborhood natural frequency fn is performed using a plurality of predetermined frequency ranges respectively set corresponding to the plurality of natural frequencies. As described above, the near natural frequency fn is set to the primary natural frequency when the primary natural frequency is closest to the dominant frequency fcp, and is set to the secondary natural frequency when the secondary natural frequency is closest to the dominant frequency fcp. Set to

Next, the inertia mass Mds for this control is calculated by the following equation (11) using the set near natural frequency fn and the rigidity θs of the predetermined layer PF of the building B where the variable rotation inertia mass damper 1 is provided. (Step 12). This equation (11) expands the equation (9) (fcu = sqrt (θs / Md) / 2π) representing the cutoff frequency fcu with respect to the inertial mass Md of the variable rotational inertial mass damper 1, and Md is expressed as Mds. And fcu are replaced with fn, respectively.
Mds = θs / (fn · 2π) ² (11)

  Next, by performing Step 4 and subsequent steps, the pump volume vm2 is calculated, the rotation speed n of the flow rate adjustment motor 31 is calculated, and the flow rate adjustment motor 31 is driven by outputting a drive signal based on the rotation speed n. After that, the current process is terminated.

  By driving the flow rate adjusting motor 31 in this way, the inertial mass Md of the variable rotary inertial mass damper 1 including the inertial mass Mr by the rotary mass 21 is controlled to the inertial mass Mds calculated in Step 12. The cutoff frequency fcu is controlled to be the same as the nearby natural frequency fn. Further, the tuning control process including steps 1, 2, 11, 12, and 4 to 6 is repeatedly executed at predetermined time intervals as described above.

  As described above, according to the second embodiment, as in the case of the first embodiment, the interlayer displacement of the predetermined layer PF transmitted to the variable rotation inertial mass damper 1 due to the vibration of the building B is the cylinder 2, The piston 3, the viscous fluid HF, the first communication path 5, and the gear motor M are converted into a rotary motion of the rotary mass 21, whereby the rotary mass 21 rotates. The inertial mass Md of the variable rotary inertial mass damper 1 generated with the rotation of the rotary mass 21 is continuously changed by adjusting the flow rate of the viscous fluid HF in the second communication path 6 via the gear pump P. Is done.

  Further, as described with reference to FIG. 12, the dominant frequency fcp, which is the frequency of the dominant frequency component of the vibrations input from the foundation side to the building B, is calculated (step 2), and the building B is vibrating. The inertial mass Md is controlled so that the cutoff frequency fcu is tuned to the nearby natural frequency fn closest to the calculated dominant frequency fcp among the predetermined plurality of natural frequencies of the building B (step 11). 12, 4-6). In this way, by synchronizing the cutoff frequency fcu with the nearby natural frequency fn closest to the dominant frequency fcp of the input vibration among the plurality of natural frequencies of the building B, the predetermined layer PF of the predetermined layer PF due to the vibration of fn is obtained. The deformation can be increased, and the transmission of the vibration of fn to the upper layer of the predetermined layer PF of the building B can be cut off. As a result, the vibration (resonance) of the upper layer can be appropriately suppressed. In this case, since the predetermined layer PF is set as the lowermost layer of the building B, it is possible to effectively obtain an effect that the vibration of the layer above the predetermined layer PF can be appropriately suppressed.

  In the second embodiment, the inertial mass Md of the variable rotational inertial mass damper 1 is controlled so that the cutoff frequency fcu is the same as the nearby natural frequency fn, but fcu is substantially the same as fn. You may control so that it may become. In that case, a value obtained by adding or subtracting a very small predetermined value to fn is used instead of the near natural frequency fn in the equation (11).

  In the first and second embodiments, the first and second communication paths 5 and 6 are directly connected to the cylinder 2, but both ends of the second communication path 6 are in the middle of the first communication path 5. In addition, they may be connected in parallel so as to straddle the gear motor M (see FIG. 7 of Japanese Patent Application No. 2016-202281 by the present applicant). In the first and second embodiments, the gear motor M is used as the flow conversion mechanism in the present invention. However, other suitable mechanisms that can convert the flow of the viscous fluid HF into a rotational motion, such as the applicant of the present application. The screw mechanism described in FIG. 5 of Japanese Patent No. 5191579 and the ball screw in which the piston described in FIG. 2 of Japanese Patent No. 5161395 by the present applicant is integrally provided on the nut, or the vane motor or the plunger A motor (piston motor) or the like may be used. When this ball screw is used as the flow conversion mechanism, it goes without saying that the portion of the communication passage where the piston moves may be formed in a cylinder shape.

  Further, in the first and second embodiments, the gear pump P is used as the electric pump constituting the flow rate adjusting mechanism in the present invention. However, other appropriate electric pumps such as a vane pump and a plunger pump (piston pump) are used. Etc. may be used. In the first and second embodiments, the gear pump P is used as the flow rate adjusting mechanism, but other appropriate flow rate adjusting fluid flow rate of the viscous fluid HF (working fluid) flowing through the second communication passage 6 can be adjusted. A mechanism, for example, a flow rate adjusting valve that adjusts the flow rate of the working fluid by changing the opening degree may be used.

  Furthermore, in 1st and 2nd embodiment, although the viscous fluid HF comprised with silicone oil is used as a working fluid in this invention, you may use other suitable fluid which has hydraulic oil and viscosity. In the first and second embodiments, the first and second relief valves 11 and 12 are provided in the piston 3, but these may be omitted.

  Further, in the first and second embodiments (tuning control processing), the inertial mass Mh due to the viscous fluid HF is ignored, the inertial mass Mr due to the rotating mass 21 is regarded as the inertial mass Md of the variable rotating inertial mass damper 1, and the flow rate is determined. Although the operation of the adjustment motor 31 is controlled, the control may be performed with Md = Mr + Mh without ignoring the inertial mass Mh. In this case, in the processing after Step 4, the value obtained by subtracting the inertial mass Mh from the inertial mass Mds calculated by the equation (10) or (11) is used as the inertial mass Mds. Of course, the variations described so far with respect to the first and second embodiments may be applied in appropriate combination.

  Next, a vibration suppression device according to a third embodiment of the present invention will be described with reference to FIGS. This vibration suppression device is applied to the building B (see FIG. 15) as in the first embodiment. The variable rotation inertia mass damper 61 shown in FIG. 13, the control device 91, and the power source 92 shown in FIG. And a seismometer 53. The variable rotary inertia mass damper 61 is configured to be able to change the inertia mass generated as the rotary masses 68 and 68 described later rotate in two stages. As shown in FIG. 62, a cylindrical inner cylinder 63 and an outer cylinder 64 accommodated in the main body 62, and a screw shaft 65 provided movably in the axial direction (left and right direction in FIG. 13) with respect to the main body 62, A nut 66 is rotatably engaged with the screw shaft 65 via a plurality of balls (not shown).

  The main body 62 integrally includes a cylindrical cylindrical wall 62a and plate-shaped first end walls 62b and second end walls 62c provided at both ends of the cylindrical wall 62a in the axial direction. A thrust bearing BE1 is attached and fixed to each of the mutually opposing surfaces of the first and second end walls 62b and 62c. The pair of thrust bearings BE1 and BE1 are arranged coaxially with each other. The first end wall 62b is integrally provided with a convex portion 62d that protrudes outward in the thickness direction, and the convex portion 62d does not rotate with the torque that acts as the rotary masses 68 and 68 rotate. The first fixture FL1 ′ is provided via a universal joint having a certain degree of friction. The second end wall 62c is formed with an insertion hole 62e penetrating in the thickness direction, and the convex portion 62d and the insertion hole 62e are disposed coaxially with the thrust bearings BE1 and BE1. The first and second end walls 62b and 62c are formed with support holes 62f penetrating in the thickness direction in parallel with the insertion holes 62e. The support holes 62f are provided with radial bearings BE2. Is provided.

  The inner cylinder 63 integrally includes a cylindrical peripheral wall 63a and disk-shaped first end walls 63b and second end walls 63c provided at both ends in the axial direction of the peripheral wall 63a. In the portion 62, it is arranged coaxially with the nut 66. The first end wall 63b is engaged with the bearing BE1 of the first end wall 62b of the main body portion 62, and the second end wall 63c is engaged with the bearing BE1 of the second end wall 62c of the main body portion 62. The inner cylinder 63 is supported by the main body portion 62 via bearings BE 1 and BE 1 so as to be rotatable about the axis thereof, and cannot move with respect to the main body portion 62. Further, an insertion hole (not shown) penetrating in the axial direction is formed at the radial center of the second end wall 63c. The outer cylinder 64 is formed in a cylindrical shape, and an inner cylinder 63 is coaxially inserted inside the outer cylinder 64 and is rotatably supported by the inner cylinder 63 via a radial bearing (not shown). It is impossible to move in the axial direction with respect to 63.

  The screw shaft 65 constitutes a ball screw together with a ball and a nut 66. The screw shaft 65 extends in the axial direction and is partially accommodated in the inner cylinder 63 so as to be movable in the axial direction while being inserted into the insertion hole of the second end wall 63c. The second end wall 62c of 62 extends outward. At the end of the screw shaft 65 opposite to the inner cylinder 63, a second fitting FL2 ′ is provided via a universal joint having a friction that does not rotate with the torque acting with the rotation of the rotary masses 68, 68. Is provided. The nut 66 is coaxially attached to the second end wall 63 c of the inner cylinder 63 and is inserted into the insertion hole 62 e of the second end wall 62 c of the main body 62. It can be rotated together.

  With the above configuration, when the screw shaft 65 moves in the axial direction with respect to the main body 62, this movement is converted into rotational movement by the ball screw, and as a result, the nut 66 and the inner cylinder 63 rotate.

  The variable rotation inertia mass damper 61 rotates in a state where the clutch 67 for connecting / disconnecting the inner cylinder 63 and the outer cylinder 64, a pair of rotary masses 68, 68, and the rotation of the outer cylinder 64 are shifted. A transmission mechanism 69 for transmitting to the masses 68, 68 is further provided. The clutch 67 is a friction clutch, for example, and has an inner attached to the inner cylinder 63, an outer attached to the outer cylinder 64, and an electromagnetic actuator 67a (see FIG. 14). The actuator 67a is connected to the power source 92 via the control device 91, and the connection / disconnection of the clutch 67 is controlled by the control device 91 via the actuator 67a. When the nut 66 and the inner cylinder 63 rotate as the screw shaft 65 moves with respect to the main body portion 62 with the clutch 67 connected, the outer cylinder 64 rotates integrally with the inner cylinder 63. Note that a hydraulic actuator may be used as the actuator 67a. Further, as the clutch 67, another appropriate clutch such as an electromagnetic powder clutch may be used.

  Each rotary mass 68 is made of a material having a relatively large specific gravity, such as iron, and is formed in a disk shape. The thickness of each rotary mass 68 is relatively large, and one of the pair of rotary masses 68 and 68 is a transmission mechanism 69. The other end of the rotating shaft 70, which will be described later, and the other end are provided integrally with the other end of the rotating shaft 70 in a coaxial manner. Of course, one of the pair of rotating masses 68 and 68 may be omitted.

  The speed change mechanism 69 is a so-called parallel shaft stepped speed change mechanism, and is provided in parallel with the rotary shaft 70 inserted into the aforementioned insertion holes 62f, 62f of the main body 62 through the radial bearings BE2, BE2. The first gear train 71 and the second gear train 72, a synchromesh mechanism (synchronous meshing mechanism) 73, and the like are provided, and has two speed stages. The rotary shaft 70 is rotatably supported by the main body 62 via radial bearings BE <b> 2 and BE <b> 2, and extends in parallel with the outer cylinder 64. The first and second gear trains 71 and 72 and the synchromesh mechanism 73 are accommodated in the main body 62.

  The first gear train 71 is composed of a first gear 71 a and a second gear 71 b that mesh with each other. The former 71 a is integrally provided coaxially with the outer cylinder 64, and the latter 71 b is coaxial with the rotating shaft 70. It is provided rotatably. The second gear train 72 includes a third gear 72 a and a fourth gear 72 b that mesh with each other. The former 72 a is integrally provided coaxially with the outer cylinder 64, and the latter 72 b is coaxial with the rotating shaft 70. It is provided so as to be freely rotatable. Setting of the number of teeth of the first to fourth gears 71a, 71b, 72a, 72b will be described later.

  The synchromesh mechanism 73 is for selectively connecting / disconnecting the second gear 71b and the fourth gear 72b to / from the rotary shaft 70. The synchromesh mechanism 73 is formed in a ring shape and has a sleeve 73a provided with internal teeth, A clutch fork provided integrally with each of a shift fork 73b coupled to 73a, an electromagnetic actuator 73c (see FIG. 14) for driving the sleeve 73a via the shift fork 73b, and the second and fourth gears 71b, 72b. (Not shown). Since the synchromesh mechanism 73 is a well-known one used in a stepped transmission mechanism for a vehicle, its configuration and operation will be briefly described.

  The sleeve 73a is provided on the rotary shaft 70 so as not to rotate and to be movable in the axial direction, and is disposed between the second gear 71b and the fourth gear 72b. In the synchromesh mechanism 73, when the sleeve 73a is in the neutral position shown in FIG. 13, the second and fourth gears 71b and 72b and the rotary shaft 70 are in a disconnected state. Further, when the sleeve 73a is driven from the neutral position to the second gear 71b side by the actuator 73c, the sleeve 73a moves to the second gear 71b side while synchronizing the rotation of the second gear 71b and the rotating shaft 70, When the internal teeth of the sleeve 73a mesh with the clutch gear integrated with the second gear 71b, the second gear 71b is connected to the rotary shaft 70, and the fourth gear 72b and the rotary shaft 70 are disconnected.

  On the other hand, when the sleeve 73a is driven from the neutral position to the fourth gear 72b side by the actuator 73c, the sleeve 73a moves to the fourth gear 72b side while synchronizing the rotation of the fourth gear 72b and the rotating shaft 70, When the internal teeth of the sleeve 73a mesh with the clutch gear integrated with the fourth gear 72b, the fourth gear 72b is connected to the rotary shaft 70 and the second gear 71b and the rotary shaft 70 are disconnected.

  The actuator 73c is connected to the power source 92 via the control device 91, and selective connection / disconnection of the second and fourth gears 71b, 72b to the rotating shaft 70 by the synchromesh mechanism 73 is via the actuator 73c. Then, it is controlled by the control device 91. Thereby, as a gear train of the transmission mechanism 69 for transmitting the rotation of the outer cylinder 64 to the rotary masses 68, 68, the first gear train 71 including the first and second gears 71a, 71b, the third and fourth gear trains. One of the second gear train 72 composed of gears 72a and 72b is selected.

  Further, as shown in FIG. 15, the first fixture FL1 ′ and the second fixture FL2 ′ of the variable rotation inertia mass damper 61 are connected to the first connecting member EN1 and the second connecting member EN2 described in the first embodiment. Each is attached. Thus, the main body 62 and the screw shaft 65 of the variable rotation inertia mass damper 61 are connected to the lower beam BD and the upper beam BU via the first and second connection members EN1 and EN2, respectively. The mass damper 61 is provided in a predetermined layer PF of the building B and extends horizontally between the upper and lower beams BU and BD. The predetermined layer PF is, for example, the lowermost layer of the building B as in the case of the first embodiment. In FIG. 15, some components are not shown for convenience.

  Next, the operation of the variable rotation inertia mass damper 61 will be described. As the building B vibrates, when a horizontal relative displacement (interlayer displacement of the predetermined layer PF) occurs between the upper and lower beams BU, BD, this relative displacement is caused by the first and second connecting members EN1, EN2. The screw shaft 65 is moved in the axial direction with respect to the main body portion 62 by being transmitted as an external force to the main body portion 62 and the screw shaft 65 via. The movement of the screw shaft 65 is converted into a rotational motion by the nut 66, and the nut 66 rotates with respect to the main body 62 together with the inner cylinder 63.

  In this case, when the clutch 67 connects between the inner cylinder 63 and the outer cylinder 64 and the first gear train 71 is selected by the synchromesh mechanism 73, the rotation of the inner cylinder 63 causes the outer cylinder 64 and the first cylinder to rotate. A state in which the gear is shifted at a predetermined first gear ratio (the number of teeth of the second gear 71b / the number of teeth of the first gear 71a) based on the gear ratio of the two gears 71a and 71b via the first and second gears 71a and 71b. Then, it is transmitted to the rotating shaft 70 and further transmitted to the rotating masses 68 and 68. Thereby, as a result of rotation of the rotary masses 68 and 68, an inertial force due to the inertial mass due to the rotation of the rotary masses 68 and 68 is generated.

  On the other hand, when the inner cylinder 63 and the outer cylinder 64 are connected by the clutch 67 and the second gear train 72 is selected by the synchromesh mechanism 73, the rotation of the inner cylinder 63 causes the outer cylinder 64, the third and the third cylinders to rotate. Rotates in a state where the gear is shifted at a predetermined second speed ratio (the number of teeth of the fourth gear 72b / the number of teeth of the third gear 72a) based on the gear ratio of both the gears 72a and 72b via the four gears 72a and 72b. It is transmitted to the shaft 70 and further transmitted to the rotary masses 68 and 68. As a result, the rotation masses 68 and 68 rotate, and as a result, an inertial force due to the inertial mass due to the rotation of the rotation masses 68 and 68 is generated.

  The gear train selected by the synchromesh mechanism 73 is changed between the first gear train 71 and the second gear train 72, and the speed ratio of the speed change mechanism 69 is switched between the first speed ratio and the second speed ratio. First, after the clutch 67 is disconnected between the inner cylinder 63 and the outer cylinder 64, the gear train is changed in that state, and the connection of the changed gear train to the rotating shaft 70 is completed. After that, the clutch 67 connects the inner cylinder 63 and the outer cylinder 64.

When the first gear train 71 is selected, the inertial mass Md ′ (equivalent mass) due to the rotary masses 68 and 68 acting on the screw shaft 65 is expressed by the following equation (12).
Md '= {2π / (Ld × R1)} 2 × md' × D '2/8 ...... (12)
Here, R1 is the first gear ratio (the number of teeth of the second gear 71b / the number of teeth of the first gear 71a), Ld is the pitch of the screw shaft 65, and md 'is the actual mass of the rotary masses 68 and 68. The quantity D ′ is the diameter of the rotating mass 68.

On the other hand, the inertial mass Md ′ is expressed by the following equation (13) when the second gear train 72 is selected.
Md '= {2π / (Ld × R2)} 2 × md' × D '2/8 ...... (13)
Here, R2 is the second gear ratio (the number of teeth of the fourth gear 72b / the number of teeth of the third gear 72a).

  As is clear from these equations (12) and (13), the inertial mass Md ′ of the variable rotation inertial mass damper 61 selects one of the first and second gear trains 71 and 72 to change the speed of the speed change mechanism 69. By changing the ratio, it is changed in two steps.

Next, setting of the number of teeth of the first to fourth gears 71a to 72b will be described. The cutoff frequency fcu ′ determined by the inertial mass Md ′ of the variable rotational inertial mass damper 61 and the rigidity θs of the predetermined layer PF of the building B is expressed by the following equation (14).
fcu ′ = sqrt (θs / Md ′) / 2π (14)

As for the number of teeth of the first and second gears 71a and 71b, when the first gear train 71 is selected and the first gear ratio R1 is selected as the gear ratio of the transmission mechanism 69, the cutoff frequency fcu ′ is, for example, It is set to be synchronized with the primary natural frequency of the building B (the natural frequency of the primary mode) f1 (for example, fcu ′ = f1 or fa≈f1). More specifically, based on the above formulas (12) and (14), the first gear ratio R1, the primary natural frequency f1, the pitch Ld of the screw shaft 65, the substantial amount md ′ of the rotary masses 68 and 68, The number of teeth of the first and second gears 71a and 71b is set so that the following equation (15) is established between the diameter D ′ of the rotating mass 68 and the rigidity θs of the predetermined layer PF.
R1 = {(2π ² × f1 × D ′) / Ld} × sqrt {md ′ / (2θs)}
...... (15)

  The above formula (15) is an example of setting the number of teeth of the first and second gears 71a and 71b so that fcu ′ = f1, but when setting so that fcu′≈f1. Instead of the primary natural frequency f1 of the above equation (15), a value obtained by adding or subtracting a very small predetermined value to f1 is used.

Further, the number of teeth of the third and fourth gears 72a and 72b is determined so that when the second gear train 72 is selected and the second speed ratio R2 is selected as the speed ratio of the speed change mechanism 69, the cutoff frequency fcu ′. Is tuned to the secondary natural frequency (the natural frequency of the secondary mode) f2 of the building B (for example, fcu ′ = f2 or fcu′≈f2). More specifically, based on the above formulas (13) and (14), the second gear ratio R2, the secondary natural frequency f2, the pitch Ld of the screw shaft 65, the mass md ′ of the rotary masses 68 and 68, the rotation The number of teeth of the third and fourth gears 72a and 72b is set so that the following equation (16) is established between the diameter D ′ of the mass 68 and the rigidity θs of the predetermined layer PF.
R2 = {(2π ² × f2 × D ′) / Ld} × sqrt {md ′ / (2θs)}
...... (16)

  The above equation (16) is an example of setting the number of teeth of the third and fourth gears 72a and 72b so that fcu ′ = f2, but when setting so that fcu′≈f2. Instead of the secondary natural frequency f2 in the above equation (16), a value obtained by adding or subtracting a very small predetermined value to f2 is used.

  Note that the first and second speed ratios R1 and R2 are both set to a speed ratio on the high speed side that is smaller than the value 1.0, whereby the inertial mass Md ′ of the variable rotation inertial mass damper 61 is As is apparent from the equations (12) and (13), the rotation mass 68 is increased to be larger than the substantial amount md ′.

  The control device 91 and the power source 92 are configured in the same manner as the control device 51 and the power source 52 of the first embodiment, respectively, and the control device 91 inputs the building B from the foundation side measured by the seismometer 53. A measurement signal representing the vibration (earthquake) to be performed is input. In accordance with the input measurement signal, the control device 91 repeatedly executes the tuning control process shown in FIG. 16 at predetermined time intervals in accordance with a control program stored in the ROM.

  In this tuning control process, the gear ratio of the transmission mechanism 69 is set in order to control the inertial mass Md 'so that the cutoff frequency fcu' is synchronized with a near natural frequency fn described later. In FIG. 16, the same step number is assigned to the same execution content as the tuning control process (FIG. 9) of the first embodiment. Hereinafter, with reference to FIG. 16, the tuning control process will be described focusing on the portion of execution contents different from the first embodiment.

  In step 21 following step 2 in FIG. 16, the neighborhood natural frequency fn is set based on the relationship between the calculated dominant frequency fcp and the primary and secondary natural frequencies f1 and f2 of the building B. In this case, the near natural frequency fn is set as follows, unlike the case of the second embodiment (step 11 in FIG. 12). That is, when the dominant frequency fcp is smaller than a value obtained by adding a predetermined value to the primary natural frequency f1, the primary natural frequency f1 of the primary and secondary natural frequencies f1 and f2 is set to the dominant frequency fcp. The nearest natural frequency fn is set to the primary natural frequency f1 as the closest. On the other hand, when the dominant frequency fcp is greater than or equal to a value obtained by adding a predetermined value to the primary natural frequency f1, the secondary natural frequency f2 of the primary and secondary natural frequencies f1 and f2 is the dominant frequency frequency fcp. The closest natural frequency fn is set to the secondary natural frequency f2 as the closest.

  Next, based on the near natural frequency fn, the transmission ratio of the transmission mechanism 69 is set (step 22), and the current process is terminated. In this step 22, when the near natural frequency fn is set to the primary natural frequency f1, the speed change of the transmission mechanism 69 is performed in order to synchronize the cutoff frequency fcu ′ with the primary natural frequency f1 of the building B. The ratio is set (controlled) to the first speed ratio R1. Further, when the near natural frequency fn is set to the secondary natural frequency f2, in order to synchronize the cutoff frequency fcu ′ with the secondary natural frequency f2 of the building B, the transmission ratio of the transmission mechanism 69 is It is set (controlled) to 2 gear ratio R2. Accordingly, the operations of the actuators 67a and 73c are controlled according to the set speed ratio. Note that the tuning control process including steps 1, 2, 21, and 22 is repeatedly executed at predetermined time intervals as described above.

  As described above, according to the third embodiment, as described with reference to FIGS. 13 to 15, the variable rotation inertia mass damper 61 is provided in the predetermined layer PF of the building B, and the vibration of the building B is The relative displacement between the upper and lower beams BU and BD, that is, the interlayer displacement of the predetermined layer PF is transmitted to the variable rotation inertia mass damper 61. The transmitted interlayer displacement is converted into rotational power by a ball screw including a screw shaft 65 and a nut 66. The converted rotational power is converted into a predetermined first and second speed ratio R1 by a stepped transmission mechanism 69. , R2 is transmitted to the rotary masses 68 and 68 in a state of being shifted at one speed ratio selected from the R2, whereby the rotary masses 68 and 68 are rotated. The inertial mass Md ′ of the variable rotary inertial mass damper 61 generated as the rotary masses 68 and 68 rotate is changed in two stages by changing the speed ratio of the speed change mechanism 69.

  The first and second transmission ratios R1 and R2 are set so that the cut-off frequency fcu ′ obtained when the first and second transmission ratios R1 and R2 are selected during the vibration of the building B is 1 for the building B. It is set so as to be tuned to the secondary and secondary natural frequencies f1 and f2, respectively. Further, as described with reference to FIG. 16, the dominant frequency fcp (the frequency of the dominant frequency component of the vibrations input to the building B from the foundation side) is calculated (step 2), and the building B is being vibrated. , The inertial mass Md so that the cut-off frequency fcu ′ is tuned to the near natural frequency fn (the natural frequency closest to the dominant frequency fcp of the primary and secondary natural frequencies f1 and f2 of the building B). 'Is controlled (steps 21 and 22).

  In this way, by synchronizing the cutoff frequency fcu ′ with the nearby natural frequency fn closest to the dominant frequency fcp of the input vibration from the foundation side among the plurality of natural frequencies of the building B, the vibration of fn The deformation of the predetermined layer PF due to the above can be increased, and the transmission of the vibration of fn to the upper layer of the predetermined layer PF of the building B can be cut off. As a result, the vibration (resonance) of the upper layer can be appropriately suppressed. it can. In this case, since the predetermined layer PF is set as the lowermost layer of the building B, it is possible to effectively obtain an effect that the vibration of the layer above the predetermined layer PF can be appropriately suppressed.

  Next, a variable rotation inertia mass damper 101 of a vibration suppression device according to a fourth embodiment of the present invention will be described with reference to FIG. In this variable rotary inertia mass damper 101, the configuration of the rotary masses 102 and 102 and the friction material 103 between the rotary masses 102 and the rotary shaft 70 are provided as compared with the third embodiment described above. Is different. In FIG. 17, the same components as those in the third embodiment are denoted by the same reference numerals. Hereinafter, a description will be given focusing on differences from the third embodiment.

  The rotating mass 102 differs from the rotating mass 68 of the third embodiment only in that a fitting hole 102a penetrating in the axial direction is formed. The friction material 103 is made of a material having a relatively stable coefficient of friction, such as Teflon (registered trademark), and is formed in an annular shape and attached to both ends of the rotating shaft 70. 102 is fitted into the fitting hole 102a. By this fitting, the rotary mass 102 is connected to the rotary shaft 70. The friction coefficient of the friction material 103 is set so that the rotation mass 102 slides against the friction material 103 when the rotation torque of the rotation mass 102 becomes very large due to the vibration of the building B being very large. Yes. Note that the friction material 103 may be discontinuously attached to the peripheral surface of the rotating shaft 70 without being formed in an annular shape.

  Further, flanges 70a are integrally provided on both sides of the rotary mass 70 in the axial direction of the rotary mass 102, and the rotary mass 102 is sandwiched between the flanges 70a and 70a.

  Although not shown, the variable rotation inertial mass damper 101 has the lower beam BD and the upper beam of the building B through the first and second connecting members EN1 and EN2, respectively, as in the first to third embodiments. It is connected to the beam BU (see FIG. 15).

  As described above, according to the fourth embodiment, the friction material 103 is attached to the rotation shaft 70, and the rotation mass 102 is fitted into the fitting hole 102a, so that the friction material 103 is fitted. The rotary shaft 70 is connected via 103. In addition, since the friction coefficient of the friction material 103 is set as described above, when the rotation torque of the rotation mass 102 becomes very large due to the vibration of the building B being very large, the rotation mass 102 becomes the friction material. Thus, the inertial force due to the inertial mass generated as the rotary masses 102 and 102 are rotated can be limited.

  In addition, during the vibration of the building B, the inertial force may be limited by the inertial mass generated with the rotation of the rotary masses 102 and 102 by closing the clutch 67.

  In the third and fourth embodiments, the single synchromesh mechanism 73 that connects / disconnects the second and fourth gears 71b, 72b to / from the rotating shaft 70 is used, but they are provided separately from each other. A synchromesh mechanism for the second gear 71b and the fourth gear 72b may be used. In the third and fourth embodiments, the first gear 71a is integrally provided with the outer cylinder 64, and the second gear 71b is rotatably provided on the rotary shaft 70. The gear 71a may be rotatably provided on the outer cylinder 64, and the second gear 71b may be provided integrally with the rotary shaft 70. This also applies to the third and fourth gears 72a and 72b.

  Furthermore, in the third and fourth embodiments, the number of shift stages of the transmission mechanism 69 is 2, but may be 3 or more. In that case, a plurality of gear ratios of three or more stages are tuned in correspondence with a plurality of cutoff frequencies fcu ′ obtained corresponding to each of the gear ratios, respectively, corresponding to a plurality of natural frequencies of the third mode or higher of the building B. To be set. In the third and fourth embodiments, the speed change mechanism 69 is a parallel shaft type stepped speed change mechanism, but other suitable stepped speed change mechanisms, for example, planetary gear devices used in vehicles and the like, Further, a stepped transmission mechanism configured by a combination of a brake and a clutch may be used.

  Furthermore, in 4th Embodiment, while attaching the friction material 103 to the rotating shaft 70 and making it fit to the fitting hole 102a of the rotation mass 102, a friction material is put on the internal peripheral surface of the fitting hole of a rotation mass. While attaching, you may fit a rotating shaft inside a friction material. Alternatively, the friction material may be fitted between the rotating shaft and the inner peripheral surface of the fitting hole without being attached (not fixed). In that case, the rotating mass is formed with a plurality of receiving holes penetrating in the radial direction and communicating with the fitting holes, each of the receiving holes is provided with a spring that contacts the friction material, and the rotating mass is radially outward. The compression degree of the spring may be changed by screwing the screw into the accommodation hole, thereby adjusting the fitting degree (friction coefficient) of the friction material with respect to the rotary shaft and the inner peripheral surface of the fitting hole.

  Next, a vibration suppression apparatus according to a fifth embodiment of the present invention will be described with reference to FIGS. FIG. 18 shows the variable rotation inertia mass damper 111 of the vibration suppressing device, and the variable rotation inertia mass damper 111 is not provided with the outer cylinder 64 and the clutch 67 as compared with the third embodiment. The structure of the speed change mechanism 112 is different. 18 to 20, the same components as those in the first to third embodiments are denoted by the same reference numerals. Hereinafter, a description will be given focusing on differences from the first to third embodiments.

  The speed change mechanism 112 of the variable rotation inertial mass damper 111 shown in FIG. 18 is a metal belt type continuously variable speed change mechanism capable of changing the speed ratio steplessly, and is a well-known one used in vehicles and the like. The configuration and operation will be briefly described below. The speed change mechanism 112 includes a driving pulley 113, a driven pulley 114, a transmission belt 115, a first electromagnetic valve 116, a second electromagnetic valve 117 (see FIG. 19), and the like. It has a trapezoidal fixed portion 113a and a movable portion 113b.

  The fixed portion 113a is fixed to the peripheral wall 63a of the inner cylinder 63, and the movable portion 113b is provided on the peripheral wall 63a of the inner cylinder 63 so as to be movable in the axial direction and relatively non-rotatable. Further, a V-shaped belt groove around which the transmission belt 115 is wound is formed between the fixed portion 113a and the movable portion 113b. A hydraulic pump (not shown) is connected to the movable portion 113b, and the hydraulic pressure supplied from the hydraulic pump to the movable portion 113b is adjusted by changing the opening degree of the first electromagnetic valve 116. As a result, the effective width of the drive pulley 113 changes steplessly by changing the pulley width of the drive pulley 113. As shown in FIG. 19, the first electromagnetic valve 116 is connected to a power source 122 via a control device 121 described later.

  The driven pulley 114 is configured in the same manner as the drive pulley 113, and has a frustoconical fixed portion 114a and a movable portion 114b facing each other. The fixed portion 114a is fixed to the rotating shaft 70, and the movable portion 114b is provided on the rotating shaft 70 so as to be movable in the axial direction and not to rotate. Further, a V-shaped belt groove is formed between the fixed portion 114a and the movable portion 114b. A hydraulic pump (not shown) is connected to the movable portion 114b, and the hydraulic pressure supplied from the hydraulic pump to the movable portion 114b is adjusted by changing the opening degree of the second electromagnetic valve 117. Thereby, the effective diameter of the driven pulley 114 changes steplessly by changing the pulley width of the driven pulley 114. As shown in FIG. 19, the second electromagnetic valve 117 is connected to the power source 122 via the control device 121.

  The transmission belt 115 is a belt in which a large number of elements made of metal plates are connected to each other with a band-shaped metal ring in a state of being overlapped with each other, and is wound around the belt grooves of the driving pulley 113 and the driven pulley 114.

  In the speed change mechanism 112 having the above-described configuration, the opening diameters of the first and second electromagnetic valves 116 and 117 are controlled by the control device 121, so that the effective diameters of the drive pulley 113 and the driven pulley 114 change steplessly. The gear ratio is controlled steplessly. The speed ratio of the speed change mechanism 112 can be changed steplessly between the first upper limit speed ratio and the second lower limit speed ratio, both of which are smaller than 1.0.

  Further, as shown in FIG. 20, the variable rotary inertia mass damper 111 is a lower beam of the building B via the first and second connecting members EN1 and EN2 as in the first to third embodiments. It is connected to the BD and the upper beam BU, and is provided in the predetermined layer PF. In FIG. 20, for convenience, some components and reference numerals are omitted.

  Next, the operation of the variable rotation inertia mass damper 111 will be described. When relative displacement (interlayer displacement of the predetermined layer PF) occurs between the upper and lower beams BU and BD along with the vibration of the building B, the relative displacement is transmitted to the main body 62 and the screw shaft 65, so that the screw shaft 65 moves in the axial direction relative to the main body 62. The movement of the screw shaft 65 is converted into a rotational motion by the nut 66, and the nut 66 rotates with respect to the main body 62 together with the inner cylinder 63. The rotation of the inner cylinder 63 is transmitted to the rotary shaft 70 while being shifted by the speed change mechanism 112, and is further transmitted to the rotary masses 68 and 68. As a result, as a result of the rotation of the rotary masses 68 and 68, an inertial force due to the inertial mass Md 'resulting from the rotation of the rotary masses 68 and 68 is generated.

  In this case, unlike the speed change mechanism 69 of the third embodiment, the speed change mechanism 112 can change its speed ratio steplessly, so that the variable rotation inertia mass damper 111 changes the speed change ratio of the speed change mechanism 112. Thus, the inertial mass Md ′ can be changed continuously.

  The control device 121 and the power source 122 are configured in the same manner as the control device 51 and the power source 52 of the first embodiment, respectively, and the vibration (earthquake) input from the foundation side to the building B measured by the seismometer 53 is used. A measurement signal is input. As shown in FIG. 19, the control device 121 further receives a detection signal indicating the rotation speed of the driving pulley 113 from the first rotation speed sensor 123 and a detection signal indicating the rotation speed of the driven pulley 114 from the second rotation speed sensor 124. Is entered. The control device 121 calculates the speed ratio of the speed change mechanism 112 (the speed of the drive pulley 113 / the speed of the driven pulley 114) based on the detection signals input from the first and second speed sensors 123 and 124. .

  Further, the control device 121 repeatedly executes the tuning control process shown in FIG. 21 at predetermined time intervals in accordance with a control program stored in the ROM in accordance with the input measurement signal and detection signal. In this tuning control process, the inertial mass Md ′ of the variable rotational inertial mass damper 111 is controlled so that the cutoff frequency fcu ′ represented by the equation (14) is synchronized with the dominant frequency fcp described in the first embodiment. In order to achieve this, the transmission ratio of the transmission mechanism 112 is set. In FIG. 21, the same step numbers are assigned to portions having the same execution contents as the tuning control processing (FIG. 9) of the first embodiment. As apparent from the comparison between FIG. 21 and FIG. 9, the only difference is that step 31 is executed instead of steps 3 to 6 as compared with the first embodiment. Only the execution contents of will be described.

In step 31, the speed ratio of the speed change mechanism 112 is set (controlled) based on the calculated dominant frequency fcp, and the current process ends. Specifically, first, based on the dominant frequency fcp, the target gear ratio Rcmd is calculated by the following equation (17) based on the equations (15) and (16). Next, the opening degree of the first and second electromagnetic valves 116 and 117 is controlled by outputting a drive signal based on the target gear ratio Rcmd. As a result, the speed ratio is controlled to be the calculated target speed ratio Rcmd.
Rcmd = {(2π ² × fcp × D ′) / Ld} × sqrt {md ′ / (2θs)}
...... (17)

  In this equation (17), the diameter D ′ of the rotary mass 68, the pitch Ld of the screw shaft 65, the substantial amount md ′ of the rotary masses 68 and 68, and the rigidity θs of the predetermined layer PF are all predetermined values. Is read from the ROM in step 31. The drive signal is obtained in advance by experiments or the like so that the gear ratio becomes the target gear ratio Rcmd, and is stored in the ROM.

  As is apparent from the equations (15) to (17), by setting the speed change ratio as described above, the inertia of the variable rotational inertia mass damper 111 is set so that the cutoff frequency fcu ′ becomes the same as the dominant frequency fcp. The mass Md ′ is controlled. In the tuning control process, as described above, the processes including steps 1, 2, and 31 are repeatedly executed at predetermined time intervals.

  As described above, according to the fifth embodiment, as described with reference to FIGS. 18 to 20, the variable rotation inertia mass damper 111 is provided in the predetermined layer PF of the building B, and the vibration of the building B is The relative displacement between the upper and lower beams BU and BD accompanying the above, that is, the interlayer displacement of the predetermined layer PF is transmitted to the variable rotation inertia mass damper 111. The transmitted interlayer displacement is converted into rotational power by a ball screw including a screw shaft 65 and a nut 66, and the converted rotational power is transmitted to the rotary masses 68 and 68 while being shifted by the continuously variable transmission mechanism 112. As a result, the rotary masses 68 and 68 rotate. The inertial mass Md ′ of the variable rotary inertial mass damper 111 generated as the rotary masses 68 and 68 rotate is continuously changed by changing the speed ratio of the speed change mechanism 112.

  Further, as described with reference to FIG. 21, the dominant frequency fcp (the frequency of the dominant frequency component of the vibrations input to the building B from the foundation side) is calculated (step 2), and the building B is being vibrated. The transmission ratio of the transmission mechanism 112 is set so that the cutoff frequency fcu ′ determined by the rigidity θs of the predetermined layer PF and the inertial mass Md ′ of the variable rotational inertial mass damper 111 is synchronized with the calculated dominant frequency fcp. Thus, the inertial mass Md ′ is controlled (step 31). Accordingly, by synchronizing the cutoff frequency fcu ′ with the dominant frequency fcp, the deformation of the predetermined layer PF due to the vibration of the fcp is increased, and the transmission of the vibration of the fcp to the layer above the predetermined layer PF of the building B is transmitted. Therefore, the vibration of the upper layer can be appropriately suppressed. In this case, since the predetermined layer PF is set as the lowermost layer of the building B, it is possible to effectively obtain an effect that the vibration of the layer above the predetermined layer PF can be appropriately suppressed.

  In the fifth embodiment, the inertial mass Md ′ is controlled so that the cutoff frequency fcu ′ is the same as the dominant frequency fcp. However, the inertial mass Md ′ is controlled so that the fcu ′ is substantially the same as fcp. May be. In that case, a value obtained by adding or subtracting a very small predetermined value to fcp is used instead of the dominant frequency fcp in the equation (17).

  Next, a vibration suppression device according to a sixth embodiment of the present invention will be described. Compared with the fifth embodiment, this vibration suppressing device has the same hardware configuration as the variable rotation inertia mass damper 111 and the like, but differs only in that the tuning control process shown in FIG. 22 is executed. In the tuning control process according to the sixth embodiment, unlike the case of the fifth embodiment, the variable rotational inertia mass damper 111 is adjusted so that the cutoff frequency fcu ′ is tuned to the near natural frequency fn described in the second embodiment. In order to control the inertial mass Md ′, the transmission ratio of the transmission mechanism 112 is set. In FIG. 22, the same step number is attached | subjected about the same execution content as the tuning control process (FIG. 21) of 5th Embodiment. Hereinafter, while referring to FIG. 22, the tuning control process will be described with a focus on differences from the fifth embodiment with reference to the hardware configuration of the fifth embodiment.

  In FIG. 22, after calculating the dominant frequency fcp by executing step 2, by executing step 11, the near natural frequency fn is set as described in the second embodiment. That is, the dominant frequency fcp is compared with a plurality of predetermined natural frequencies of the building B (the natural frequencies of the first-order to x-order modes), and the natural frequency closest to the dominant frequency fcp among these natural frequencies. The frequency is set as the neighborhood natural frequency fn. Thus, the near natural frequency fn is set to the primary natural frequency when the primary natural frequency of the building B (the natural frequency of the primary mode) is closest to the dominant frequency fcp (secondary natural frequency ( When the natural frequency of the secondary mode is closest to the dominant frequency fcp, the secondary natural frequency is set.

Next, the speed ratio of the speed change mechanism 112 is set (controlled) based on the set near natural frequency fn (step 41), and the current process is terminated. In step 41, the gear ratio is set as follows. That is, first, based on the near natural frequency fn, the target gear ratio Rcmd is calculated by the following equation (18) based on the equations (15) and (16). Next, the opening degree of the first and second electromagnetic valves 116 and 117 is controlled by outputting a drive signal based on the target gear ratio Rcmd. As a result, the speed ratio is controlled to be the calculated target speed ratio Rcmd.
Rcmd = {(2π ² × fn × D ′) / Ld} × sqrt {md ′ / (2θs)}
...... (18)

  As is clear from the equations (15), (16), and (18), by setting the gear ratio as described above, the variable rotation is performed so that the cutoff frequency fcu ′ becomes the same as the nearby natural frequency fn. The inertial mass Md ′ of the inertial mass damper 111 is controlled. In the tuning control process, as described above, the processes including steps 1, 2, 11, and 41 are repeatedly executed at predetermined time intervals.

  As described above, according to the sixth embodiment, as in the case of the fifth embodiment, the interlayer displacement of the predetermined layer PF transmitted to the variable rotation inertial mass damper 111 due to the vibration of the building B is the screw shaft 65. And converted into rotational power by a ball screw including a nut 66, and the converted rotational power is transmitted to the rotary masses 68 and 68 while being shifted by the continuously variable transmission mechanism 112, whereby the rotary masses 68 and 68 are Rotate. The inertial mass Md ′ of the variable rotary inertial mass damper 111 generated as the rotary masses 68 and 68 rotate is continuously changed by changing the speed ratio of the speed change mechanism 112.

  Further, as described with reference to FIG. 22, the dominant frequency fcp (frequency of the dominant frequency component of the vibrations input from the foundation side to the building B) is calculated (step 2), and the building B is being vibrated. The inertial mass Md ′ is controlled so that the cutoff frequency fcu ′ is tuned to the nearest natural frequency fn closest to the calculated dominant frequency fcp among the predetermined plurality of natural frequencies of the building B ( Steps 11 and 41). In this way, by synchronizing the cutoff frequency fcu ′ with the nearby natural frequency fn closest to the dominant frequency fcp of the input vibration from the foundation side among the plurality of natural frequencies of the building B, the vibration of fn The deformation of the predetermined layer PF due to the above can be increased, and the transmission of the vibration of fn to the upper layer of the predetermined layer PF of the building B can be cut off. As a result, the vibration (resonance) of the upper layer can be appropriately suppressed. it can. In this case, since the predetermined layer PF is set as the lowermost layer of the building B, it is possible to effectively obtain an effect that the vibration of the layer above the predetermined layer PF can be appropriately suppressed.

  In the sixth embodiment, the inertial mass Md ′ is controlled so that the cutoff frequency fcu ′ is the same as the near natural frequency fn, but the fcu ′ is substantially the same as fn. You may control. In that case, a value obtained by adding or subtracting a very small predetermined value to fn is used instead of the near natural frequency fn in the equation (18).

  Further, in the fifth and sixth embodiments, the outer cylinder 64 and the clutch 67 of the third and fourth embodiments are omitted, but these may be adopted, and in that case, the fixing portion 113a of the drive pulley 113 is used. The movable portion 113b is provided on the outer cylinder 64. Further, regarding the fifth and sixth embodiments, the rotary masses 68, 68 and the rotary shaft 70 are configured as described in the fourth embodiment, that is, each rotary mass is connected to the rotary shaft via a friction material. May be. Also in this case, it is needless to say that the above-described variations may be adopted for the rotating mass and the friction material. Further, in the fifth and sixth embodiments, the transmission mechanism 112 is a metal belt type continuously variable transmission mechanism, but other suitable continuously variable transmission mechanisms such as a traction drive type (for example, a vehicle) A toroidal-type continuously variable transmission mechanism may be used.

  In the third to sixth embodiments, a ball screw including a screw shaft 65 and a nut 66 is used as the conversion mechanism in the present invention. However, other appropriate conversion for converting the transmitted displacement of the structure into rotational power. For example, a mechanism configured by a rack and a pinion that mesh with each other, a mechanism configured by the cylinder 2, the piston 3, the first communication path 5, the gear motor M, and the like of the first embodiment may be used. In this case, it goes without saying that the screw mechanism of the aforementioned Japanese Patent No. 5191579 may be used in place of the gear motor M.

  Next, a vibration suppressing device according to a seventh embodiment of the present invention will be described with reference to FIGS. This vibration suppression device is applied to the building B (see FIG. 25) as in the first embodiment. The variable rotation inertia mass damper 131 shown in FIG. 23, the control device 141, and the power source 142 shown in FIG. And a seismometer 53. 23 and 25, the same components as those in the first embodiment are denoted by the same reference numerals. Hereinafter, a description will be given focusing on differences from the first embodiment.

  As is clear from the comparison between FIG. 23 and FIG. 1, the variable rotational inertia mass damper 131 does not include the second communication path 6 and the gear pump P as compared with the variable rotational inertia mass damper 1 of the first embodiment. The difference is that a variable displacement fluid pressure motor 132 is provided instead of the gear motor M.

  Since the fluid pressure motor 132 is, for example, a known swash plate type variable displacement hydraulic motor, its configuration and operation will be briefly described below. The fluid pressure motor 132 includes a rotating shaft 132 a, an actuator 132 b (see FIG. 24), a swash plate, a cylinder block, a piston, a shoe (all not shown), and the like, and is provided in the middle of the first communication path 5. ing. The cylinder block is provided with an inflow port and an outflow port. The inflow port and the outflow port are connected to the first and second fluid chambers via the first communication passage 5 and a check valve (not shown). 2d and 2e are connected in parallel to each other.

  In the fluid pressure motor 132, when the viscous fluid HF flows into the inflow port, the pressure energy of the viscous fluid HF that has flowed in is converted into rotational energy of the rotating shaft 132a by the cylinder block, piston, shoe, and swash plate, The rotating shaft 132a rotates. The tilt angle of the swash plate is configured to be continuously changed by the actuator 132b. By changing the tilt angle of the swash plate, the displacement volume VM (per rotation of the rotating shaft 132a) of the fluid pressure motor 132 is changed. By continuously changing the geometric volume that is pushed away, the amount of rotation of the rotating shaft 132a with respect to the pressure of the same viscous fluid HF changes continuously.

  The actuator 132b is, for example, an electromagnetic type, and is connected to the control device 141 shown in FIG. Like the control device 51, the control device 141 is composed of a combination of a CPU, RAM, ROM, I / O interface, etc., and is connected to a power source 142. The displacement volume VM of the fluid pressure motor 132 is adjusted by changing the angle. Of course, a fluid pressure type actuator or the like may be used as the actuator 132b.

  The rotating mass 21 is coaxially and integrally provided on the rotating shaft 132a. When the pressure energy of the viscous fluid HF is converted into the rotational energy of the rotating shaft 132a by the fluid pressure motor 132, the rotating mass 21 rotates integrally with the rotating shaft 132a.

  As shown in FIG. 25, the variable rotational inertia mass damper 131 having the above-described configuration is provided in a predetermined layer PF of the building B like the variable rotational inertia mass damper 1 of the first embodiment, and the cylinder 2 and the piston rod 4 thereof. Are connected to the lower beam BD and the upper beam BU via the first and second connecting members EN1 and EN2, respectively, and extend horizontally between the BD and BU. In FIG. 25, illustration of some components, such as the 1st communicating path 5, is abbreviate | omitted for convenience.

  Next, the operation of the variable rotation inertia mass damper 131 will be described. When the horizontal displacement occurs between the upper and lower beams BU and BD as the building B vibrates, the relative displacement is transferred to the cylinder 2 and the piston via the first and second connecting members EN1 and EN2. By being transmitted to the rod 4 as an external force, the cylinder 2 and the piston rod 4 relatively move in the axial direction, and the piston 3 slides in the cylinder 2.

  In this case, when the piston 3 moves to the first fluid chamber 2d side (left side in FIG. 23), a part of the viscous fluid HF in the first fluid chamber 2d is pushed out by the piston 3 to the first communication passage 5. Thus, the viscous fluid HF flows in the first communication passage 5 toward the second fluid chamber 2e (right side). On the contrary, when the piston 3 moves to the second fluid chamber 2e side (right side), a part of the viscous fluid HF in the second fluid chamber 2e is pushed out to the first communication passage 5 by the piston 3. As a result, the working fluid HF flows to the first fluid chamber 2 d side (left side) in the first communication path 5.

  The pressure energy of the viscous fluid HF due to this flow is converted into rotational energy of the rotating shaft 132 a by the fluid pressure motor 132, and the rotating shaft 132 a rotates with the rotating mass 21. With the flow of the viscous fluid HF and the rotation of the rotating mass 21, the inertial mass (inertial mass based on the rotating inertial mass of the rotating mass 21) MR and the first series are the same as in the first embodiment. An inertial mass MD (inertial mass in the axial direction with respect to an external force caused by vibrations input to the cylinder 2 and the piston 3) including the inertial mass Mh due to the viscous fluid HF in the passage 5 is generated.

In this case, the inertial mass MR due to the rotating mass 21 is expressed by the following equation (19), and the inertial mass Mh due to the viscous fluid HF is as described in the first embodiment. Further, the inertial mass Mh due to the viscous fluid HF tends to be very small compared to the inertial mass MR due to the rotating mass 21.
^{MR = (2π / XM) 2} · md · D 2/8
= {(2π · Ap) / VM} 2 · md · D 2/8 ...... (19)

  In Equation (19), XM is the amount of movement of the piston 3 relative to the cylinder 2 required for one rotation of the rotating shaft 132a of the fluid pressure motor 132 due to the flow of the viscous fluid HF, and the rotational inertia using the ball screw mechanism. This corresponds to the lead length Ld of the ball screw in the mass damper. Further, VM is the displacement volume of the fluid pressure motor 132 as described above, and the other parameters (md, D, Ap) are as described in the first embodiment.

  As apparent from the above equation (19), the displacement volume VM of the fluid pressure motor 132 is adjusted by the control device 141, whereby the inertial mass MD of the variable rotary inertial mass damper 131 including the inertial mass MR by the rotary mass 21. Is controlled. In this case, the inertial mass MD is continuously changed by adjusting the displacement volume VM, and the smaller the displacement volume VM, the more the rotation amount of the rotation shaft 132a and the rotation mass 21 with respect to the pressure energy of the same viscous fluid HF. Since it becomes large, inertial mass MD becomes larger. This is also clear from equation (19).

Further, the control device 141 repeatedly executes the tuning control process shown in FIG. 26 at predetermined time intervals in accordance with the control program stored in the ROM in accordance with the measurement signal input from the seismometer 53. This tuning control process is performed so that the cutoff frequency fCU determined by the inertial mass MD of the variable rotary inertial mass damper 131 and the rigidity θs of the predetermined layer PF of the building B is synchronized with the dominant frequency fcp described in the first embodiment. In order to control the mass MD, the displacement volume VM of the fluid pressure motor 132 is controlled. Here, the cutoff frequency fCU is expressed by the following equation (20).
fCU = sqrt (θs / MD) / 2π (20)

  In FIG. 26, the same step numbers are assigned to the same execution contents as those in the tuning control process (FIG. 9) of the first embodiment. As apparent from the comparison between FIG. 26 and FIG. 9, the only difference is that steps 51 and 52 are executed instead of steps 4 to 6 as compared with the first embodiment. Therefore, only the execution contents of these steps 51 and 52 will be described below. As described above, the inertial mass Mh due to the viscous fluid HF contained in the inertial mass MD of the variable rotational inertial mass damper 131 tends to be very small as compared with the inertial mass MR due to the rotational mass 21. For this reason, in the tuning control process, the inertial mass Mh is ignored, the inertial mass MR by the rotating mass 21 is regarded as the inertial mass MD of the variable rotating inertial mass damper 131, and the displacement volume VM of the fluid pressure motor 132 is controlled. .

In step 51, using the inertial mass Mds for main control calculated in step 3 above, a target displacement volume VMobj that is a target value of the displacement volume VM is calculated by the following equation (21). This equation (21) is obtained by expanding the equation (19) with respect to the displacement volume VM, replacing the displacement volume VM with the target displacement volume VMobj, and replacing the inertial mass MR due to the rotary mass 21 with the inertial mass Mds. is there.
VMobj = (2π · Ap) / sqrt {8Mds / (md · D ² )} (21)

  In step 52 following step 51, the actuator 132b is driven by outputting a drive signal based on the calculated target displacement volume VMobj to the actuator 132b. Thus, the inertial mass MR by the rotary mass 21 regarded as the inertial mass MD of the variable rotary inertial mass damper 131 is controlled by controlling the displacement volume VM of the fluid pressure motor 132 to be the target displacement volume VMobj. The inertial mass Mds calculated in step 4 is controlled. As a result, the cutoff frequency fCU (= sqrt (θs / MD) / 2π) determined by the inertial mass MD and the rigidity θs of the predetermined layer PF of the building B is the same as the dominant frequency fcp described in the first embodiment. To be controlled. The drive signal is obtained in advance by experiments or the like so as to obtain the target displacement volume VMobj, and is stored in the ROM.

  As described above, according to the seventh embodiment, as in the case of the first embodiment, the variable rotary inertia mass damper 131 is provided in the predetermined layer PF of the building B, and the upper and lower beams accompanying the vibration of the building B are provided. The relative displacement between BU and BD, that is, the interlayer displacement of the predetermined layer PF is transmitted to the cylinder 2 and the piston 3. Accordingly, when the piston 3 slides in the cylinder 2 and moves to one side of the first and second fluid chambers 2d and 2e, the viscous fluid HF in the one fluid chamber is the piston 3 and the first communication passage 5 As a result, the viscous fluid HF flows into the first fluid passage 5 toward the other fluid chamber. The pressure energy of the viscous fluid HF is converted into rotational energy by the variable displacement fluid pressure motor 132, and the rotational mass 21 is rotated by transmitting the converted rotational energy to the rotational mass 21. Along with this, an inertial mass MD corresponding to the rotary inertial mass MR of the rotary mass 21 is generated, and the inertial mass MD is continuously changed by adjusting the displacement volume VM of the fluid pressure motor.

  Further, as in the case of the first embodiment, a dominant frequency fcp, which is a frequency of a frequency component that is dominant among vibrations input from the foundation side to the building B, is calculated (step 2 in FIG. 26). Further, during the vibration of the building B, more specifically, the fCU is equal to the fcp so that the cutoff frequency fCU determined by the rigidity θs of the predetermined layer PF and the inertial mass MD is synchronized with the calculated dominant frequency fcp. Thus, by adjusting the displacement volume VM, the inertial mass MD including the inertial mass MR by the rotating mass 21 is controlled (steps 3, 51, 52).

  Thus, by tuning the cutoff frequency fCU to the dominant frequency fcp, the deformation of the predetermined layer PF due to the vibration of the fcp is increased, and the transmission of the vibration of the fcp to the upper layer of the predetermined layer PF of the building B is cut off. As a result, the vibration of the upper layer can be appropriately suppressed. In this case, since the predetermined layer PF is set as the lowermost layer of the building B, it is possible to effectively obtain an effect that the vibration of the layer above the predetermined layer PF can be appropriately suppressed. In addition, the effect by 1st Embodiment can be acquired similarly.

  Next, a vibration suppression device according to an eighth embodiment of the present invention will be described. Compared with the seventh embodiment, this vibration suppressing device has the same hardware configuration as the variable rotation inertial mass damper 131 and the only difference is that the tuning control process shown in FIG. 27 is executed. In this tuning control process, unlike the case of the seventh embodiment (FIG. 26), the inertia of the variable rotary inertia mass damper 131 is adjusted so that the cutoff frequency fCU is synchronized with the near natural frequency fn described in the second embodiment. In order to control the mass MD, the displacement volume VM of the fluid pressure motor 132 is controlled. From the difference from the seventh embodiment, in the tuning control process, as is apparent from the comparison between FIG. 27 and FIG. 26, steps 11 and 12 described in the second embodiment are executed instead of step 3, thereby The displacement volume VM is controlled using the inertial mass Mds for main control calculated based on the near natural frequency fn.

  As described above, according to the eighth embodiment, during the vibration of the building B, the nearby natural frequency fn closest to the calculated dominant frequency fcp among the plurality of predetermined natural frequencies of the building B is set to the cutoff frequency fCU. More specifically, the inertial mass MD is controlled so that fCU is the same as fn (steps 11, 12, 51, and 52 in FIG. 27). In this way, by synchronizing the cutoff frequency fcu with the nearby natural frequency fn closest to the dominant frequency fcp of the input vibration among the plurality of natural frequencies of the building B, the predetermined layer PF of the predetermined layer PF due to the vibration of fn is obtained. The deformation can be increased, and the transmission of the vibration of fn to the upper layer of the predetermined layer PF of the building B can be cut off. As a result, the vibration (resonance) of the upper layer can be appropriately suppressed. In this case, since the predetermined layer PF is set as the lowermost layer of the building B, it is possible to effectively obtain an effect that the vibration of the layer above the predetermined layer PF can be appropriately suppressed.

  In the seventh and eighth embodiments, the fluid pressure motor 132 is a swash plate type, but other suitable variable displacement type fluid pressure motors such as a slant shaft type and a vane type are also used. Further, in the eighth embodiment, the fluid pressure motor 132 is configured to be able to continuously change the displacement volume VM, but may be configured to be able to change in stages. Furthermore, in the seventh and eighth embodiments, the first and second relief valves 11 and 12 are provided on the piston 3, but these may be omitted.

  Further, the inertial mass MD of the variable rotation inertial mass damper 131 is set to be the same as the near natural frequency fn in the eighth embodiment, so that the cutoff frequency fCU is the same as the dominant frequency fcp in the seventh embodiment. However, it may be controlled so as to be substantially the same as fcp and fn, respectively. In that case, instead of the dominant frequency fcp in the equation (10), a value obtained by adding or subtracting a very small predetermined value to the fcp is used, and instead of the neighborhood natural frequency fn in the equation (11), A value obtained by adding or subtracting a very small predetermined value to fn is used.

  In the seventh and eighth embodiments (tuning control processing), the inertial mass Mh due to the viscous fluid HF is ignored, the inertial mass MR due to the rotating mass 21 is regarded as the inertial mass MD of the variable rotating inertial mass damper 131, and the displacement is pushed. Although the volume VM is controlled, the control may be performed by setting MD = MR + Mh without ignoring the inertial mass Mh. In this case, in the processing after step 3 in FIG. 26, a value obtained by subtracting the inertial mass Mh from the inertial mass Mds calculated by the equation (10) is used as the inertial mass Mds. A value obtained by subtracting the inertial mass Mh from the inertial mass Mds calculated by the equation (11) is used as the inertial mass Mds. Furthermore, it goes without saying that the variations described so far with respect to the seventh and eighth embodiments may be applied in appropriate combination.

  The present invention is not limited to the first to eighth embodiments described below (hereinafter collectively referred to as “embodiments”), and can be implemented in various modes. For example, in the embodiment, the first and second connecting members EN1 and EN2 are provided so as to extend in the vertical direction. However, the former EN1 may be provided in an inverted V-shaped brace shape, and the latter EN2 may be provided as V. You may provide in the shape of a character brace. Alternatively, the first and second connecting members EN1 and EN2 may be deleted, and the variable rotary inertia mass dampers 1, 61, 101, 111, and 131 may be obliquely connected to the upper and lower beams BU and BD in a brace shape. . In this case, the variable rotational inertia mass dampers 1, 61, 101, 111, 131 may be connected to the joint between the upper beam BU and the column and the joint between the lower beam BD and the column, and are arranged in the horizontal direction. You may connect with one upper end part of the two pillars, and the other lower end part.

  Moreover, the variable rotational inertial mass dampers 1, 61, 101, 111, 131 of the embodiment are merely examples, and other appropriate variable rotational inertial mass dampers that can change the inertial mass may be used. Of course. For example, in a state where a plurality of rotating masses coaxially arranged in the axial direction with each other and an interlayer displacement accompanying the vibration of the transmitted structure are converted into a rotational motion, end portions in the axial direction of the plurality of rotating masses And a plurality of clutches for connecting / disconnecting between two adjacent rotation masses of the plurality of rotation masses (number of clutches = number of rotation masses −1) A variable rotational inertial mass damper having the following may be used.

  In the variable rotational inertial mass damper having the above configuration, the inertial mass of the entire rotational mass acting on the conversion mechanism is obtained by connecting the two adjacent rotational masses with a clutch in order from the conversion mechanism side to the opposite side. , Get bigger step by step. In this case, for example, when the number of rotating masses is three, the actual amount and diameter of each rotating mass are set as follows. That is, when the two rotating masses are connected by a clutch (the inertial mass is maximum), the cutoff frequency is synchronized with the natural frequency of the primary mode of the structure, and is opposite to the conversion mechanism. When one set of rotating masses is blocked and the other set of rotating masses are connected (inertial mass is medium), the cutoff frequency is the natural frequency of the secondary mode of the structure. When the two masses are separated by a clutch (the inertial mass is minimum), each rotation is performed so that the cutoff frequency is tuned to the natural frequency of the third-order mode of the structure. The actual mass and diameter of the mass are set.

  When the variable rotation inertial mass damper having the above-described configuration is used, the inertial mass is controlled so that the cutoff frequency is synchronized with the near natural frequency by controlling the connection / disconnection of the clutch. Of course, various conversion mechanisms as described in the embodiments and the above-described variations may be used as the conversion mechanism in this case. Alternatively, a variable rotational inertia mass damper disclosed in Japanese Patent Laid-Open No. 2016-151287 may be used.

  Furthermore, the control method of the tuning control process described in the embodiment is merely an example, and it is needless to say that other appropriate control methods may be adopted within the scope of the present invention. In the embodiment, only the variable rotational inertia mass dampers 1, 61, 101, 111, 131 are provided in the predetermined layer PF of the building B. However, other appropriate dampers such as a viscous damper, a friction damper, A history damper, a viscoelastic damper, and the like may be further provided. Furthermore, in the embodiment, the rigidity θs of the predetermined layer PF is set to a predetermined value, but is set lower than the rigidity of the other layers of the building B, thereby easily deforming the predetermined layer (absorbing vibration). The above-described effects according to the present invention may be effectively obtained by making a base isolation layer in an extreme example. In that case, in order to prevent an excessive deformation of the predetermined layer PF due to an increase in vibration of the building B, it is preferable to use the above-described viscous damper together.

  In the embodiment, the vibration suppression damper is not provided in the layer above the predetermined layer PF of the building B. However, an inertia mass damper, a viscous damper, a friction damper, a hysteresis damper, a viscoelastic damper, etc. Needless to say, an additional vibration system including a rotary inertia mass damper may be provided as in the above-described prior art. Furthermore, in the embodiment, the predetermined layer PF is set to a single lowermost layer of the building B, but may be set to other appropriate layers, or may be set to a plurality of layers. As an example in this case, FIG. 28 is a model diagram showing the variable rotation inertia mass damper 1 and the like when two layers including one layer and two layers of the building B are set as the predetermined layer PF. Further, in the embodiment, the structure in the present invention is the building B, but may be another appropriate structure having a plurality of layers. In addition, it is possible to appropriately change the detailed configuration within the scope of the gist of the present invention.

B Building (structure)
PF Predetermined layer 1 Variable rotary inertia mass damper 2 Cylinder 2d First fluid chamber 2e Second fluid chamber 3 Piston 5 First communication path 6 Second communication path HF Viscous fluid (working fluid)
11 First Relief Valve 12 Second Relief Valve M Gearmotor (Flow Conversion Mechanism)
21 Rotating mass P Gear pump (flow rate adjustment mechanism, electric pump)
51 Control device (excellent frequency acquisition means, control means)
53 Seismograph (Means for obtaining prevailing frequency)
fcp dominant frequency fn near natural frequency 61 variable rotary inertia mass damper 65 screw shaft (conversion mechanism)
66 Nut (conversion mechanism)
68 Rotating mass 69 Transmission mechanism 70 Rotating shaft 91 Control device (dominant frequency acquisition means, control means)
53 Seismograph (Means for obtaining prevailing frequency)
DESCRIPTION OF SYMBOLS 101 Variable rotation inertia mass damper 102 Rotary mass 102a Fitting hole 103 Friction material 111 Variable rotation inertia mass damper 112 Transmission mechanism 121 Control apparatus (dominant frequency acquisition means, control means)
131 Variable Rotational Inertia Mass Damper 132 Fluid Pressure Motor 132b Actuator 141 Control Device (Prominent Frequency Acquisition Unit, Control Unit)

Claims (9)

A vibration suppressing device for a structure having a plurality of layers and suppressing vibrations of the structure standing on the foundation,
A rotating mass is provided on a predetermined layer of the structure, and the interlayer displacement of the predetermined layer transmitted along with the vibration of the structure is converted into a rotational motion of the rotating mass, and the rotating mass is rotated. A variable rotational inertial mass damper configured to be able to continuously change the inertial mass generated with the
A prevailing frequency acquisition means for acquiring a prevailing frequency that is the frequency of the prevailing frequency component of the vibration input to the structure from the foundation side;
During the vibration of the structure, the inertial mass of the variable rotational inertial mass damper is adjusted so that the cutoff frequency determined by the rigidity of the predetermined layer and the inertial mass of the variable rotational inertial mass damper is synchronized with the acquired dominant frequency. Control means for controlling
A vibration suppressing device for a structure, comprising: A vibration suppressing device for a structure having a plurality of layers and suppressing vibrations of the structure standing on the foundation,
A rotating mass is provided on a predetermined layer of the structure, and the interlayer displacement of the predetermined layer transmitted along with the vibration of the structure is converted into a rotational motion of the rotating mass, and the rotating mass is rotated. A variable rotation inertial mass damper configured to be able to change the inertial mass generated when the
A prevailing frequency acquisition means for acquiring a prevailing frequency that is the frequency of the prevailing frequency component of the vibration input to the structure from the foundation side;
During the vibration of the structure, the rigidity of the predetermined layer and the inertia of the variable rotational inertia mass damper are set to a nearby natural frequency closest to the acquired dominant frequency among a plurality of predetermined natural frequencies of the structure. Control means for controlling the inertial mass of the variable rotational inertial mass damper so that the cutoff frequency determined by the mass is synchronized;
A vibration suppressing device for a structure, comprising: The variable rotational inertial mass damper is
A cylinder to which an interlayer displacement of the predetermined layer accompanying the vibration of the structure is transmitted;
The cylinder is partitioned into a first fluid chamber and a second fluid chamber filled with a working fluid, and the displacement of the predetermined layer accompanying the vibration of the structure is transmitted, whereby the cylinder is axially moved. A piston configured to slide into,
A first communication path that bypasses the piston and communicates with the first and second fluid chambers and is filled with a working fluid;
A flow conversion mechanism that is provided in the first communication path and converts the flow of the working fluid in the first communication path into a rotational motion of the rotary mass;
A second communication path that is provided in parallel with the first communication path, bypasses the piston, communicates with the first and second fluid chambers, and is filled with a working fluid;
A flow rate adjusting mechanism provided in the second communication path for adjusting the flow rate of the working fluid flowing in the second communication path;
The control means controls the inertial mass of the variable rotational inertial mass damper during vibration of the structure by adjusting the flow rate of the working fluid flowing through the second communication path via the flow rate adjusting mechanism. The vibration suppression device for a structure according to claim 1 or 2, wherein   4. The structure vibration suppressing device according to claim 3, wherein the flow rate adjusting mechanism includes an electric pump for sending the working fluid in the second communication path.   The piston opens when the pressure of the working fluid in the first fluid chamber reaches a first predetermined pressure, and the first relief valve communicates the first and second fluid chambers, and the second The second relief valve is provided, which opens when the pressure of the working fluid in the fluid chamber reaches a second predetermined pressure and communicates the second and first fluid chambers with each other. 5. A vibration suppression device for a structure according to 3 or 4. The variable rotational inertial mass damper is
A cylinder to which an interlayer displacement of the predetermined layer accompanying the vibration of the structure is transmitted;
The cylinder is partitioned into a first fluid chamber and a second fluid chamber filled with a working fluid, and the displacement of the predetermined layer accompanying the vibration of the structure is transmitted, whereby the cylinder is axially moved. A piston configured to slide into,
A bypass passage bypassing the piston, communicating with the first and second fluid chambers, and filled with a working fluid;
A variable displacement fluid pressure motor configured to convert the pressure energy of the working fluid flowing in the communication path into rotational energy and change the displacement volume;
An actuator for changing the displacement volume of the fluid pressure motor;
A rotating mass that rotates by transmitting rotational energy converted by the fluid pressure motor;
The control means controls the inertial mass of the variable rotary inertial mass damper during vibration of the structure by adjusting a displacement volume of the fluid pressure motor via the actuator. Item 3. The structure vibration suppression device according to Item 1 or 2. The variable rotational inertial mass damper is
A conversion mechanism that converts the interlayer displacement of the predetermined layer transmitted along with the vibration of the structure into rotational power;
A stepless transmission mechanism configured to transmit the rotational power converted by the conversion mechanism to the rotating mass in a state of being shifted, and to change the transmission ratio steplessly;
The said control means controls the inertial mass of the said variable rotation inertial mass damper by setting the said transmission gear ratio of the said transmission mechanism during the vibration of the said structure, It is characterized by the above-mentioned. Vibration suppression device for structures. The variable rotational inertial mass damper is
A conversion mechanism that converts the interlayer displacement of the predetermined layer transmitted along with the vibration of the structure into rotational power;
A stepped transmission mechanism that transmits the rotational power converted by the conversion mechanism to the rotary mass in a state where the rotational power is changed at one transmission ratio selected from a plurality of predetermined transmission ratios;
The plurality of transmission ratios are a plurality of cutoff frequencies obtained respectively corresponding to each of the plurality of transmission ratios when each of the plurality of transmission ratios is selected during vibration of the structure. The structure is set so as to be tuned corresponding to each of a plurality of predetermined natural frequencies.
The control means selects the speed ratio corresponding to the near natural frequency of the structure from the plurality of speed ratios of the speed change mechanism so that the cutoff frequency is synchronized with the near natural frequency. 3. The vibration suppression device for a structure according to claim 2, wherein the inertial mass of the variable rotation inertial mass damper is controlled. The speed change mechanism has a rotation shaft that is transmitted in a state where the rotational power converted by the conversion mechanism is changed,
The rotating mass is formed with a fitting hole,
A friction material fitted between the rotary shaft and the inner peripheral surface of the fitting hole;
The vibration suppression device for a structure according to claim 7 or 8, wherein the rotating mass is connected to the rotating shaft via the friction material.

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