Damping device

Abstract

To provide a damping device that can suppress rise of cost of manufacture and exert excellent vibration reduction effect in accordance with dominant frequencies of components of a building that is a damping object due to change and disturbance in natural frequencies of the components.SOLUTION: A damping device 100 for damping vibrations of components F of a building includes a synchronization mass damper 10 and a control unit 80. The synchronization mass damper 10 includes an adjustment means 70 for adjusting an effective length of a spring 30. The control unit 80 specifies dominant frequencies of the vibrations of the components F on the basis of measurement data acquired from a vibration sensor 60 and controls the adjustment means 70 by specifying an effective length of the spring 30 which is suitable for vibration damping on the basis of a mass and a dominant frequency of a mass 50.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, Patent Document 1 proposes an installation system for residential vibration control devices in which a divided mass dynamic damper, each with elastically supported divided masses, is installed as a secondary vibration system for a house, which is a primary vibration system. In this installation system, divided mass dynamic dampers with 2 to 8 divided masses and set so that the natural frequency increases or decreases in increments of 0.1 to 0.8 Hz are standardized for each of a plurality of house frequency ranges, which are preset within a range of 2 to 8 Hz for the house's natural frequency, and when installing the divided mass dynamic dampers in an individual house, a standardized divided mass dynamic damper within a house frequency range that includes the house's natural frequency is selected and installed in the house.

[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 Laid-Open No. 2003-120069 [Patent Document 2] Japanese Patent Application Laid-Open No. 2005-276118 Summary of the Invention [Problem to be solved by the invention]

[0009] The installation system for residential vibration control devices described in Patent Document 1 requires multiple divided masses with different corresponding frequency ranges in order to accommodate a wide range of residential natural frequencies, which poses the problem that the number of masses inevitably has to increase in order to accommodate the various natural frequencies.

[0010] On the other hand, the active floor 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, resulting in problems such as 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 spring installed on the frame; a mass supported by the spring; and an adjustment means for adjusting the effective length of the spring. 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, and the effective length of the spring suitable for vibration control is identified based on the mass of the mass and the predominant frequency, thereby controlling the adjustment means.

[0013] According to this aspect, an adjustment means for adjusting the effective length of the spring is provided, and the control unit identifies the predominant frequency of vibration of the component based on the measurement data obtained from the vibration sensor, identifies the effective length of the spring suitable for vibration control based on the mass of the mass and the predominant frequency, and controls the adjustment means to adjust the length of the spring to that effective length.By doing so, it is possible to achieve an excellent vibration reduction effect in accordance with changes in the natural frequency of the component of the building to be vibration-controlled and the predominant frequency of the component due to external disturbances, while suppressing increases in manufacturing costs.

[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 mass of the mass is set (fixed) in advance, and the effective length of the spring is adjusted to change the spring stiffness, thereby enabling effective control of the natural frequency of the vibration damping device.

[0016] Here, "effective spring length" refers to the length of the spring that ensures the stiffness of the spring that determines the natural frequency of the tuned mass damper. For example, if there are multiple springs, the effective length of each spring is determined based on the overall stiffness of the springs. Furthermore, "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 mass is attached to a connecting member, the connecting member being supported by the spring; The adjusting means is a shaft member that can penetrate a through hole provided in either the connecting member or the base and enter the inside of the spring; an actuator that raises and lowers the shaft member, The control unit is characterized in that it operates the actuator to adjust the length of the shaft member that penetrates into the spring, thereby adjusting the area where the spring protrudes from the shaft member as the effective length of the spring.

[0018] According to this aspect, the adjustment means comprises an axial member such as a bolt that can freely penetrate into the interior of the spring by passing through a through hole provided in the connecting member or the frame, and an actuator that raises and lowers the axial member.By using the actuator to change the length of penetration of the axial member into the interior of the spring to adjust the effective length of the spring, the effective length of the spring can be adjusted flexibly and precisely using an adjustment means with a relatively simple configuration.

[0019] In another aspect of the vibration damping device according to the present invention, the mass is attached to a connecting member, the connecting member being supported by the spring; The adjusting means is a bolt attached to either the connecting member or the frame; a long nut having a hollow, accommodating at least a portion of the bolt in the hollow, and threadably engaging with the bolt; an actuator that directly or indirectly rotates the long nut to raise and lower the long nut relative to the bolt, The inner wall of the long nut is provided with a thread groove for guiding the spring as it enters and leaves the hollow. The control unit operates the actuator to raise and lower the long nut relative to the bolt, and adjusts the length of the spring that penetrates into the hollow in accordance with the raising and lowering of the long nut, thereby adjusting the area where the spring protrudes from the long nut as the effective length of the spring.

[0020] According to this aspect, the adjustment means includes a bolt attached to the connecting member or the frame, a long nut that threadably engages with the bolt while accommodating a portion of the bolt in the hollow and that has a threaded inner wall that guides the spring as it moves in and out of the hollow, and an actuator that rotates the long nut. By operating the actuator to raise and lower the long nut relative to the bolt and change the length of insertion of the spring into the hollow, the effective length of the spring can be adjusted, thereby enabling flexible and precise adjustment of the effective length of the spring with a relatively simple adjustment means. Here, there are two types of adjustment: one in which the long nut is directly rotated by the actuator, and one in which the long nut is housed inside a gear and rotates when the gear is rotated by the actuator, so that the long nut also rotates when the gear is rotated by the actuator, thereby allowing the long nut to be indirectly rotated by the actuator.

[0021] Another aspect of the vibration damping device according to the present invention is When the component is vibrating, the control unit controls the adjusting means to adjust the effective length of the spring so that the dominant frequency of the vibration of the component matches the natural frequency of the tuned mass damper.

[0022] According to this aspect, when a component is vibrating due to an external disturbance, the effective length of the spring is adjusted so that the dominant 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 against the vibration of the component.

[0023] Another aspect of the vibration damping device according to the present invention is One end of the connecting member is rotatably or non-rotatably attached to the stand or to an upright member standing upright on the stand, and the other end of the connecting member is supported by the spring, The tuned mass damper is characterized in that it is of a cantilever type configuration, with the mass attached to the connecting member.

[0024] According to this aspect, a cantilever-type vibration control device can be formed that 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 dominant frequency of the constituent components due to external disturbances.

[0025] Another aspect of the vibration damping device according to the present invention is A plurality of the springs are attached to the base, The tuned mass damper is characterized in that it is of a flat type in which the mass is supported by a plurality of the springs via the connecting members.

[0026] According to this aspect, a flat vibration damping device can be formed that can achieve excellent vibration reduction effects in accordance with changes in the natural frequency of the constituent members of the building to be damped and the dominant frequency of the constituent members due to external disturbances.

[0027] Another aspect of the vibration damping device according to the present invention is a pair of connecting members are attached to a pair of standing members standing upright from the frame, respectively, via the springs, and the mass is attached in a sandwiched state between the pair of connecting members; The present invention is characterized in that a rail is installed on the frame, and the mass is attached along the rail so as to be able to vibrate freely in the lateral direction, which is a flat type variant.

[0028] According to this aspect, it is possible to form another type of flat vibration control device that 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.

[0029] 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.

[0030] 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.

[0031] 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]

[0032] 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]

[0033] [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] 3 is a view taken in the direction of the arrow III in FIG. 1, and is a front view of a tuned mass damper that constitutes an example of a vibration damping device according to an embodiment. FIG. [Figure 4] 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 5] 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 6A] FIG. 2 is an exploded view of an example of an adjustment means. [Figure 6B] FIG. 10 is an assembly diagram of an example of an adjustment means, showing the operation state. [Figure 6C] 10A and 10B are diagrams illustrating an example of an operating state of an adjustment unit. [Figure 7A] FIG. 10 is an assembly diagram of another example of the adjusting means, showing the operating state. [Figure 7B] 10A and 10B are diagrams illustrating the operating state of another example of the adjusting means. [Figure 8A] FIG. 10 is an exploded view of yet another example of the adjusting means. [Figure 8B] FIG. 10 is yet another assembly view of the adjusting means, showing the operating state. [Figure 8C] 10A and 10B are diagrams illustrating an operating state of yet another example of the adjusting means. [Figure 9] 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 10] 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. [Figure 11] FIG. 10 is a side view of another example of a tuned mass damper that constitutes a vibration damping device according to an embodiment. [Figure 12] 12 is a view taken in the direction of the arrow XII in FIG. 11 and is a front view of another example of a tuned mass damper that constitutes a vibration damping device according to an embodiment. [Figure 13] FIG. 10 is a side view of yet another example of a tuned mass damper that constitutes a vibration damping device according to an embodiment. [Figure 14] 14 is a view taken in the direction of the arrow XIV in FIG. 13, and is a plan view of still another example of a tuned mass damper that constitutes a vibration damping device according to an embodiment. FIG. DETAILED DESCRIPTION OF THE INVENTION

[0034] 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.

[0035] [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 14. 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, and Figure 3 is a view taken in the direction of arrow III in Figure 1 and is a front view of the tuned mass damper constituting an example of a vibration damping device according to an embodiment.

[0036] 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.

[0037] 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.

[0038] 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.

[0039] 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.

[0040] 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 placed on the connecting member 40, and an adjustment means 70 for adjusting the effective length t of the spring 30.

[0041] 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 plurality of springs 30 (two in the illustrated example). This is a cantilever-type tuned mass damper.

[0042] A vibration sensor 60 is installed on one end side of the upper surface 21 of the stand 20. The vibration sensor 60 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 60 are vibrations of the floor F caused by environmental vibrations.

[0043] 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.

[0044] Microtremors constantly occur in floor F due to environmental vibrations, and in order to reduce vibrations (acceleration) in the X1 direction at the level of such microtremors constantly occurring in floor F, tuned mass damper 10 is installed so as to vibrate mass 50 in the X2 direction, which is the vertical direction, and this vibration at the level of microtremors is constantly measured by vibration sensor 60. Here, an accelerometer, speedometer, displacement meter, etc. is used as vibration sensor 60, and the measurement data becomes acceleration data, speed data, displacement data, etc. depending on the type of sensor.

[0045] 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.

[0046] The measurement data measured by the vibration sensor 60 is transmitted wirelessly to the control unit 80 in the R1 direction, and the control unit 80, having acquired the measurement data, transmits an operation signal to the adjustment means 70 in the R2 direction to operate the actuator 74 that constitutes the adjustment means 70, thereby adjusting the length of the spring 30 to an effective length t suitable for damping the vibration of the vibrating floor F. Here, the measurement data may be transmitted to the control unit 80 by wire, and the operation signal may also be transmitted to the adjustment means 70 by wire.

[0047] Based on the measurement data obtained from the vibration sensor 60, 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 mass of the mass 50 and the identified predominant frequency, identifies the effective length t of the spring 30 suitable for damping the vibration of the vibrating floor F (optimal length suitable for vibration damping), and controls the actuator 74 of the adjustment means 70 to adjust the length of the spring 30 to the identified effective length t.

[0048] With regard to vibration damping of the floor F, it is possible to effectively reduce the vibration of the floor F when the natural frequency of the tuned mass damper 10 matches the natural frequency of the floor F or the predominant frequency when the floor F vibrates due to environmental vibration (when vibrates due to an exciting force). To this end, the vibration damping device 100 measures the vibration of the floor F using the vibration sensor 60, identifies the primary natural frequency of the floor F or the predominant frequency of the vibration of the floor F vibrating due to environmental vibration, and adjusts the effective length t of the spring 30 so that the natural frequency of the tuned mass damper 10 matches or nearly matches these identified values. The specific configuration of the adjustment means 70 that adjusts the effective length t of the spring 30 will be described in detail below.

[0049] Next, the vibration reduction effect of one example of a vibration damping device according to the embodiment will be described with reference to Figures 4 and 5. The vibration damping device for which the damping reduction effect will be described with reference to Figures 4 and 5 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 that makes the natural frequency of the vibration damping device variable (in the illustrated example, a mechanism that makes the natural frequency variable by adjusting the effective length of the spring) is required.

[0050] Here, Fig. 4 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. 5 is a graph illustrating the vibration reduction effect (difference in damping due to natural frequency) of an example of the vibration damping device according to the embodiment.

[0051] In the graph shown in Figure 4, 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 4, 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.

[0052] 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.

[0053] 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.

[0054] To address these inherent problems in conventional vibration control devices, as shown in Figure 5, 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 length of the spring in the tuned mass damper as needed. That is, Figure 5 shows the case where 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 4, 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.

[0055] The vibration control device 100 shown in the figure takes advantage of these characteristics and has the function of identifying the dominant frequency of vibration of the floor F, which is the target of vibration control, in a configuration that does not include a damping mechanism or that includes a damping mechanism with a small amount of damping, and adjusting the effective length t of the spring 30 in order to change the natural frequency of the tuned mass damper 10 according to the identified dominant frequency.

[0056] The natural frequency of tuned mass damper 10 can be changed relatively easily by changing the effective length t of spring 30, as shown in Figure 1. Since the effective length t of spring 30 can be continuously changed as described in detail below, the natural frequency of tuned mass damper 10 can also be continuously changed accordingly.

[0057] 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 length of the spring 30 is adjusted so that the natural frequency matches), the maximum vibration reduction effect on the floor F is achieved (the curve in FIG. 4 <2> (See A1 of the above).

[0058] By utilizing a technique for matching the natural frequency of the tuned mass damper 10 with the dominant frequency of the disturbance, the 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.

[0059] 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 4). <2> A2 state).

[0060] Therefore, the effective length of the spring 30 is adjusted by the adjusting means 70 so that the natural frequency of the tuned mass damper 10 constituting the vibration control device 100 matches the predominant frequency of the disturbance, thereby controlling it to match the predominant frequency of the disturbance.

[0061] 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.

[0062] Furthermore, when the vibration of the floor F caused by the environmental vibration has subsided, the adjustment means 70 is controlled so that the effective length of the spring is such that the natural frequency of the tuned mass damper 10 matches or nearly matches the natural frequency (primary natural frequency) of the floor F.

[0063] 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 changes the effective length of the spring 30 that supports the mass 50 to change the characteristics of the vibration system. Therefore, there is no need for a large-scale, complex drive mechanism or the like to constantly vibrate the mass.

[0064] 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.

[0065] Next, with reference to Figures 6 to 8, several examples of adjustment means that constitute the tuned mass damper 10 will be described. Here, in each figure, motor 74 (see Figures 1 to 3, an example of an actuator) that rotates gear 72 while meshing with the outer periphery of gear 72 is not shown, but motor 74 is also a component of adjustment means 70, 70A, 70B.

[0066] First, as shown in the exploded view of Figure 6A, the adjustment means 70 shown in Figures 6A to 6C has a bolt 76 and a shaft 76a with a threaded groove on its outer periphery that is screwed into a tapped hole 45 (a hole with a threaded groove 45a on the wall surface of a through hole) provided in the connecting member 40, and the lower part of the shaft 76a is fitted inside the spring 30.

[0067] 6B, head 76b (hexagonal nut) of bolt 76 is inserted into hollow 72a of gear 72, which is rotatably mounted on upper surface 41 of connecting member 40, so as to be vertically movable but not rotatable relative to it, and thread groove 72b on the outer periphery of gear 72 meshes with a thread groove on the outer periphery of rotating shaft 75 of motor 74 (an example of an actuator) shown in FIG. 1, thereby forming adjustment means 70. For example, by making the inner diameter of hollow 72a of gear 72 a hexagonal, complementary to head 76b, it is possible to prevent relative rotation between them.

[0068] As shown in Figure 6B, by driving the motor 74 (see Figures 1 to 3) to rotate the gear 72 slightly in the Y1 direction, and then stopping the driving of the motor 74, the bolt 76 descends downward in the Y2 direction, and the tip of the bolt 76 penetrates inside the upper part of the spring 30, and the spring 30 enters the thread groove 76c of the shaft 76a (adjusting the penetration length of the bolt 76 into the interior of the spring 30), and the effective length by which the spring 30 extends from the tip of the bolt 76 is adjusted to a maximum length t1.

[0069] Next, as shown in FIG. 6C, by driving the motor 74 again, the gear 72 rotates in the Y1 direction, and the bolt 76 descends further downward in the Y2 direction and enters the inside of the spring 30, thereby adjusting the effective length of the spring 30 extending from the tip of the bolt 76 to a relatively short length t2.

[0070] By maximizing the penetration length of the bolt 76 into the interior of the spring 30, the effective length of the spring 30 can be adjusted to a minimum length.

[0071] Although not shown, a guide tube may be provided around tapped hole 45 on underside 42 of connecting member 40, and the upper part of spring 30 may be inserted into the guide tube, thereby stably maintaining the posture of the upper part of spring 30. According to this configuration, when the lower part of bolt 76 enters the interior of spring 30, the pushing force from bolt 76 changes the posture of spring 30, which effectively prevents the entry of bolt 76 into the interior of spring 30 from being obstructed.

[0072] On the other hand, the adjustment means 70A shown in Figures 7A and 7B has a protrusion 25 with an accommodation groove 26 on the upper surface 21 of the base 20, and the shaft 76a of the bolt 76 passes through from the inside of the accommodation groove 26 through a through hole 27 provided in the protrusion 25.

[0073] A guide tube 28 is provided around the through hole 27 on the upper surface of the projection 25, and the lower part of the bolt 76 fits inside the guide tube 28. A gear 72 is housed inside the housing groove 26, and a head 76b (hexagonal nut) of the bolt 76 is inserted into a hollow 72a of the gear 72 so as to be vertically movable but not rotatable relative to the gear 72.

[0074] As shown in Figure 7A, by driving motor 74 (see Figures 1 to 3) to rotate gear 72 slightly in the Y3 direction, and then stopping the driving of motor 74, bolt 76 rises upward in the Y4 direction, the tip of bolt 76 penetrates inside the lower part of spring 30, and spring 30 enters thread groove 76c of shaft 76a (adjusting the penetration length of bolt 76 into spring 30), and the effective length of spring 30 extending from the tip of bolt 76 is adjusted to maximum length t3.

[0075] Next, as shown in FIG. 7B, by driving the motor 74 again, the gear 72 rotates in the Y3 direction, and the bolt 76 rises further upward in the Y4 direction and enters the inside of the spring 30, thereby adjusting the effective length of the spring 30 extending from the tip of the bolt 76 to a relatively short length t4.

[0076] By maximizing the penetration length of the bolt 76 into the interior of the spring 30, the effective length of the spring 30 can be adjusted to a minimum length.

[0077] On the other hand, in the adjustment means 70B shown in Figures 8A to 8C, as shown in the exploded view of Figure 8A, one end of a bolt 77 (another example of an axial member) is welded to the underside 42 of the connecting member 40, and the bolt 77 is threaded into a screw hole 78c in a top plate 78b provided at one end of a main body 78a having a hollow 78d, and extends into the hollow 78d.

[0078] A thread groove 78e is provided on the inner wall of the main body 78a of the long nut 78, and the upper part of the spring 30 housed in the hollow 78d fits into the thread groove 78e so that the length of insertion of the spring 30 into the hollow 78d can be adjusted.

[0079] 8B, adjustment means 70B is formed by inserting long nut 78 into hollow 72a of gear 72 so that it can move up and down but cannot rotate relative to the long nut 78. For example, by making the outer shape of long nut 78 hexagonal and the inner diameter of hollow 72a of gear 72 a complementary hexagonal shape, it is possible to prevent relative rotation between the two.

[0080] As shown in Figure 8B, by driving the motor 74 (see Figures 1 to 3) to rotate the gear 72 slightly in the Y5 direction, and then stopping the driving of the motor 74, the long nut 78 threaded onto the bolt 77 descends downward in the Y6 direction, and the upper part of the spring 30 enters the hollow 78d of the long nut 78 (adjusting the length of the bolt 76 entering the interior of the spring 30), and the effective length of the spring 30 extending from the tip of the long nut 78 is adjusted to a maximum length t5.

[0081] Next, as shown in FIG. 8C, by driving the motor 74 again, the gear 72 rotates in the Y5 direction, the long nut 78 descends further downward in the Y6 direction, and the spring 30 enters the hollow 78d of the long nut 78, thereby adjusting the effective length of the spring 30 extending from the tip of the long nut 78 to a relatively short length t6.

[0082] As shown in Figures 6 to 8, the adjustment means 70, 70A, 70B may be provided on either the connecting member 40 side or the base 20 side, and depending on which side they are provided on, the fixed part (the protruding base end of the spring 30) that changes the effective length of the spring 30 changes between the upper and lower sides.

[0083] Although the actuator 74 constituting the adjustment means 70 in the illustrated example is a motor, the actuator may be a hydraulic cylinder, an air cylinder, or the like, other than a motor.

[0084] 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. 9 and Fig. 10. Here, Fig. 9 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. 10 is a diagram showing an example of the functional configuration of the control unit that forms the vibration damping device according to the embodiment.

[0085] 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.

[0086] 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.

[0087] The CPU 81 is a central processing unit that performs overall control of the control unit 80, which is made up of a computer.

[0088] 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).

[0089] 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.

[0090] The input / output IF 85 is an interface for inputting and outputting data to and from devices connected to the control unit 80 .

[0091] 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 60 and transmits a command signal to the actuator 74 via various networks including a public network such as the Internet.

[0092] As shown in FIG. 10, 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 executing a program by a CPU 81.

[0093] The acquisition unit 102 acquires measurement data transmitted from the vibration sensor 60, 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.

[0094] The storage unit 110 further stores the mass of the mass 50 that constitutes the tuned mass damper 10 and the natural frequency (first natural frequency) of the floor F that is the target of vibration damping, which is specified in advance.

[0095] 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.

[0096] Furthermore, the calculation unit 104 identifies the effective length of the spring suitable for damping the vibration of the floor F based on the mass of the mass 50 stored in the memory unit 110 and the identified dominant frequency of the vibration of the floor F.

[0097] As a preliminary design step, the effective length of the spring is set based on the mass of the mass 50 and the natural frequency of the floor F, and the vibration control device 100 is then manufactured. After that, a pre-operation experiment is conducted using the manufactured vibration control device 100, and the relationship between the natural frequency of the tuned mass damper 10 and the control amount is confirmed, after which the control amount for operation is set.

[0098] The relationship between the rotation speed of the rotating shaft 75 of the motor 74, the rotation speed of the gear 72, and the length of insertion of the bolt 76 into the spring 30 according to the rotation of the gear 72 is specified in advance, and the memory unit 110 further stores this relationship data.

[0099] Based on the above-mentioned relationship data in the memory unit 110, the calculation unit 104 determines the rotation speed of the motor 74 that will achieve the determined effective length of the spring, and the operation unit 106 transmits command signals related to the determined rotation speed to the two motors 74, thereby performing synchronized drive control of the two motors 74.

[0100] By driving the two motors 74 in synchronization, the lengths of the corresponding springs 30 are adjusted to effective lengths suitable for damping vibrations of the floor F.

[0101] When the vibration of floor F caused by environmental vibration subsides, a command signal is sent from the operating unit 106 to the motor 74, and the motor 74 is driven and controlled so that the effective length of the spring matches the natural frequency of the tuned mass damper 10 with the primary natural frequency of floor F.

[0102] The display unit 108 displays the measurement data from the vibration sensor 60, which changes due to environmental vibrations (external disturbances), and further displays the dominant frequency of the vibration of the floor F identified based on the measurement data, and displays the effective length of the spring 30 suitable for damping the vibration of the floor F.

[0103] Next, another example of a tuned mass damper that constitutes a vibration damping device according to an embodiment will be described with reference to Figures 11 to 14. Here, Figure 11 is a side view of another example of a tuned mass damper that constitutes a vibration damping device according to an embodiment, and Figure 12 is a front view of another example of a tuned mass damper that constitutes a vibration damping device according to an embodiment, taken in the direction of arrow XII in Figure 11. Also, Figure 13 is a side view of yet another example of a tuned mass damper that constitutes a vibration damping device according to an embodiment, and Figure 14 is a plan view of yet another example of a tuned mass damper that constitutes a vibration damping device according to an embodiment, taken in the direction of arrow XIV in Figure 13.

[0104] The tuned mass damper 10A shown in Figures 11 and 12 differs from the tuned mass damper 10 in that the connecting member 40 carrying the mass 50 is of a flat type, supported by multiple springs 30 (four in the illustrated example).

[0105] The illustrated example includes four adjusting means 70 corresponding to the four springs 30, and the actuators 74 constituting each adjusting means 70 are controlled synchronously.

[0106] Furthermore, because of its flat shape, the connecting member 40 and the mass 50 mounted thereon reduce vibrations of the floor F as they vibrate in the X3 direction, which is the up-and-down direction, while maintaining a parallel posture as a whole.

[0107] As with the cantilever-type tuned mass damper 10, the length of each spring 30 in the flat-type tuned mass damper 10A is adjusted to an effective length suitable for damping vibrations in the floor F.

[0108] On the other hand, the tuned mass damper 10B shown in Figures 13 and 14 differs from the tuned mass dampers 10 and 10A in that it is a flat modified form in which a pair of connecting members 40A are attached to a pair of upright members 29 standing upright on the frame 20 via multiple springs 30 (in the illustrated example, two sets of two springs 30 make up a total of four), a mass 50 is attached in a sandwiched state between the pair of connecting members 40A, guide rails 90 are installed on the upper surface 21 of the frame 20, and running bodies 91 such as wheels are installed on the underside of the mass 50, so that the running bodies 91 run along the guide rails 90, allowing the mass 50 to vibrate freely in the horizontal direction, X4.

[0109] In the illustrated example, four adjusting means 70 corresponding to the four springs 30 are provided, and the actuators 74 constituting each adjusting means 70 are controlled in synchronization.

[0110] As with the cantilever-type tuned mass damper 10 and the flat-type tuned mass damper 10A, the length of each spring 30 in the flat-type modified tuned mass damper 10B is adjusted to an effective length suitable for damping vibrations in the floor F.

[0111] 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]

[0112] 10, 10A, 10B: Tuned mass damper 20: Stand 21:Top surface 22: Rotating part 25: Protrusion 26: Storage groove 27:Through hole 28: Guide tube 29: Standing material 30: Spring 40, 40A: Connecting member 41:Top surface 42: Bottom surface 43: Rotating part 45:Through hole (tapped hole) 45a: Thread groove 50: Square 60: Vibration sensor 70,70A,70B: Adjustment means 72: Gear 72a:Hollow 72b: Thread groove 74: Actuator (motor) 75: Rotation axis 76, 77: Shaft member (bolt) 76a: Shaft body 76b:Head 76c: Thread groove 78: Long nut 78a:Main body 78b: Top plate 78c: screw hole 78d:Hollow 78e: Thread groove 78f: opening 79: Thread groove 80: Control unit 90: Guide rail 91: Running body 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 spring installed on the frame; a mass supported by the spring; and an adjustment means for adjusting the effective length of the spring. 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, and the effective length of the spring suitable for vibration damping is identified based on the mass of the mass and the dominant frequency, thereby controlling the adjustment means.

2. the mass is attached to a connecting member, the connecting member being supported by the spring; The adjusting means is a shaft member that can penetrate a through hole provided in either the connecting member or the base and enter the inside of the spring; an actuator that raises and lowers the shaft member, 2. The vibration damping device according to claim 1, wherein the control unit adjusts the length of the shaft member that penetrates into the spring by operating the actuator, thereby adjusting the area where the spring protrudes from the shaft member as the effective length of the spring.

3. the mass is attached to a connecting member, the connecting member being supported by the spring; The adjusting means is a bolt attached to either the connecting member or the frame; a long nut having a hollow, accommodating at least a portion of the bolt in the hollow, and threadably engaging with the bolt; an actuator that directly or indirectly rotates the long nut to raise and lower the long nut relative to the bolt, The inner wall of the long nut is provided with a thread groove for guiding the spring as it enters and leaves the hollow.

2. The vibration damping device according to claim 1, wherein the control unit operates the actuator to raise and lower the long nut relative to the bolt, and adjusts the length of the spring that penetrates into the hollow in accordance with the raising and lowering of the long nut, thereby adjusting the area where the spring protrudes from the long nut as the effective length of the spring.

4. 2. The vibration damping device according to claim 1, wherein, when the component is vibrating, the control unit controls the adjusting means to adjust the effective length of the spring so that the dominant frequency of the vibration of the component matches the natural frequency of the tuned mass damper.

5. One end of the connecting member is rotatably or non-rotatably attached to the stand or to an upright member standing upright on the stand, and the other end of the connecting member is supported by the spring, 4. The vibration damping device according to claim 2, wherein the tuned mass damper is of a cantilever type, with the mass attached to the connecting member.

6. A plurality of the springs are attached to the base, 4. The vibration damping device according to claim 2, wherein the tuned mass damper is of a flat type, in which the mass is supported by a plurality of the springs via the connecting members.

7. a pair of connecting members are attached to a pair of standing members standing upright from the frame, respectively, via the springs, and the mass is attached in a sandwiched state between the pair of connecting members; 4. The vibration damping device according to claim 2 or 3, wherein a rail is provided on the frame, and the mass is attached along the rail so as to be able to vibrate laterally.

8. the component to be damped is a floor, 4. The vibration damping device according to claim 2, wherein at least the tuned mass damper is installed directly or indirectly on the floor.

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