JP2022098305A - Vibration control device - Google Patents

Abstract

To provide a vibration control device which properly adjusts a block frequency according to a change of an excitation frequency, blocks the transmission of an excitation force to a structure, and can sufficiently suppress peripheral vibration.SOLUTION: A vibration control device for suppressing vibration transmitted to a periphery from a foundation B to which an excitation force is applied comprises: a floating floor F arranged at an upper side of the foundation B, and applied with the excitation force; a support spring 2 arranged between the foundation B and the floating floor F; and a second rotation inertia mass damper 4 arranged between the foundation B and the floating floor F in parallel with the support spring 2, converting a relative displacement of the floating floor F with respect to the foundation B which is applied with the excitation force to the rotation movement of a flywheel 16, and generating a rotation inertia mass. The vibration control device changes an equivalent mass md of the second rotation inertia mass damper 4 so that a block frequency fs for blocking the transmission of vibration to the foundation B from the floating floor F coincides with an acquired excitation frequency fa. The vibration control device also comprises a synchronization mass damper 5 synchronizing with a natural frequency fn1 of the floating floor F as a whole between the foundation B and the floating floor F.SELECTED DRAWING: Figure 10

Description

The present invention relates to a vibration damping device that suppresses vibration transmitted from a structure on which a vibrating force acts to the periphery.

As a conventional vibration damping device of this type, for example, one disclosed in Patent Document 1 is known. This vibration damping device has a floating foundation oscillatingly installed on the outer foundation of the structure, and a spring, a viscous damper (dashpot) and a rotary inertial mass damper arranged in parallel between the outer foundation and the floating foundation. I have. The rotary inertia mass damper is, for example, a ball screw type having a screw shaft, a ball and a nut, and the rotating body is fixed to the screw shaft, the screw shaft is connected to the floating foundation, and the nut is connected to the outer foundation. Has been done. Further, the natural frequency (cutting frequency) determined by the rotational inertia mass by the rotational inertia mass damper and the spring constant (rigidity) of the spring is set to match the vibration frequency acting on the floating foundation.

In this configuration, when an exciting force acts on the floating foundation, the relative displacement of the floating foundation with respect to the outer foundation is converted into the rotational motion of the rotating body of the rotary inertial mass damper, and the rotational inertial mass effect is exerted. The foundation is lengthened. In addition, the breaking frequency determined by the rotational inertia mass and the spring constant matches the vibration frequency to the floating foundation, so that the reaction force of the outer foundation at the vibration frequency is reduced, and the periphery from the outer foundation via the ground. The vibration transmitted to is suppressed.

Such a vibration damping device is used, for example, as a countermeasure against vertical vibration in a live house or the like. This "vertical glue" is an action in which a large number of spectators repeat the tiptoe in small steps according to the tempo of the music during the concert, and the vibration caused by the vertical glue (hereinafter referred to as "vertical glue vibration") is transmitted to the periphery of the building. It is known to cause vibration damage. When the vibration damping device is used as a countermeasure against vertical vibration, the hall floor on which a large number of spectators stand is configured as a floating floor above the foundation of the building, and a spring, a viscous damper and a rotational inertia mass damper are installed between the foundation and the floating floor. At the same time as being arranged, the breaking frequency due to the rotational inertia mass or the like is set so as to match the vibration frequency to the floating floor due to the vertical glue.

Japanese Patent No. 4936174

Since the above-mentioned vertical glue is performed according to the tempo of the music to be played, the vibration frequency due to the vertical glue vibration changes, for example, in the range of 2.0 to 3.5 Hz depending on the tempo of the music. On the other hand, in the conventional vibration damping device, the breaking frequency is set to a predetermined fixed value by the rotational inertia mass of the rotational inertia mass damper and the spring constant of the spring. For this reason, if the vibration frequency changes according to the change in the performance music during the concert, the breaking frequency does not match the changed vibration frequency, so the vertical vibration is not sufficiently cut off and the basics. As a result of not being able to sufficiently reduce the reaction force of the above, it is not possible to sufficiently suppress the longitudinal vibration transmitted from the foundation to the surroundings via the ground.

Further, in the conventional vibration damping device, a viscous damper is provided between the foundation and the floating floor in parallel with the spring and the rotational inertia mass damper. The viscous resistance of this viscous damper acts to limit the movement of the floating floor in a state where the inertial force due to the rotational inertial mass and the spring force are balanced when the longitudinal vibration due to the breaking frequency is cut off. As a result, the reaction force of the foundation increases, and the blocking effect of the longitudinal vibration is reduced.

The present invention has been made to solve such a problem, and appropriately adjusts the breaking frequency according to the change of the vibration frequency, thereby transmitting the vibration force to the structure. It is an object of the present invention to provide a vibration damping device capable of sufficiently suppressing ambient vibration by shutting off.

In order to achieve this object, the invention according to claim 1 is a vibration damping device for suppressing vibration transmitted from a structure on which a vibrating force acts to the periphery, and is arranged on the upper side of the structure. It has a floating floor on which a vibrating force acts, a support spring provided between the structure and the floating floor to support the floating floor, and a rotating mass, and is provided in parallel with the support spring between the structure and the floating floor. By converting the relative displacement of the floating floor with respect to the structure when a vibration force is applied into the rotational motion of the rotating mass, a rotational inertia mass is generated, and the rotational inertia mass is configured so that the rotational inertia mass can be changed. , The vibration from the floating floor to the structure, which is determined by the vibration frequency acquisition means that acquires the frequency of the excitation force as the vibration frequency, the rotational inertia mass of the rotary inertia mass damper, and the spring constant of the support spring. A control means for changing the rotational inertial mass by the rotary inertial mass damper and a floating floor provided between the structure and the floating floor so that the breaking frequency for interrupting the transmission matches the acquired excitation frequency. It is characterized by being provided with a tuning mass damper that is tuned to the entire natural frequency.

In this vibration damping device, a floating floor is arranged on the upper side of the structure, and a support spring and a rotary inertial mass damper are provided in parallel between the structure and the floating floor. Further, the rotary inertial mass damper is configured so that the rotary inertial mass can be changed. When an exciting force acts on the floating floor, this exciting force is supported by the support spring, and the floating floor is displaced with respect to the structure, and the relative displacement is converted into the rotational motion of the rotating mass in the rotary inertial mass damper. By doing so, a rotational inertia mass is generated.

Further, the frequency of the vibrating force is acquired as the vibrating frequency, and the breaking frequency for blocking the transmission of vibration from the floating floor to the structure matches the acquired vibrating frequency. Rotational inertial mass The rotational inertial mass due to the damper is changed. As a result, the breaking frequency is adjusted and matches the vibration frequency, so that the inertial force due to the rotational inertial mass and the spring force of the support spring cancel each other out. As a result, the transmission of the exciting force from the floating floor to the structure can be blocked, and the surrounding vibration can be sufficiently suppressed.

Further, according to this configuration, a tuning mass damper is provided between the structure and the floating floor, and this tuning mass damper reflects the spring force of the support spring and the rotational inertia mass due to the rotational inertia mass damper of the entire floating floor. Synchronized with the natural frequency composed of mass. By this tuning, the vibration damping effect of the floating floor in the vicinity of the natural frequency can be enhanced. Further, unlike the above-mentioned conventional device in which a viscous damper is provided between the structure and the floating floor, the viscous damper is in a state where the inertial force due to the rotational inertial mass and the spring force of the support spring cancel each other out when the exciting force is cut off. Since the viscous resistance of the above does not act, the breaking effect of the exciting force can be maintained satisfactorily.

According to the second aspect of the present invention, in the vibration damping device according to the first aspect, the tuning mass damper is configured so that the natural frequency can be changed, and the control means is the rotational inertia due to the changed rotational inertia mass damper. It is characterized in that the natural frequency of the tuned mass damper is changed to tune to the natural frequency of the entire floating floor according to the mass.

As described above, when the rotational inertia mass of the rotary inertia mass damper is changed in order to match the breaking frequency with the excitation frequency, the natural frequency of the entire floating floor changes. According to this configuration, when the rotational inertia mass is changed, the natural frequency of the tuning mass damper is changed accordingly, and the natural frequency of the entire floating floor is tuned. As a result, even if the natural frequency of the entire floating floor changes due to the adjustment of the breaking frequency, it is possible to perform good tuning with the tuning mass damper, and the vibration damping effect of the floating floor near the natural frequency is good. Can be maintained at.

The invention according to claim 3 is the vibration damping device according to claim 1 or 2, wherein the rotary inertial mass damper is filled with a working fluid, and is a cylinder connected to one of a structure and a floating floor, and a cylinder. The first fluid chamber is divided into a first fluid chamber and a second fluid chamber, and the piston is bypassed with the piston connected to the other of the structure and the floating floor. And the flow of the working fluid in the first communication passage and the first communication passage provided in the first communication passage and the second communication passage connected in parallel to each other through the connection portion while communicating with the second fluid chamber. Is provided at the connection between the gear motor that generates the rotational inertia mass by converting the rotational motion of the rotating mass, and the communication passage between the first and second fluid chambers is the first communication passage and the second communication. It is characterized by having a switching valve for switching to one of the passages.

According to this configuration, the rotary inertial mass damper is a gear motor type using a working fluid, and operates as follows. When a vibrating force acts on the floating floor and the floating floor is displaced with respect to the structure, this relative displacement is transmitted to the cylinder and piston, and as the piston moves in the cylinder, the first or second fluid chamber Working fluid is pushed out by the piston. In this case, when the communication passage between the first and second fluid chambers is switched to the first communication passage side by the switching valve, the working fluid flows in the first communication passage, so that the rotation is driven to rotate. The rotational inertia mass due to the rotational moment of inertia of the mass is obtained. On the other hand, when the communication passage is switched to the second communication passage side, the working fluid does not flow in the first communication passage, so that the rotational inertia mass due to the rotational moment of inertia of the rotating mass cannot be obtained.

As described above, this rotary inertial mass damper is a gear motor type using a working fluid, and the rotary inertial mass can be obtained only by switching the flow path of the working fluid to the first or second continuous passage by the switching valve. It can be easily changed. As a result, compared to the case where a ball screw type damper is used as the rotational inertia mass damper as in a conventional device and the rotational inertia mass is changed by changing the rotational radius of the weight with an electric motor. , It is possible to realize simplification of configuration and cost reduction.

It is a figure which shows the vibration damping device by 1st Embodiment of this invention. It is sectional drawing which shows the 1st rotary inertia mass damper. It is sectional drawing which shows the 2nd rotary inertial mass damper in the communication state of the 1st communication passage by a solenoid valve. It is sectional drawing which shows the 2nd rotary inertial mass damper in the communication state of the 2nd communication passage by a solenoid valve. It is a figure which models and shows the foundation, the floating floor and the vibration damping device. It is a figure which shows (a) the relationship between the displacement, the phase of velocity and acceleration, and (b) the relationship between displacement and a resistance force of a vibrated floating floor. It is a table which shows the relationship between the ON number and the breaking frequency of the solenoid valve of the 2nd rotary inertial mass damper. It is a block diagram which shows the control apparatus of 1st Embodiment. It is a flowchart which shows the solenoid valve control process which is executed in the control apparatus of FIG. It is a figure which shows the relationship between the vibration frequency of a floating floor obtained by 1st Embodiment, and the acceleration response magnification in 3 cases where the breaking frequency is different. It is a figure which shows the vibration damping device by the 2nd Embodiment of this invention. It is a block diagram which shows the control apparatus of 2nd Embodiment. It is a flowchart which shows the solenoid valve control process which is executed in the control device of FIG. It is a figure which shows the relationship between the vibration frequency of a floating floor obtained by 2nd Embodiment, and the acceleration response magnification in 3 cases where the breaking frequency is different. It is a figure which compares and shows the characteristic of the acceleration response magnification with respect to the vibration frequency in the case where the vibration damping device does not have a viscous damper, when it has a viscous damper, and when it has a tuning mass damper.

Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings. The vibration damping device of the embodiment is installed as a countermeasure against vertical vibration in a live house, for example. Reference numeral B in FIG. 1 is a foundation (slab foundation) of a live house building, and the foundation B is supported by the ground G via a plurality of piles P.

The vibration damping device A1 of the first embodiment shown in FIG. 1 is arranged above the foundation B and is between the floating floor F configured as a hall floor on which a large number of spectators in a live house stand and between the foundation B and the floating floor F. The anti-vibration unit U provided in the above is provided. The anti-vibration unit U suppresses vertical vibration by blocking the vibrating force due to the vertical glue acting on the floating floor F and reducing the force transmitted from the foundation B to the ground G. The vibration isolation unit U includes a support spring 2, a first rotary inertial mass damper 3, and a second rotary inertial mass damper 4. A predetermined number of these components 2 to 4 are provided, and they are arranged in parallel with each other.

Although not shown, the support spring 2 is composed of, for example, a disc spring unit assembled by stacking a large number of disc springs in the vertical direction, and the disc spring unit as a whole has a predetermined spring constant (rigidity).

As shown in FIG. 2, the first rotary inertial mass damper 3 is a gear motor type using a working fluid HF, and is slidably provided in a cylinder 12 filled with the working fluid HF and in the cylinder 12. , The piston 13 that partitions the inside of the cylinder 12 into the first and second fluid chambers 12a and 12b, the communication passage 14 that bypasses the piston 13 and communicates with the first and second fluid chambers 12a and 12b, and the communication passage 14. The arranged gear motor 15 is provided. The working fluid HF is composed of a fluid having an appropriate viscosity, for example, silicone oil.

The gear motor 15 is, for example, an external type, and has an input gear 15b and an output gear 15c that are housed in a casing 15a communicating with the communication passage 14 and mesh with each other, and an output shaft 15d integrally connected to the output gear 15c. Have. A flywheel 16 as a rotating mass is integrally connected to the output shaft 15d.

The first rotary inertial mass damper 3 has a foundation B and a floating floor F via a first attachment FL1 connected to a cylinder 12 and a second attachment FL2 connected to a piston rod 17 integrated with a piston 13. It is installed between.

In the first rotary inertial mass damper 3 having the above configuration, for example, when the floating floor F is displaced with respect to the foundation B in response to the occurrence of vertical shear vibration in the floating floor F, the piston 13 moves in the cylinder 12. As a result, the working fluid HF flows into the communication passage 14 from one of the first and second fluid chambers 12a and 12b, passes through the casing 15a, and flows toward the other of the first and second fluid chambers 12a and 12b. do.

By converting the flow of the working fluid HF in the casing 15a into the rotational movement of the output gear 15c of the gear motor 15 and rotating the flywheel 16, the rotational inertia mass due to the rotational moment of inertia (hereinafter, "first equivalent"). "Mass") md1 is obtained. Further, the inertial mass (hereinafter referred to as “second equivalent mass”) md2 due to the flow of the working fluid HF in the communication passage 14 is obtained.

In this case, the first equivalent mass md1 and the second equivalent mass md2 are represented by the following equations (1) and (2), respectively, and the sum of both md1 and md2 is the equivalent mass md of the first rotational inertia mass damper 3. (Equation (3)).

Further, the piston 13 is formed with a plurality of holes penetrating in the axial direction (only two are shown), and the first relief valve 18 and the second relief valve 19 are provided in these holes.

The first relief valve 18 is composed of a valve body and a spring that urges the valve body to the valve closing side, and when the piston 13 moves to the left in FIG. 2, it operates in the first fluid chamber 12a. The valve is opened when the pressure of the fluid HF rises and reaches a predetermined upper limit value. As a result, the pressure of the working fluid HF in the first fluid chamber 12a is released to the second fluid chamber 12b side, so that the pressure is limited to the upper limit or less. The second relief valve 19 has the same configuration as the first relief valve 18, and when the piston 13 moves to the right in FIG. 2, the pressure of the working fluid HF in the second fluid chamber 12b becomes the upper limit value. When the valve is reached, the valve is opened and the pressure of the working fluid HF in the second fluid chamber 12b is released to the first fluid chamber 12a side, so that the pressure is limited to the upper limit or less.

Next, the second rotational inertia mass damper 4 will be described with reference to FIGS. 3 and 4. The second rotary inertial mass damper 4 is equipped with a solenoid valve 21 and is parallel to the first rotary inertial mass damper 3 in FIG. 2 as a communication passage communicating with the first and second fluid chambers 12a and 12b. It has the first and second communication passages 14a and 14b, and is provided with a solenoid valve 21 for switching between the first and second communication passages 14a and 14b. Hereinafter, the same reference numerals will be given to the components of the second rotary inertial mass damper 4, which is the same as the first rotary inertial mass damper 3, and the description will be given focusing on the different points.

As shown in FIG. 3, the communication passage has two common portions 14c and 14d communicating with the first and second fluid chambers 12a and 12b, respectively, and the first and first communication passages connected in parallel to the common portions 14c and 14d. It is composed of double passages 14a and 14b. A gear motor 15 similar to the first rotary inertial mass damper 3 is provided in the first continuous passage 14a. On the other hand, the second continuous passage 14b is not provided with a device such as the gear motor 15, and has only a passage.

The solenoid valve 21 is provided at a connection portion between the common portion 14c on the first fluid chamber 12a side and the first and second continuous passages 14a and 14b. The solenoid valve 21 is a spool type and has a sleeve 22 and a solenoid 23, a plunger 24, a spool 25, and a return spring 26 housed in the sleeve 22.

The sleeve 22 extends in the vertical direction, and its internal space communicates with the first continuous passage 14a, the common portion 14c, and the second continuous passage 14b in order from the upper side at different positions in the vertical direction. The plunger 24 is configured to be sucked downward by the solenoid 23 when the solenoid 23 is excited. The spool 25 is integrated with the plunger 24, extends downward from the plunger 24, is arranged vertically, and connects the first valve body 25a and the second valve body 25b inscribed in the sleeve 22 and both valve bodies 25a and 25b. It is composed of a valve shaft 25c. ON / OFF of the solenoid valve 21 (excitation / non-excitation of the solenoid 23) is controlled by a control device 31 described later. The return spring 26 is composed of a coil spring and is arranged at the bottom of the sleeve 22. The integrated plunger 24 and the spool 25 are constantly urged upward via the second valve body 25b.

Like the first rotary inertial mass damper 3, the second rotary inertial mass damper 4 has a foundation B via a first mounting tool FL1 connected to the cylinder 12 and a second mounting tool FL2 connected to the piston rod 17. It is installed between the floating floor F and the floating floor F.

In the second rotational inertia mass damper 4 having the above configuration, when the floating floor F is displaced with respect to the foundation B due to vertical glue vibration generated in the floating floor F, the piston 13 is generated as in the first rotational inertia mass damper 3. As the fluid moves in the cylinder 12, the working fluid HF flows out from the first or second fluid chambers 12a and 12b. In this state, when the solenoid valve 21 is turned off and the solenoid 23 is in the non-excited state, the spool 25 integrated with the plunger 24 moves upward by the spring force of the return spring 26, and is in the first position shown in FIG. Located in. In this first position, the first valve body 25a of the spool 25 opens the first continuous passage 14a, and at the same time, the second valve body 25b closes the second continuous passage 14b.

As a result, as shown in FIG. 3, the working fluid HF flowing out from the first or second fluid chambers 12a and 12b does not flow into the closed second communication passage 14b and is inside the open first communication passage 14a. Flow. Therefore, the operation of the second rotary inertial mass damper 4 at this time is basically the same as that of the first rotary inertial mass damper 3 described above, and the flow of the working fluid HF in the first continuous passage 14a is the fly wheel. By being converted into the rotational motion of 16, the first equivalent mass md1 (Equation (1)) due to the rotational inertia moment is obtained, and the second equivalent mass md2 (Equation (2)) is obtained due to the flow of the working fluid HF. Be done. Further, the sum of both equivalent masses md1 and md2 becomes the equivalent mass md of the second rotational inertia mass damper 4 (Equation (3)).

On the other hand, as described above, the floating floor F is displaced with respect to the foundation B due to longitudinal vibration or the like, and the piston 13 moves in the cylinder 12 to cause the working fluid HF from the first or second fluid chambers 12a and 12b. When the solenoid valve 21 is turned on while the fluid is flowing out, the spool 25 integrated with the plunger 24 moves downward against the spring force of the return spring 26 due to the excitation of the solenoid 23. It is located at the second position shown in FIG. In this second position, the first valve body 25a of the spool 25 closes the first connecting passage 14a, and at the same time, the second valve body 25b opens the second connecting passage 14b.

As a result, as shown in FIG. 4, the working fluid HF flowing out from the first or second fluid chambers 12a and 12b does not flow into the closed first communication passage 14a, and only the open second communication passage 14b. Flow. Therefore, the flywheel 16 provided on the first continuous passage 14a side does not rotate, the first equivalent mass md1 becomes 0, and only the second equivalent mass md2 (formula (2)) due to the flow of the working fluid HF becomes. can get. Therefore, the equivalent mass md of the second rotational inertia mass damper 4 is extremely small md2 (≈0). As described above, the equivalent mass md of the second rotary inertial mass damper 4 is changed by turning the solenoid valve 21 ON / OFF.

In the case of FIGS. 3 and 4, the working fluid HF flows in the first passage 14a and the second passage 14b, so that a relatively small viscous damping effect is exhibited. In particular, in the case of FIG. 4, since the mass effect of the second rotational inertia mass damper 4 is extremely small (md≈0), it functions as a viscous damper having a small damping coefficient.

When the vibration damping device A1 is modeled from the above configuration, as shown in FIG. 5, between the foundation B and the floating floor F having a mass of M, (a) the support spring 2 is formed, and the spring constant is K. The spring element, which is (b), and the flywheel 16 of the first and second rotary inertial mass dampers 3 and 4, and the inertial connecting element having a variable inertial mass of m (= Σmd) are connected in parallel to each other. Become a model. In this configuration, when a vibration force in the vertical direction acts on the floating floor F, the spring force Fk of the support spring 2 and the inertial force Fm of the flywheel 16 act on the floating floor F as a resistance force (reaction force) to the vibration force. It works.

In this case, when the exciting force is a harmonic vibration type, as shown in FIG. 6A, the displacement DIS (= u) of the floating bed F and the acceleration ACC are in an antiphase relationship, so that the figure (b) is shown. ), The spring force Fk (= K · u) of the support spring 2 depending on the displacement DIS and the inertial force Fm (= −mω2 · u) of the fly wheel 16 depending on the acceleration ACC have opposite gradients to each other. become. Further, the magnitude of the gradient of the inertial force Fm changes according to the vibration frequency to the floating floor F, and when it matches that of the spring force Fk, the spring force Fk and the inertial force Fm cancel each other out, and both of them cancel each other out. When the sum becomes 0, the transmission of the exciting force (vibration) to the foundation B is cut off. The frequency at which the transmission of vibration from the floating floor F to the foundation B is cut off is called the cutoff frequency fs.

The breaking frequency fs is determined based on the spring constant K of the entire support spring 2 and the equivalent mass m of the first and second rotary inertial mass dampers 3 and 4, and is calculated by the following equation (4).

Therefore, since the equivalent mass md of this equation (4) and the second rotary inertial mass damper 4 is variable according to the ON / OFF of the solenoid valve 21, it is cut off by the ON / OFF number of the plurality of solenoid valves 21. The frequency fs can be changed (adjusted). An example thereof will be described below.

For example, the mass M of the floating floor F = 1000 ton, the spring constant K = 39478 kN / m of the entire support spring 2, the equivalent mass md = 20.5 ton per unit of the first rotational inertia mass damper 3, and the electromagnetic valve 21 is in the OFF state. At this time, the equivalent mass md per unit of the second rotational inertia mass damper 4 is 24 ton, the number of installations of the first rotational inertia mass damper 3 is 4, and the number of installations of the second rotational inertia mass damper 4 is 7.

In this example, when all the solenoid valves 21 of the seven second rotary inertial mass dampers 4 are OFF, the breaking frequency fs becomes the minimum, and from the equation (4),
fs = (1 / 2π) square (K / m)
= (1 / 2π) square (39478 / (20.5 × 4 + 24 × 7))
= (1 / 2π) square (39478/250)
= Set to about 2.0 Hz.

Similarly, when two solenoid valves 21 are OFF and five solenoid valves 21 are ON among the seven second rotational inertia mass dampers 4, the breaking frequency fs becomes an intermediate value.
fs = (1 / 2π) sqrt (39478 / (20.5 × 4 + 24 × 2))
= (1 / 2π) square (39478/130)
= Approximately 2.75 Hz is set.

Similarly, when all the solenoid valves 21 of the seven second rotational inertia mass dampers 4 are ON, the breaking frequency fs becomes maximum.
fs = (1 / 2π) square (39478 / (20.5 × 4 + 0))
= (1 / 2π) square (39478/82)
= Set to about 3.5 Hz.

As described above, as for the breaking frequency fs, the larger the ON number Non of the electromagnetic valve 21 of the second rotary inertial mass damper 4, the smaller the equivalent mass m of the first and second rotary inertial mass dampers 3 and 4 as a whole. By becoming, it is set to a larger value. In this example, the solenoid valve 21 is set in a range of 2.0 to 3.5 Hz, which is a frequency range in which longitudinal vibration occurs, in eight stages according to the ON number Non = 0 to 7. FIG. 7 summarizes the relationship between the ON number Non of the solenoid valve 21 and the breaking frequency fs.

As shown in FIG. 1, the vibration damping device A1 further includes a plurality of tuning mass dampers 5 provided between the foundation B and the floating floor F. The tuning mass damper 5 is for enhancing the vibration damping effect of the floating floor F by tuning with the primary natural frequency in the vertical direction of the entire floating floor F. Each tuning mass damper 5 includes a spring 6 whose upper end is connected to the floating floor F, an attenuator (not shown) arranged in parallel with the spring 6, and a mass body 7 connected to the spring 6 and the attenuator. Have.

The specifications of the tuned mass damper 5 (spring constant ktmd of the spring 6, damping coefficient ctmd of the attenuator, and mass mtmd of the mass body 7) are such that the natural frequency of the tuned mass damper 5 is 1 in the vertical direction of the entire floating floor F. It is set to tune to the next natural frequency fn1.

The primary natural frequency fn1 of the entire floating floor F is the sum of the mass M of the floating floor F and the equivalent mass m of the first and second rotary inertial mass dampers 3 and 4, and the spring of the entire support spring 2. It is calculated by the following equation (5) based on the constant K. Therefore, the primary natural frequency fn1 changes accordingly when the equivalent mass md of the second rotational inertia mass damper 4 is changed in order to adjust the breaking frequency fs.

For example, as described above, when the mass M = 1000 ton, the spring constant K = 39478 kN / m, and the breaking frequency fs is set to 2.75 Hz, the first and second rotational inertia mass dampers. Since the equivalent mass m = 130 ton of all 3 and 4, the primary natural frequency fn1 is
fn1 = (1 / 2π) sqrt (K / (M + m))
= (1 / 2π) square (39478 / (1000 + 130))
= 0.94 Hz is calculated.
Further, the primary natural period Tn1 is Tn1 = 1 / fn1 = 1.06s.

On the other hand, when the breaking frequency fs is set to 2.0 Hz, the equivalent mass m = 250 ton, so that fn1 = 0.89 Hz and Tn1 = 1.12 s. Further, when the breaking frequency fs is set to 3.5 Hz, the equivalent mass m = 82 ton, so that fn1 = 0.96 Hz and the primary natural period Tn1 = 1.04 s.

In the present embodiment, the specifications of the tuning mass damper 5 are the primary natural frequencies of the floating bed F when the natural frequency is set to fs = 2.75 Hz among the plurality of breaking frequency fs. It is set to tune to fn1 (= 0.94 Hz).

As shown in FIG. 8, each solenoid valve 21 of the second rotary inertial mass damper 4 is connected to the control device 31. The control device 31 is composed of a microcomputer including a CPU, RAM, ROM, an I / O interface (none of which is shown), and the like. As will be described later, the control device 31 controls ON / OFF of the solenoid valve 21 according to the vibration frequency fa to the floating floor F.

Next, the operation of the vibration damping device A1 having the above configuration will be described. As described above, when the floating floor F is displaced with respect to the foundation B in response to the vertical glue vibration generated in the floating floor F, each first rotational moment of inertia mass damper 3 operates, and the piston 13 in the cylinder 12 operates. An equivalent mass md consisting of the sum of the first equivalent mass md1 due to the rotational moment of inertia of the fly wheel 16 and the second equivalent mass md2 due to the flow of the working fluid HF in the first continuous passage 14a is obtained. By adding the equivalent mass md of the first rotational inertia mass damper 3 to the mass of the floating floor F, the vibration of the floating floor F becomes longer.

Further, during the generation of this longitudinal vibration, the control device 31 executes the solenoid valve control process shown in FIG. In this electromagnetic valve control process, the second rotation is performed so that the breaking frequency fs that cuts off the transmission of vibration from the floating floor F to the foundation B matches the vibration frequency fa that is applied to the floating floor F due to the vertical inertial vibration. It controls the ON number Non of the electromagnetic valve 21 of the inertial mass sensor 4, and is executed at predetermined time intervals.

In this process, first, in step 1, the vibration frequency fa to the floating floor F is acquired. The vibration frequency fa is generally determined by the tempo of the music being played. Therefore, the organizer of the live concert determines the vibration frequency fa in advance for the music to be performed, and manually inputs the vibration frequency fa to the control device 31 according to the actual progress of the concert. It is possible. The control device 31 reads out and acquires the input vibration frequency fa. Alternatively, instead of such manual input, the control device 31 receives the music being played, and automatically calculates and determines the vibration frequency fa according to the tempo of the music from the analysis result of the signal. You may try to do it. Further, a load cell for measuring the vibration force may be installed at a part of the floating floor F, and the vibration frequency fa may be automatically calculated and determined from the analysis result of the signal.

Next, in step 2, the ON number Non of the solenoid valve 21 of the second rotational inertia mass sensor 4 is calculated according to the acquired vibration frequency fa. This calculation is performed, for example, by setting vibration frequency fa = breaking frequency fs and searching the table of FIG. 7 described above according to the breaking frequency fs. If the vibrating frequency fa acquired in step 1 does not match any of the plurality of breaking frequency fs in FIG. 7, the ON number Non corresponding to the breaking frequency fs closest to the vibrating frequency fa. Is selected.

Next, in step 3, a drive signal is output to the solenoid valves 21 having a number equal to the calculated ON number Non, and these solenoid valves 21 are turned ON. As a result, the equivalent mass m of the first and second rotary inertial mass dampers 3 and 4 is controlled so that the breaking frequency fs matches the vibrating frequency fa. As a result, the transmission of the vertical glue vibration from the floating floor F to the foundation B is cut off, and the transmission of the vertical glue vibration to the periphery is suppressed.

FIG. 10 shows the relationship between the vibration frequency fa of the floating floor F and the acceleration response magnification Racc, which is obtained when the cutoff frequency fs is set according to the present embodiment, (a) fs = 2.0 Hz, (b). ) Fs = 2.75 Hz and (c) fs = 3.5 Hz are shown together with the above-mentioned conventional examples. The acceleration response magnification Racc is defined as the ratio of the acceleration of the foundation B to the acceleration of the floating floor F, and represents the degree of transmission of the exciting force (vibration) from the excited floating floor F to the foundation B. In, it is synonymous with the reaction force response ratio (the ratio of the reaction force of the foundation B to the vibration force to the floating floor F).

First, in both the embodiment and the conventional example, the acceleration response magnification Racc shows a maximum value when the vibration frequency fa is near the natural frequency (= about 1 Hz) of the floating floor F, and the vibration vibration. It decreases as the number fa increases.

In the conventional example, since the rotational inertia mass due to the rotational inertia mass damper is constant, the breaking frequency fs'is set to a constant value (= about 3 Hz) regardless of the vibration frequency fa, and becomes the vibration frequency fa. The relationship with the acceleration response magnification Racc is also constant. Therefore, when the actual vibrating frequency fa deviates from the breaking frequency fs', the acceleration response magnification Racc is not sufficiently reduced and the longitudinal vibration cannot be sufficiently cut off. Further, when the vibration frequency fa is near the breaking frequency fs', the acceleration response magnification Racc is reduced to almost the minimum value, but the viscous resistance of the viscous damper acts at the time of breaking, so that the valley of the acceleration response magnification Racc is formed. It becomes shallow (see FIG. 15), and the vertical vibration cannot be sufficiently blocked.

On the other hand, in the embodiment, the cutoff frequency fs is set so as to match the actual vibration frequency fa of the acquired floating floor F, and the second cutoff frequency fs is obtained. The ON number Non of the electromagnetic valve 21 of the rotary inertial mass damper 4 is controlled, and the equivalent mass m of the first and second rotary inertial mass dampers 3 and 4 as a whole is adjusted. As a result, as shown in FIGS. 10 (a) to 10 (c), the longitudinal vibration is satisfactorily cut off at each set breaking frequency fs, and the acceleration response magnification Racc becomes the minimum. Further, unlike the conventional example, the viscous resistance of the viscous damper does not act at the time of breaking, and the valley of the acceleration response magnification Racc is maintained in a deep state (see FIG. 15), so that the longitudinal vibration can be sufficiently cut off. can.

Further, in the embodiment, the natural frequency of the tuning mass damper 5 is tuned to the primary natural frequency fn1 (= about 1 Hz) in the vertical direction of the entire floating floor F, so that the peak of the acceleration response magnification Racc in the vicinity thereof is , The value becomes as small as the case where the viscous damper is applied in the conventional example (see FIG. 15). As a result, it is possible to enhance the vibration damping effect on the primary natural frequency fn1 of the entire floating floor F.

As described above, in the present embodiment, the tuning mass damper 5 is synchronized with the primary natural frequency fn1 of the entire floating floor F when the natural frequency is the breaking frequency fs = 2.75Hs. Is set to. Therefore, when the breaking frequency fs = 2.75 Hs, the tuning by the tuning mass damper 5 is performed well, and as a result, as shown in FIG. 10B, the peak of the acceleration response magnification Racc is smaller and smaller than that of the conventional example. A good vibration damping effect can be obtained.

On the other hand, when the breaking frequency fs = 2.0 Hz or 3.5 Hs, the natural frequency of the tuning mass damper 5 deviates from the primary natural frequency fn1 of the entire floating floor F, so that the tuning mass damper 5 is used. As a result of poor tuning, as shown in FIGS. (A) and (c), the peak of the acceleration response magnification Racc is not minimized as in the conventional example, and a good vibration damping effect cannot be obtained. .. The vibration damping device A2 according to the second embodiment described below improves this point.

As shown in FIG. 11, the vibration damping device A2 of the second embodiment has a variable natural frequency instead of the tuning mass damper 5 as compared with the vibration damping device A1 of the first embodiment shown in FIG. A certain second tuning mass damper 35 is provided. The second tuning mass damper 35 includes a plurality of springs 36 whose upper ends are connected to the floating floor F, a damper (not shown) arranged in parallel with the plurality of springs 36, and a plurality of springs 36 and a damper. It has a mass body 37 connected to and suspended from, and a plurality of rotational inertia mass dampers 38 connected between the floating floor F and the mass body 37.

A predetermined number of rotary inertial mass dampers 38 are provided (only two are shown in FIG. 11), and have the same configuration as, for example, the second rotary inertial mass damper 4. Specifically, the rotary inertial mass damper 38 has a cylinder filled with a working fluid, a piston for partitioning the inside of the cylinder into the first and second fluid chambers, and parallel to each other communicating with the first and second fluid chambers. The first and second passages are provided at the connection between the first and second passages, the gear motor and flywheel provided in the first passage (neither shown), and the first and second passages, and the first and second passages are provided. It has a second solenoid valve 41 (see FIG. 12) for switching the communication passage between the fluid chambers to one of the first and second communication passages.

As shown in FIG. 12, the second solenoid valve 41 is connected to the control device 31, and its ON / OFF is controlled by the control device 31. Further, the cylinder of the rotary inertia mass damper 38 is connected to the floating floor F, and the piston rod is connected to the mass body 37.

In the rotary inertial mass damper 38 having the above configuration, when vertical glue vibration is generated in the floating floor F and the mass body 37 is displaced with respect to the floating floor F, the piston moves in the cylinder, and the first or first position is used. 2 Working fluid flows out of the fluid chamber.

In this state, when the second solenoid valve 41 is turned off, only the first communication passage is opened, the working fluid flows in the first communication passage, and the first equivalent mass due to the rotational moment of inertia of the rotating mass is exhibited. Since the second equivalent mass is obtained and added by the flow of the working fluid, the natural frequency of the second tuned mass damper 35 is lowered (the natural period becomes long) by that amount. On the other hand, when the second solenoid valve 41 is turned on, only the second passage is opened, the working fluid does not flow in the first passage, and only the second equivalent mass is obtained, but the mass effect is Since it is extremely small (≈0), the natural frequency of the second tuning mass damper 35 is increased (the natural period is shortened) by that amount. As described above, the larger the ON number Non2 of the second solenoid valve 41, the higher the natural frequency of the second tuning mass damper 35.

FIG. 13 shows a solenoid valve control process executed by the vibration damping device A2 during the generation of longitudinal vibration. This process is executed by the control device 31 of FIG. 12 at predetermined time intervals. In this process, first, in step 11, the vibration frequency fa of the floating floor F is acquired in the same manner as in step 1 of FIG.

Next, in step 12, as in step 2, the solenoid valve 21 of the second rotary inertial mass sensor 4 is searched by searching the table of FIG. 7 according to the vibration frequency fa (= breaking frequency fs). Calculate the number of ONs Non. Further, the ON number Non2 of the second solenoid valve 41 is calculated by searching a predetermined table according to the vibration frequency fa (= breaking frequency fs). Although not shown, in this table, the second solenoid valve 41 so that the natural frequency of the second tuning mass damper 35 is tuned to the primary natural frequency fn1 of the entire floating floor F that changes according to the breaking frequency fs. The ON number Non2 of is set to a larger value as the breaking frequency fs is higher.

Next, in step 13, a drive signal is output to the solenoid valves 21 having a number equal to the calculated ON number Non, and these solenoid valves 21 are turned ON. As a result, the equivalent mass m of the first and second rotational inertial mass dampers 3 and 4 is controlled so that the breaking frequency fs matches the vibrating frequency fa, so that the floating floor F becomes the foundation B. The transmission of the vertical inertial vibration is cut off, and the transmission of the vertical inertial vibration to the periphery is suppressed.

Next, in step 14, a drive signal is output to the second solenoid valve 41 having a number equal to the calculated ON number Non2, and these second solenoid valves 41 are turned ON. As a result, the equivalent mass of the rotational inertia mass damper 38 is controlled so that the natural frequency of the second tuning mass damper 35 is synchronized with the primary natural frequency fn1 of the entire floating floor F, and as a result, the second tuning mass is controlled. Tuning by the damper 35 is performed well.

FIG. 14 shows the vibration frequency fa and the acceleration response magnification Racc of the floating floor F obtained when the cutoff frequency fs is set according to the present embodiment and the natural frequency of the second tuning mass damper 35 is changed. The relationship between (a) fs = 2.0 Hz, (b) fs = 2.75 Hz, and (c) fs = 3.5 Hz is shown together with conventional examples.

In the figure, focusing on the vicinity of the primary natural frequency fn1 (= about 1 Hz) of the entire floating floor F, the second tuning mass damper 35 is applied regardless of the case where the breaking frequency fs is (a) to (c). The natural frequency of is changed to tune to the first natural frequency fn1, and as a result of good tuning by the second tuning mass damper 35, the peak of the acceleration response magnification Racc is minimized smaller than the conventional example. It was confirmed that the vibration damping effect at the primary natural frequency fn1 of the entire floating floor F was improved.

The present invention is not limited to the first and second embodiments described above (hereinafter, collectively referred to as "embodiments"), and can be implemented in various embodiments. For example, in the embodiment, the first and second rotary inertial mass dampers 3 and 4 are of the gear motor type operated by the working fluid, but other hydraulic type such as a vane motor and a piston motor, and the like. A ball screw type may be used. Further, although the gear motor of the embodiment is an external type, it may be an internal type, and the working fluid F is not limited to silicon oil, and of course, a fluid such as hydraulic oil may be used.

Further, as the tuned mass dampers 5 and 35 of the first and second embodiments, a tuned mass damper (TMD) in which a mass body and a spring are connected in series is used, but instead of this, a rotational inertia mass and a viscous body are used. May be used, and a tuned viscous mass damper in which flexible support members are connected in series may be used. Further, in the first and second embodiments, the first rotary inertial mass damper 3 whose mass effect cannot be changed is used in combination, but the first rotary inertial mass damper 3 is eliminated and all of the second rotary inertial mass damper 4 are used. Changed to an improved type (a gear motor is also installed on the 2nd passage 14b side, a fly wheel smaller than the fly wheel on the 1st passage 14a side is provided, and the equivalent mass of the rotary inertial mass damper is changed). Of course, the equivalent mass may be changed step by step.

Further, a plurality of electromagnetic valves 21 of the second rotary inertial mass damper 4 and a plurality of second electromagnetic valves 41 of the rotary inertial mass damper 38 of the second embodiment are provided, and are ON / OFF type, and the continuous passage is first. Alternatively, it is a type that switches to the second continuous passage, and the equivalent mass of the rotary inertia mass damper is changed stepwise depending on the number of ONs thereof. As these solenoid valves, a type that changes the flow rate ratio between the first-passage and the second-passage steplessly may be adopted. In that case, for example, using a single solenoid valve, the equivalent mass of the rotary inertial mass damper can be finely controlled steplessly.

Further, the embodiment is an example in which the vibration damping devices A1 and A2 are installed in the lowest layer immediately above the foundation B of the building, but the present invention is not limited to this, and the vibration damping devices A1 and A2 may be installed in the middle layer of the building. Of course. Further, in the embodiment, the vibration damping device of the present invention has been described as being applied as a countermeasure for suppressing vertical vibration in a live house or the like, but the present invention is not limited to this, but as other appropriate vibration damping measures. For example, it can be applied when a device that generates a large vibration is installed on a structure and the vibration frequency of the device changes.

Further, the configurations, numbers, arrangements, and the like of the various devices shown in the embodiments are merely examples, and can be appropriately changed within the scope of the gist of the present invention.

A1 Vibration damping device of the first embodiment A2 Vibration damping device of the second embodiment 2 Support spring 3 First rotational inertia mass damper (rotary inertia mass damper)
4 Second rotary inertial mass damper (rotary inertial mass damper)
5 Tuning mass damper 12 Cylinder 12a 1st fluid chamber 12b 2nd fluid chamber 13 Piston 14a 1st continuous passage 14b 2nd continuous passage 15 Gear motor 16 Flywheel (rotary mass)
21 Solenoid valve (switching valve)
31 Control device (vibration frequency acquisition means, control means)
35 Second tuning mass damper 41 Second solenoid valve B Foundation (structure)
F Floating floor fa Vibration frequency fs Breaking frequency
fn1 Primary natural frequency of the entire floating floor (natural frequency of the entire floating floor)
md1 1st equivalent mass (rotational inertial mass)
m Equivalent mass of the entire first and second rotational inertia mass dampers (rotational inertial mass of the rotational inertia mass damper)
K Spring force of the entire support spring (spring force of the support spring)
HF working fluid

Claims (3)

It is a vibration damping device for suppressing the vibration transmitted from the structure on which the exciting force acts to the surroundings.
A floating floor arranged on the upper side of the structure and on which the exciting force acts,
A support spring provided between the structure and the floating floor to support the floating floor, and
It has a rotating mass and is provided in parallel with the support spring between the structure and the floating floor, and the relative displacement of the floating floor with respect to the structure when the vibration force is applied is used as the rotational movement of the rotating mass. By converting, a rotational inertia mass is generated, and the rotational inertia mass damper is configured so that the rotational inertia mass can be changed.
The vibration frequency acquisition means for acquiring the vibration frequency of the vibration force as the vibration frequency, and the vibration frequency acquisition means.
The breaking frequency for blocking the transmission of vibration from the floating floor to the structure, which is determined by the rotational inertia mass of the rotary inertia mass damper and the spring constant of the support spring, is the acquired vibration vibration. A control means for changing the rotational inertial mass by the rotational inertial mass damper so as to match the number, and
A tuning mass damper provided between the structure and the floating floor and tuned to the natural frequency of the entire floating floor,
A vibration damping device characterized by being equipped with. The tuning mass damper is configured so that the natural frequency can be changed.
The control means is characterized in that the natural frequency of the tuning mass damper is changed to be tuned to the natural frequency of the entire floating floor in accordance with the rotational inertia mass of the changed rotational inertia mass damper. The vibration damping device according to claim 1. The rotary inertia mass damper is
With the cylinder filled with the working fluid and connected to one of the structure and the floating floor,
A piston that is slidably provided in the cylinder in the axial direction, divides the inside of the cylinder into a first fluid chamber and a second fluid chamber, and is connected to the other of the structure and the floating floor.
Bypassing the piston, communicating with the first and second fluid chambers, and connecting the first and second communication passages in parallel to each other via a connecting portion,
A gear motor provided in the first communication passage and generating a rotational inertial mass by converting the flow of the working fluid in the first communication passage into the rotational motion of the rotating mass.
It is characterized by having a switching valve provided in the connection portion and for switching the communication passage between the first and second fluid chambers to one of the first communication passage and the second communication passage. , The vibration damping device according to claim 1 or 2.

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