Vibration control device

Abstract

To provide a vibration control device capable of suppressing an increase in a manufacturing cost and producing an excellent vibration damping effect according to the predominant frequency of a constituent member due to a change in natural frequency of the constituent member of a building to be a vibration control target and external disturbance.SOLUTION: A vibration control device 100 which damps vibration on a constituent member F of a building comprises a tuned mass damper 10 and a control unit 80. The tuned mass damper 10 has: a crossbeam 60 which intersects with a connection member 40 and fixes a slidable mass block 50; and adjustment means 70 which adjusts an intersection angle between the crossbeam 60 and the connection member 40. The control unit 80: identifies predominant frequency of vibration on the constituent member F based on measurement data acquired through a vibration sensor 75; determines an effective mass of the mass block 50 suitable for vibration control based on the stiffness of a spring 30 and the predominant frequency; and controls the adjustment means 70 by identifying a position of the mass block 50 on the connection member 40 forming the effective mass.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a vibration damping device. [Background technology]

[0002] Vibrations (vertical and horizontal vibrations) occur in the structural components of a building (or structure), such as floors, due to disturbances such as environmental vibrations. More specifically, microtremors occur constantly due to so-called environmental vibrations, such as traffic vibrations from trains and other vehicles, vibrations during the operation of factory equipment, vibrations due to wind loads, and even vibrations caused by walking indoors. To reduce the constant microtremor level shaking (acceleration) of such floors, tuned mass dampers (TMDs), which constitute vibration control devices, are sometimes installed on floors and the beams that support the floors.

[0003] Tuned mass dampers generally have their natural frequency and damping set to match the mass and natural frequency of the building's structural members that they are intended to damp, and the mass of the structural members and the spring stiffness of the springs that support the mass are set to achieve the set natural frequency. After a tuned mass damper is installed on a building's structural members, the natural frequency of the tuned mass damper is usually maintained at its initial set value (a constant value).

[0004] However, the vibration damping effect of the tuned mass damper can be reduced by changes in the natural frequency of the component to be damped due to changes in the stiffness of the component over time or changes in the mass of the component due to factors such as the load. Therefore, it is preferable that the natural frequency of the tuned mass damper be variable in response to changes in the natural frequency of the component, rather than being maintained at a constant value as described above. Furthermore, since the vibration damping effect of the tuned mass damper can be reduced even when the natural frequency of the tuned mass damper is not close to the dominant frequency of the component due to the disturbance, it is preferable that the natural frequency of the tuned mass damper be variable in response to the dominant frequency of the component due to the disturbance.

[0005] For these reasons, a tuned mass damper with a variable natural frequency is desirable. Because the natural frequency of a tuned mass damper is determined by the mass of the mass and the stiffness of the spring, as mentioned above, the natural frequency can be changed by changing the mass of the mass or the stiffness of the spring.

[0006] Here, a vibration damping device is proposed in Patent Document 1. This vibration damping device is provided with a compression coil spring that resiliently moves in the vertical direction and a damping means that damps the force in the vertical direction, with a mass (weight) placed on top of these, and further with a damping means provided between the mass and the floor.

[0007] Also, Patent Document 2 proposes an active floor vibration control device. This active floor vibration control device is equipped with a sensor for detecting vibrations of the floor to be controlled, a controller for controlling the actuator by determining the actuator operation amount that can reduce vibration and structure-borne sound from the detection signal from the sensor and a dynamic characteristic model of the floor to be controlled, and an actuator that is driven and controlled by the controller to generate an excitation force. [Prior art documents] [Patent documents]

[0008] [Patent Document 1] Japanese Patent Application Publication No. 10-252253 [Patent Document 2] Japanese Patent Application Laid-Open No. 2005-276118 Summary of the Invention [Problem to be solved by the invention]

[0009] The vibration damping device described in Patent Document 1 is a tuned mass damper that tunes the mass and coil to the natural frequency of the floor or beam, so in order to achieve a high vibration reduction effect, the mass of the mass needs to be sufficiently large, which inevitably results in the vibration damping device being large and heavy, requiring a large installation space and increasing manufacturing costs.For example, in a typical tuned mass damper, the mass of the mass is designed to be about 1 to 3% of the mass of the object to be damped, which makes it difficult to achieve a sufficient vibration reduction effect.

[0010] On the other hand, the vibration control device described in Patent Document 2 is an active mass damper (AMD) that detects vibrations with a sensor and dynamically moves a mass with an actuator, which necessitates precise control of the actuator to cancel out the acting excitation force, which also poses the problem of rising manufacturing costs.

[0011] The present invention has been made in consideration of the above-mentioned problems, and aims to provide a vibration control device that can suppress increases in manufacturing costs and can achieve excellent vibration reduction effects in accordance with changes in the natural frequency of the constituent members of the building to be vibration-controlled and the predominant frequency of the constituent members due to external disturbances. [Means for solving the problem]

[0012] In order to achieve the above object, one aspect of the vibration damping device according to the present invention is A vibration control device that attenuates vibrations of building components, a tuned mass damper and a control unit; The tuned mass damper comprises: a stand that is directly or indirectly installed on the component; a connecting member, one end of which is attached in a cantilever shape so as to be rotatable or non-rotatable to the frame or an erecting member erected upward from the frame; a spring that supports the other end of the connecting member; a mass mounted on the connecting member so as to be slidable laterally; a cross beam having a stopper that crosses the connecting member and stops the mass that is slidable on the connecting member from sliding downward in an inclined direction; an adjustment means for adjusting the crossing angle of the connecting member relative to the cross beam, A vibration sensor is installed on the platform, The control unit The predominant frequency of vibration of the component is identified based on the measurement data obtained from the vibration sensor, the effective mass of the mass suitable for vibration control is identified based on the stiffness of the spring and the predominant frequency, and the position of the mass in the connecting member that forms the effective mass is identified to control the adjustment means.

[0013] According to this aspect, the structure includes a connecting member that is attached in a cantilever fashion to a frame or the like and on which a mass is mounted so as to be able to slide freely, a cross beam that crosses the connecting member and has a stopper that stops the mass from sliding diagonally downward, and an adjustment means for adjusting the crossing angle of the connecting member with the cross beam, and the control unit identifies the predominant frequency of vibration of the component member based on measurement data obtained from the vibration sensor, identifies the effective mass of the mass suitable for vibration control based on the stiffness of the spring and the predominant frequency, and controls the adjustment means to move the mass to the identified position, thereby suppressing increases in manufacturing costs and achieving excellent vibration reduction effects in accordance with changes in the natural frequency of the component member of the building to be vibration-controlled and the predominant frequency of the component member due to external disturbances.

[0014] In order to maximize the vibration-damping effect of the constituent components of a building that are the target of vibration control, the natural frequency of the vibration-damping device must be matched each time to the natural frequency of the constituent components, which can change for various reasons.Furthermore, in order to maximize the vibration-damping effect of the constituent components when an external disturbance is acting, the natural frequency of the vibration-damping device must be matched to the dominant frequency of the vibration of the constituent components.In this case, either the mass or the spring rigidity of the mass that makes up the vibration-damping device will be adjusted.

[0015] In this embodiment, the stiffness of the spring is set (fixed) in advance, and the effective mass of the mass is adjusted by adjusting (changing) the position of the mass relative to the spring, thereby enabling effective control of the natural frequency of the vibration damping device.

[0016] Here, "effective mass of the mass" refers to the mass of the mass that determines the natural frequency of the tuned mass damper, and the effective mass of the mass changes depending on the position of the mass relative to the spring; for example, the effective mass decreases as the mass moves farther away from the spring. Also, "building components" include the floors and walls that make up the building (partition walls that are interior walls and exterior walls).

[0017] In another aspect of the vibration damping device according to the present invention, The adjusting means is an actuator mounted on the connecting member on the pivot point side and above the connecting member, and movable up and down; one end of the cross beam is rotatably attached to a driving member constituting the actuator, The other end of the cross beam is rotatably attached to a protruding member that protrudes downward from the connecting member on the side of the connecting member that is supported by the spring.

[0018] According to this aspect, the adjustment means includes an actuator that moves up and down above the pivot point side of the connecting member, one end of the cross beam is rotatably attached to the drive member of the actuator, and the other end of the cross beam is rotatably attached to a protruding member that protrudes below the connecting member on the side supported by the spring of the connecting member, so that the position of the mass can be changed flexibly and stably by tilting the connecting member as desired and sliding the mass. Furthermore, compared to, for example, operating the actuator to move the position of the mass on a horizontal connecting member to change the position, the amount of operation of the actuator (the amount of displacement of the drive member) can be made smaller, which leads to a reduction in the specifications and size of the actuator used.

[0019] The actuator can be a hydraulic cylinder, an air cylinder, a unit of a motor and a rack and pinion mechanism, etc. In the case of a hydraulic cylinder or an air cylinder, the driving member is a piston, and for example, one end of a cross beam is rotatably attached to the tip of the piston.

[0020] In another aspect of the vibration damping device according to the present invention, When the component is vibrating, the control unit controls the adjustment means to adjust the position of the mass in the connecting member so that the dominant frequency matches the natural frequency of the vibration control device.

[0021] According to this aspect, when a component is vibrating due to an external disturbance, the position of the mass is changed and the effective mass of the mass is adjusted so that the predominant frequency of the vibration of the component matches the natural frequency of the tuned mass damper, thereby achieving the maximum vibration reduction effect of the tuned mass damper on the vibration of the component.

[0022] Another aspect of the vibration damping device according to the present invention is the component to be damped is a floor, The present invention is characterized in that at least the tuned mass damper is installed directly or indirectly on the floor.

[0023] According to this aspect, floor vibrations caused by environmental vibrations can be effectively reduced. Here, "the tuned mass damper is installed directly or indirectly on the floor" includes both a configuration in which the tuned mass damper is installed on the floor of a building and a configuration in which the tuned mass damper is indirectly installed on the floor by being installed on a beam or the like supporting the floor.

[0024] The tuned mass damper may also be installed on the floor slab of a double floor. By installing the tuned mass damper on the floor slab of a double floor in this way, floor vibrations caused by environmental vibrations can be effectively reduced while effectively utilizing the under-floor space of the double floor, such as a free-access floor, as an installation space for the tuned mass damper. [Effects of the Invention]

[0025] As can be understood from the above explanation, the vibration control device of the present invention can suppress increases in manufacturing costs and can achieve excellent vibration reduction effects in accordance with changes in the natural frequency of the constituent components of the building to be vibration-controlled and the predominant frequency of the constituent components due to external disturbances. [Brief explanation of the drawings]

[0026] [Figure 1] FIG. 1 is an overall configuration diagram of an example of a vibration damping device according to an embodiment, showing a state in which a tuned mass damper constituting an example of the vibration damping device is installed on a beam supporting a floor. [Figure 2] 2 is a view taken in the direction of the arrow II in FIG. 1, and is a plan view of a tuned mass damper that constitutes an example of a vibration damping device according to an embodiment. [Figure 3] FIG. 10 is a diagram illustrating the relationship between the position of the mass from the fulcrum and the natural frequency. [Figure 4] 10A and 10B are diagrams illustrating the relationship between the inclination angle and the intersection position of the connecting member and the cross beam. [Figure 5] 6 is a graph illustrating the vibration reduction effect of one example of a vibration damping device according to an embodiment, together with the vibration reduction effect of another reference example. [Figure 6] 4 is a graph illustrating the vibration damping effect (difference in damping due to natural frequency) of an example of a vibration damping device according to an embodiment. [Figure 7] FIG. 2 is a diagram illustrating an example of a hardware configuration of a control unit that constitutes an example of a vibration damping device according to an embodiment. [Figure 8] FIG. 2 is a diagram illustrating an example of the functional configuration of a control unit that constitutes an example of a vibration damping device according to an embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0027] Hereinafter, vibration damping devices according to embodiments will be described with reference to the accompanying drawings. In this specification and the drawings, substantially identical components will be designated by the same reference numerals, and redundant description may be omitted.

[0028] [Vibration damping device according to the embodiment] An example of a vibration damping device according to an embodiment will be described with reference to Figures 1 to 8. Here, Figure 1 is an overall configuration diagram of an example of a vibration damping device according to an embodiment, showing a state in which a tuned mass damper constituting an example of a vibration damping device is installed on a beam supporting a floor. Also, Figure 2 is a view taken in the direction of arrow II in Figure 1, and is a plan view of the tuned mass damper constituting an example of a vibration damping device according to an embodiment.

[0029] The target of vibration damping by the tuned mass damper 10 constituting the vibration damping device 100 shown in Figure 1 is a floor F (an example of a structural component) that forms a building, and the floor F in the illustrated example is a long concrete floor slab with a span of about 15 m between a pair of girders G. Between the pair of girders G are multiple sub-girders B that also support the floor F. Here, the structural component of the building that is the target of vibration reduction may be an exterior wall, an interior wall such as a partition wall, or the like, in addition to the floor in the illustrated example.

[0030] The main girder G and the secondary beams B are both formed from H-shaped steel (including I-shaped steel) of different dimensions, and a frame 20 constituting the tuned mass damper 10 is installed across the lower flanges B1 of the two secondary beams B, which have a lower beam height than the main girder G. Therefore, the tuned mass damper 10 in the illustrated example is installed indirectly on the floor F via the secondary beams B.

[0031] The vibration damping device 100 includes a tuned mass damper 10 and a control unit 80. Although the damping mechanism is not shown in the illustrated example of the vibration damping device 100, the vibration damping device 100 may be in a form that does not include a damping mechanism as shown, or in a form that includes a damping mechanism.

[0032] The tuned mass damper 10 is installed below the floor F, between two small beams B that support the floor F. This installation configuration makes it possible to effectively utilize the space under the floor as installation space for the tuned mass damper 10. Although not shown in the figures, there are other configurations in which the space under a double floor, such as a free access floor, can be effectively utilized as installation space for the tuned mass damper.

[0033] The tuned mass damper 10 comprises a base 20 mounted on a pair of small beams B supporting a floor F, a spring 30 mounted on the upper surface 21 of the base 20, a connecting member 40 supported by the spring 30, a mass 50 mounted so as to be able to slide freely in the Y2 direction which is horizontal to the connecting member 40, a cross beam 60 which intersects with the connecting member 40 and has a stopper 65 which stops the mass 50 from sliding diagonally downward, and an adjustment means 70 which adjusts the crossing angle of the cross beam 60 relative to the connecting member 40.

[0034] More specifically, a rotating part 22 provided at one end of the upper surface 21 of the frame 20 and a rotating part 43 provided at one end of the lower surface 42 of the connecting member 40 are rotatably connected to each other, and the other end of the upper surface 21 of the frame 20 and the other end of the lower surface 42 of the connecting member 40 are connected by a spring 30, thereby forming a cantilever-type tuned mass damper.

[0035] A hydraulic cylinder 70, which is an actuator, is mounted on the pivot point side of the connecting member 40, and one end 61 of the cross beam 60 is rotatably attached to the tip of a piston 72 (an example of a driving member) which is movable up and down in the Y1 direction, which is the vertical direction. In addition, a protruding member 44 that protrudes downward is provided on the underside 42 of the connecting member 40 on the spring 30 side, and the other end 62 of the cross beam 60 is rotatably attached to the tip of the protruding member 44.

[0036] Rails 45 are laid on the upper surface 41 of the connecting member 40, and running bodies 55 such as wheels attached to the mass 50 slide laterally on the connecting member 40 along the rails 45, and the sliding of the mass 50 downward inclined is stopped by stoppers 65 provided on the cross beams 60, thereby determining the position of the mass 50 relative to the springs 30.

[0037] A vibration sensor 75 is installed on one end side of the upper surface 21 of the stand 20. The vibration sensor 75 measures vibrations in the X1 direction, which is the vertical direction of the floor F, which is the target of vibration control, and the small beams B that support the floor F. More specifically, the vibrations measured by the vibration sensor 75 are vibrations of the floor F caused by environmental vibrations.

[0038] Here, environmental vibrations include traffic vibrations caused by the running of vehicles including railways, vibrations during operation of factory facilities (facility vibrations), and walking vibrations caused by walking indoors.

[0039] Micro-tremors occur constantly in floor F due to environmental vibrations, and in order to reduce the vibrations in the X1 direction at the level of micro-tremors constantly occurring in floor F, tuned mass damper 10 is installed to vibrate mass 50 in the X2 direction, which is the vertical direction, and this vibration at the level of micro-tremors is constantly measured by vibration sensor 75. Here, an accelerometer, speedometer, displacement meter, etc. is used as vibration sensor 75, and the measurement data becomes acceleration data, speed data, displacement data, etc. depending on the type of sensor.

[0040] The control unit 80 is formed by a computer and is installed in a location different from the floor F or the beams G and B, but may, for example, be mounted on an installation stand (not shown) attached to the beams G and B in the same manner as the tuned mass damper 10.

[0041] The measurement data measured by the vibration sensor 75 is transmitted wirelessly to the control unit 80 in the R1 direction. Upon receiving the measurement data, the control unit 80 transmits an operation signal in the R2 direction to the actuator 70, which serves as an adjustment means, and operates the actuator 70 to change the position of one end 61 of the cross beam 60, thereby adjusting the crossing angle θ1 of the connecting member 40 relative to the cross beam 60. Adjusting the crossing angle θ1 adjusts the position of the mass 50 relative to the spring 30, and adjusts the effective mass of the mass 50, which determines the natural frequency of the tuned mass damper 10, to an effective mass suitable for damping the vibrating floor F. Here, the measurement data may be transmitted to the control unit 80 via a wire, and the operation signal may also be transmitted to the actuator 70 via a wire.

[0042] Based on the measurement data obtained from the vibration sensor 75, the control unit 80 identifies the predominant frequency of the vibration of the floor F by frequency analysis such as a fast Fourier transform (FFT), and based on the stiffness of the spring 30 and the identified predominant frequency, identifies the effective mass of the mass 50 suitable for damping the vibration of the vibrating floor F (optimal mass suitable for damping), and controls the actuator 70, which is an adjustment means, to set the effective mass of the mass 50 to the identified effective mass.

[0043] With regard to vibration damping of floor F, it is possible to effectively reduce vibration of floor F when the natural frequency of tuned mass damper 10 matches the natural frequency of floor F or the predominant frequency when floor F vibrates due to environmental vibration (when vibrates due to an exciting force). Therefore, vibration damping device 100 measures the vibration of floor F with vibration sensor 75, identifies the primary natural frequency of floor F or the predominant frequency of vibration of floor F vibrating due to environmental vibration, and moves mass 50 to a position that defines the effective mass of mass 50 so that the natural frequency of tuned mass damper 10 matches or nearly matches these specified values.

[0044] Next, the relationship between the mass position and the natural frequency will be explained with reference to Figures 3 and 4. Here, Figure 3 is a diagram explaining the relationship between the mass position from the fulcrum and the natural frequency, and Figure 4 is a diagram explaining the relationship between the inclination angle of the connecting member and the cross beam and the crossing position.

[0045] A change in the position of the mass 50 causes a change in its effective mass, which in turn causes a change in the natural frequency of the vibration damping device 100. Specifically, the closer the mass 50 is to the pivot point, the higher the natural frequency becomes, and the closer it is to the spring 30, the lower the natural frequency becomes.

[0046] As shown in Figure 3, the vibration damping device to be evaluated had a connecting member mass w0 of 10 kg, a mass wd of 40 kg, a spring constant ks of the spring (elastic body) of 26.6 kg / cm, a distance Ls to the spring (elastic member) of 40 cm, and a distance Lo to the center of gravity of the connecting member of 20 cm.

[0047] As shown in the graph in FIG. 3, it can be seen that as the distance Ld from the pivot point of the mass increases (the distance to the spring decreases), the natural frequency decreases.

[0048] Also, as shown in Figure 4, by changing the inclination of the cross beam in the range of 0.5 to 2 times the inclination of the connecting member, it is possible to change the position of the mass in the range of 0.33 to 0.67 (the mass position is the center position of the connecting member at 0.5).

[0049] For example, based on the dimensions of the vibration control device 100 to be manufactured, if the length of the connecting member 40 is approximately 300 mm and the inclination angle of the connecting member is 3.8°, then by adjusting the height β of the cross beam 60 to approximately 10 mm to 30 mm using the actuator 70, the position of the mass can be changed from the center position of 0.5 on the connecting member to a position between 0.33 and 0.67.

[0050] That is, by changing the inclination angle of the connecting member 40 by changing the inclination angle of the cross beam 60 as in the illustrated example, it is possible to reduce the amount of movement of the actuator 70 compared to, for example, a case in which the actuator is operated to move the position of the mass on a horizontal connecting member to change the position. This makes it possible to use an actuator 70 with as small an amount of movement as possible, thereby reducing the manufacturing cost of the tuned mass damper 10 (vibration control device 100).

[0051] Next, the vibration reduction effect of one example of a vibration damping device according to the embodiment will be described with reference to Figures 5 and 6. The vibration damping device for which the damping reduction effect will be described with reference to Figures 5 and 6 is intended for a configuration that includes, for example, a damping mechanism with a small amount of damping, and since the amount of damping is small, a mechanism for varying the natural frequency of the vibration damping device is required (in the illustrated example, a mechanism for varying the natural frequency by adjusting the effective mass of the mass).

[0052] Here, Fig. 5 is a graph illustrating the vibration reduction effect of an example of the vibration damping device according to the embodiment together with the vibration reduction effect of other reference examples, and is a graph showing an example of the acceleration transmission characteristics of a floor. Also, Fig. 6 is a graph illustrating the vibration reduction effect (difference in attenuation due to natural frequency) of an example of the vibration damping device according to the embodiment.

[0053] In the graph shown in Figure 5, the horizontal axis indicates the ratio of the dominant frequency of the disturbance to the natural frequency of the floor, and the vertical axis indicates the ratio of the floor acceleration to the disturbance excitation force. As shown in Figure 5, when there is no vibration control device (curve <1> ) shows that the acceleration transmission characteristics of the floor are at their maximum when the horizontal axis is "1" (when the natural vibration frequency of the floor and the dominant frequency of the disturbance are equal (this frequency is called the resonance frequency)). <4> ) is a configuration in which the damping characteristic is adjusted to be a relatively flat characteristic against fluctuations in the dominant frequency of the disturbance by optimizing the damping amount of the damping mechanism, and the same vibration reduction effect is obtained at the position B1 of the resonance frequency and at the position B2 shifted from the resonance frequency. On the other hand, when the damping amount of the damping mechanism is larger than the optimal value (curve <5> ) cannot achieve sufficient vibration reduction effect, and the damping amount is smaller than the optimum value (curve <3> ) vibration becomes small at the resonance frequency, and two peaks appear at frequencies before and after the resonance frequency, destroying the flat characteristics.

[0054] On the other hand, when the damping amount of the damping mechanism is set to zero (curve <2> ) creates a valley at the resonance frequency, minimizing vibration, but the peaks that appear at frequencies around the resonance frequency become larger.

[0055] In this way, when the natural frequency of the tuned mass damper is constant and the dominant frequency of the disturbance matches the natural frequency of the floor, a significant vibration reduction effect can be achieved. However, if the dominant frequency of the disturbance and the natural frequency of the floor change and no longer match, there may be cases where a sufficient vibration reduction effect cannot be achieved.

[0056] To address these inherent problems in conventional vibration control devices, as shown in Figure 6, it is possible to constantly obtain the maximum vibration reduction effect in response to disturbances by changing the natural frequency of the tuned mass damper by adjusting the effective mass of the mass of the tuned mass damper as needed. That is, Figure 6 shows the results when the natural frequency of the vibration control device and the natural frequency of the floor are in resonance (curve <30> ), when the natural frequency of the vibration control device is 5% lower than the floor natural frequency, the position of the valley where the vibration reduction effect is maximum shifts to the left (the side where the dominant frequency of the disturbance is lower), and when the natural frequency of the vibration control device is 5% higher than the floor natural frequency, the position of the valley where the vibration reduction effect is maximum shifts to the right (the side where the dominant frequency of the disturbance is higher). In the characteristics shown in the graph in Figure 3, by changing the natural frequency of the tuned mass damper, the curve <2> This allows the position of the valley to be changed, making it possible to achieve a significant vibration reduction effect.

[0057] The vibration control device 100 shown in the figure takes advantage of these characteristics and, for example, in a configuration that does not include a damping mechanism or a configuration that includes a damping mechanism with a small amount of damping, has the function of identifying the dominant frequency of vibration of the floor F, which is the object to be damped, and adjusting the effective mass of the mass 50 by moving the position of the mass 50 in order to change the natural frequency of the tuned mass damper 10 according to the identified dominant frequency.

[0058] The natural frequency of tuned mass damper 10 can be changed relatively easily by changing the effective mass of mass 50 by moving the position of mass 50 as shown in Figure 1. The effective mass of mass 50 can be continuously changed by actuator 70, and therefore the natural frequency of tuned mass damper 10 can also be continuously changed.

[0059] In the vibration damping device 100, when the natural frequency of the tuned mass damper 10 matches the dominant frequency of the disturbance acting on the floor F to be damped (when the effective mass of the mass 50 is adjusted so that the natural frequency matches), the maximum vibration reduction effect of the floor F is achieved (the curve in FIG. 5 <2> (See A1 of the above).

[0060] By utilizing this technology for matching the natural frequency of the tuned mass damper 10 with the dominant frequency of the disturbance, the mass (actual mass) of the mass can be made significantly smaller than that of conventional tuned mass dampers. That is, while the mass of the mass in conventional tuned mass dampers is generally 1 to 3% of the mass of the object to be damped, the mass of the mass 50 of the tuned mass damper 10 constituting the vibration damping device 100 of the illustrated example can be reduced to approximately 0.1 to 0.3% of the mass of the object to be damped.

[0061] Disturbances acting on the floor F, such as foot traffic and equipment, have different dominant frequencies. However, if the natural frequency of the tuned mass damper is fixed, the dominant frequency of the disturbance and the natural frequency of the tuned mass damper 10 may differ, and the vibration of the floor F may not be reduced (see the curve in Figure 5). <2> A2 state).

[0062] Therefore, the actuator 70, which is an adjustment means, is controlled to move the mass 50 to a position that determines the effective mass of the mass 50 so that the natural frequency of the tuned mass damper 10 that constitutes the vibration control device 100 matches the dominant frequency of the disturbance.

[0063] Furthermore, when no disturbance is acting, the vibration of the object to be damped tends to increase at its natural frequency (first natural frequency). Therefore, the natural frequency of the tuned mass damper 10 constituting the vibration damping device 100 is initially set to the first natural frequency of the object to be damped.

[0064] Furthermore, when the vibration of floor F caused by environmental vibration subsides, actuator 70 is controlled to move mass 50 to a position that determines the effective mass of mass 50 so that the natural frequency of tuned mass damper 10 matches or nearly matches the natural frequency (first-order natural frequency) of floor F.

[0065] The tuned mass damper 10 that constitutes the vibration control device 100 does not constantly vibrate the mass in accordance with the vibration of the object to be damped as in the active control system, but rather changes the position of the mass 50 to change its effective mass and thereby change the characteristics of the vibration system. Therefore, there is no need for a large-scale, complex drive mechanism to constantly vibrate the mass.

[0066] As a result, the tuned mass damper 10 constituting the vibration control device 100 can suppress increases in manufacturing costs. Furthermore, it can provide an excellent vibration reduction effect in accordance with the dominant frequency of the constituent members due to disturbances. Even if the natural frequency of the floor F of the building to be damped changes from its initial value, the natural frequency of the tuned mass damper 10 can be adjusted in accordance with the changed natural frequency of the floor F, thereby providing an excellent vibration reduction effect.

[0067] Next, an example of the hardware configuration and functional configuration of the control unit 80 that forms the vibration damping device 100 will be described with reference to Fig. 7 and Fig. 8. Here, Fig. 7 is a diagram showing an example of the hardware configuration of the control unit that forms the vibration damping device according to the embodiment, and Fig. 8 is a diagram showing an example of the functional configuration of the control unit that forms the vibration damping device according to the embodiment.

[0068] The control unit 80 is configured by an information processing device (computer) such as a relatively small controller, and has a size that allows it to be placed on a stand spanning two small beams B, for example, as described above.

[0069] The controller constituting the control unit 80 includes a CPU (Central Processing Unit) 81, a main memory device 82, an auxiliary memory device 83, a communication IF (interface) 84, and an input / output IF 85, which are interconnected by a connection bus 86. The main memory device 82 and the auxiliary memory device 83 are computer-readable recording media.

[0070] The CPU 81 is a central processing unit that performs overall control of the control unit 80, which is made up of a computer.

[0071] The main storage device 82 stores computer programs executed by the CPU 81, data processed by the CPU 81, etc. The main storage device 82 includes, for example, a flash memory, a RAM (Random Access Memory), and a ROM (Read Only Memory).

[0072] The auxiliary storage device 83 is used, for example, as a storage area that assists the main storage device 82, and stores computer programs executed by the CPU 81, data processed by the CPU 81, and the like.

[0073] The input / output IF 85 is an interface for inputting and outputting data to and from devices connected to the control unit 80 .

[0074] The communication IF 84 is an interface with a network to which the control unit 80 is connected. The communication IF 84 receives measurement data from the vibration sensor 75 and transmits command signals to the actuator 70 via various networks including public networks such as the Internet.

[0075] As shown in FIG. 8, the control unit 80 provides various functions of at least an acquisition unit 102, a calculation unit 104, an operation unit 106, a display unit 108, and a storage unit 110 by the execution of a program by a CPU 81.

[0076] The acquisition unit 102 acquires measurement data transmitted from the vibration sensor 75, which measures micro-movements of the floor F caused by disturbances at any time, and stores the data in the storage unit 110 each time.

[0077] The storage unit 110 further stores the mass of the mass 50 that constitutes the tuned mass damper 10, the stiffness of the spring 30, and the natural frequency (first natural frequency) of the floor F that is the target of vibration damping, which is specified in advance.

[0078] The calculation unit 104 identifies the dominant frequency of vibration of the floor F when a disturbance acts, by frequency analysis, based on the measurement data transmitted as needed.

[0079] Furthermore, the calculation unit 104 identifies the effective mass of the mass 50 suitable for damping the vibration of the floor F based on the stiffness of the spring 30 stored in the memory unit 110 and the identified predominant frequency of the vibration of the floor F, and identifies the position of the mass 50 (position from the spring 30) that determines this effective mass.

[0080] As a preliminary design step, the position of mass 50, which determines the effective mass of mass 50, is set based on the mass of mass 50, the stiffness of spring 30, and the natural frequency of floor F, and then vibration control device 100 is manufactured. After that, a pre-operation experiment is conducted using the manufactured vibration control device 100, and the relationship between the natural frequency of tuned mass damper 10 and the control amount is confirmed, after which the control amount for operation is set.

[0081] As shown in Figure 4, the memory unit 110 further stores relationship data between the height β of one end of the cross beam (the amount of rise of the piston 72 of the hydraulic cylinder 70) and the corresponding intersection position (mass position) between the connecting member and the cross beam.

[0082] Based on the above-mentioned relationship data in the memory unit 110, the calculation unit 104 identifies the amount of lift of the piston 72 corresponding to the position of the mass that defines the effective mass of the identified mass, and the operation unit 106 transmits a command signal regarding the identified amount of lift to the hydraulic cylinder 70, thereby driving and controlling the hydraulic cylinder 70.

[0083] When the vibration of floor F caused by environmental vibration subsides, a command signal is sent from the operating unit 106 to the hydraulic cylinder 70, and the hydraulic cylinder 70 is driven and controlled to move the mass to a position that determines the effective mass of the mass that matches the natural frequency of the tuned mass damper 10 to the first-order natural frequency of floor F.

[0084] The display unit 108 displays the measurement data from the vibration sensor 75, which changes due to environmental vibrations (external disturbances), and further displays the dominant frequency of vibration of the floor F identified based on the measurement data, and displays the effective mass of the mass suitable for damping the vibration of the floor F and the position of the mass that determines this effective mass.

[0085] It should be noted that the configurations of the above-described embodiments may be combined with other components, and the present invention is not limited to the configurations shown here. In this regard, the present invention may be modified within the scope of the gist of the present invention, and may be appropriately determined depending on the application form. [Explanation of symbols]

[0086] 10: Tuned mass damper 20: Stand 21:Top surface 22: Rotating part 30: Spring 40: Connecting member 41:Top surface 42: Bottom surface 43: Rotating part 44: Protruding member 45: Rail 50: Square 55: Running body (wheel) 60: Cross beam 61: One end 62: Other end 65: Stopper 70: Actuator (hydraulic cylinder) 72: Piston (driving member) 75: Vibration sensor 80: Control unit 100: Vibration control device F: Floor (component) B: Beam (small beam) B1: Lower flange G: Liang (girder)

Claims

1. A vibration control device that attenuates vibrations of building components, a tuned mass damper and a control unit; The tuned mass damper comprises: a stand that is directly or indirectly installed on the component; a connecting member, one end of which is attached in a cantilever shape so as to be rotatable or non-rotatable to the frame or an erecting member erected upward from the frame; a spring that supports the other end of the connecting member; a mass mounted on the connecting member so as to be slidable laterally; a cross beam having a stopper that crosses the connecting member and stops the mass that is slidable on the connecting member from sliding downward in an inclined direction; an adjustment means for adjusting the crossing angle of the connecting member relative to the cross beam, A vibration sensor is installed on the platform, The control unit A vibration damping device characterized in that the dominant frequency of vibration of the component is identified based on measurement data obtained from the vibration sensor, the effective mass of the mass suitable for vibration damping is identified based on the stiffness of the spring and the dominant frequency, and the position of the mass in the connecting member that forms the effective mass is identified to control the adjustment means.

2. The adjusting means is an actuator mounted on the connecting member on the pivot point side and above the connecting member, and movable up and down; one end of the cross beam is rotatably attached to a driving member constituting the actuator, 2. The vibration damping device according to claim 1, wherein the other end of the cross beam is rotatably attached to a protruding member that protrudes downward from the connecting member on the side supported by the spring of the connecting member.

3. 3. A vibration damping device as described in claim 1 or 2, characterized in that, when the component is vibrating, the control unit controls the adjustment means to adjust the position of the mass in the connecting member so that the dominant frequency matches the natural frequency of the vibration damping device.

4. the component to be damped is a floor, 4. The vibration damping device according to claim 3, wherein at least the tuned mass damper is installed directly or indirectly on the floor.

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