JP2006002862A - Vibration control device of structure - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a vibration control device of a structure capable of simplifying a configuration, saving a space, and reducing possibility of corrosion by forming a damping mechanism such as a heavy weight into a sealed structure. <P>SOLUTION: This vibration control device of the structure is provided with a sealed vessel 1 provided in the structure 30, the heavy weight 7 provided movably in the sealed vessel to partition the inside of the sealed vessel 1 into a first space 11A and a second space 11B, and energizing bodies 12A, 12B for energizing the heavy weight in the direction of travel. A fluid flow rate control means 20 communicating with at least the space on one side is provided to adjust damping coefficient freely by controlling the fluid flow rate control means. The fluid flow rate control means is controlled in accordance with movement of the heavy weight by letting fluid in the space flow through the fluid flow rate control means to control flow rate of fluid in spite of a simple device configuration, ever-change damping characteristic to realize the optimum damping rate, and save electric power. The whole vibration control device can be miniaturized and be inexpensively constituted by realizing the sealed structure to avoid contact with outside air as much as possible and eliminate possibility of corrosion even under corrosion environment. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a structure damping device used for damping a structure exposed to vibration caused by natural disturbance or artificial disturbance such as a bridge, a chimney, and a building.

  In general, a structure such as a bridge or a high-rise building is provided with a vibration control device for reducing vibration. Conventionally, a tuned mass damper is well known as one type of vibration damping device. This is intended to reduce vibration by installing weights and springs on the structure in synchronization with the structure's vibration cycle, but the damping factor is nonlinear due to mechanical friction and the attenuator used. It becomes a characteristic, and it becomes difficult to always realize optimum attenuation.

  On the other hand, a drive motor is directly connected to the weight on the structure, and the drive motor is controlled by a computer to control the vibration of the structure more actively than the conventional tuned mass damper. A mass damper (Active Mass Damper) is known. However, since this active mass damper controls the weight with a drive motor, it consumes a large amount of power, and if the drive motor does not operate during a computer trouble or power failure, it will not function as a vibration damping device. Furthermore, the use of a relatively large drive motor increases the cost.

Therefore, by adding a variable damping mechanism to the tuned mass damper, a semi-active tuned mass damper (damping device) that improves the reliability of the device by functioning as a tuned mass damper at the minimum in the event of a computer trouble or power failure. ) Has been developed (see, for example, Patent Document 1).
JP-A-7-113436

  However, the above-described conventional vibration damping device (semi-active tuned mass damper) is a large-scale structure with exposed mechanisms such as a weight, a spring, and an actuator (attenuator). It is difficult to install in a narrow space such as under the floor of a building, and in a corrosive environment, there is a problem that corrosion easily occurs due to contact with outside air.

  Accordingly, the invention according to claim 1 of the present invention is a structure damping device that can save space by reducing the worry of corrosion while simplifying the configuration by providing a damping structure such as a weight with a sealed structure. Is intended to provide.

  To achieve the above-described object, a vibration damping device for a structure according to claim 1 of the present invention includes a sealed container installed in the structure, a first space and a second space in the sealed container. A weight that is movably provided in the sealed container so as to be partitioned into a space; and a biasing body that biases the weight in the moving direction. The present invention is characterized in that the damping coefficient is adjustable by controlling the fluid flow rate control means.

  Therefore, according to the first aspect of the present invention, when an amplitude (vibration) acts on the structure and the integral sealed container, the biasing body on the side opposite to the direction of the amplitude is compressed and the weight is compressed. Thus, the sealed container moves, and at that time, the weight is delayed (oscillated) in the direction of the amplitude and a damping force is generated due to the relative speed with the structure. Furthermore, since the vibration of the structure and the weight is adjusted so as to be substantially synchronized, the structure and the weight are substantially coupled to vibrate. The damping force exerts an effect of suppressing the coupled vibration, and consequently contributes to the vibration suppression of the structure body. At this time, the fluid in the space to be compressed (reduced) or expanded (expanded) can flow through the fluid flow rate control means.

  Thus, by controlling the fluid flow rate control means in accordance with the movement of the weight, the damping characteristic is adjusted momentarily so that the flow rate of the fluid can be controlled and the optimum damping rate can be realized while having a simple device configuration. And can be changed. That is, when the weight amplitude is small, the additional attenuation can be reduced by increasing the flow amount in the fluid flow control means, and when the amplitude is large, the additional attenuation is achieved by decreasing the flow amount in the fluid flow control means. Can be increased. In addition, by using a sealed structure in which a weight and an urging body are housed in a sealed container, the entire vibration damping device can be downsized (compact), and contact with outside air can be avoided as much as possible. Thus, there is no need to worry about corrosion even in a corrosive environment.

  The structure damping device according to claim 2 of the present invention is the bypass pipe in which the fluid flow rate control means is provided between the first space and the second space in the configuration according to claim 1 described above. And a variable valve provided in the bypass pipe portion and a control unit for controlling the variable valve, wherein the attenuation coefficient can be adjusted by controlling the variable valve. .

  Therefore, according to the invention of claim 2, when amplitude (vibration) acts on the sealed container side, the space on the side opposite to the direction of the amplitude is compressed (reduced), so that the fluid in the space is bypassed. It flows into the space expanded (expanded) in the direction of the amplitude through the tube. As a result, the control unit controls the opening and closing of the variable valve according to the movement of the weight, thereby controlling the flow rate of the fluid through the bypass pipe and adjusting the damping characteristics from moment to moment so as to achieve the optimum damping rate. And can be changed. That is, when the weight amplitude is small, the additional attenuation can be reduced by opening the variable valve, and when the amplitude is large, the additional attenuation can be increased by closing the variable valve. Furthermore, by controlling the variable valve by the control unit, it is possible to realize an arbitrary opening degree from moment to moment, while achieving a simple device configuration, and also to achieve power saving.

  According to the first aspect of the present invention, when the amplitude (vibration) acts on the structure and the integral hermetic container, the weight is compressed in the state in which the biasing member on the side opposite to the direction of the amplitude is compressed. In this case, the sealed container moves, and at this time, the weight is delayed (oscillated) in the direction of the amplitude and a damping force is generated due to the relative speed with the structure. Further, since the vibrations of the structure and the weight are adjusted so as to be substantially synchronized, the structure and the weight vibrate substantially in combination. Since the damping force exhibits an effect of suppressing the coupled vibration, it can contribute to the vibration suppression of the structure body as a result. At this time, the fluid in the space compressed (reduced) or expanded (expanded) can flow through the fluid flow rate control means. As a result, by controlling the fluid flow rate control means according to the movement of the weight, the flow rate of the fluid can be controlled and the damping characteristic can be adjusted momentarily so as to achieve the optimum damping rate, even with a simple device configuration. And can be realized with power saving. That is, when the weight amplitude is small, the additional attenuation can be reduced by increasing the flow rate in the fluid flow control means, and when the amplitude is large, the additional attenuation can be reduced by decreasing the flow amount in the fluid flow control means. Can be big.

  In addition, by using a sealed structure in which a weight and an urging body are housed in a sealed container, the entire vibration damping device can be reduced in size and configured at low cost, and contact with outside air can be prevented. It can be avoided as much as possible, and there is no need to worry about corrosion even in a corrosive environment, and the need for maintenance associated with corrosion can be avoided as much as possible. And since it can comprise compactly, it can install easily in the limited narrow space. Further, the vibration damping device can maintain the function as a tuned mass damper even if the fluid flow rate control means is damaged or a power failure occurs, and has a fail-safe function against an emergency failure.

  According to the second aspect of the present invention, when the amplitude (vibration) acts on the sealed container side, the fluid in the space flows into the space expanded (expanded) in the direction of the amplitude through the bypass pipe. Will do. As a result, the flow rate of the fluid through the bypass pipe can be controlled by controlling the opening and closing of the variable valve by the control unit according to the movement of the weight, and the damping characteristic is momentarily adjusted so as to realize the optimum damping rate. Can change. That is, when the weight amplitude is small, the additional attenuation can be reduced by opening the variable valve, and when the amplitude is large, the additional attenuation can be increased by closing the variable valve. Furthermore, by controlling the variable valve by the control unit, it is possible to realize an arbitrary opening degree from moment to moment, while achieving a simple device configuration, and also to achieve power saving.

[Embodiment 1]
Embodiment 1 of the present invention will be described below with reference to FIGS.
In FIG. 1, an airtight container 1 is formed in a cylinder body shape by a tube body 2 and a pair of head cover bodies 3 in contact with both ends of the tube body 2. The tie lot 4 is provided to maintain a sealed shape. A pair of end guide shafts 5 are provided in the sealed container 1 with the outer ends thereof being fitted to the head cover body 3, and are fitted between the inner ends of the end guide shafts 5 so as to be central guide shafts. 6 is provided.

  Furthermore, a weight 7 consisting of a pair of divided bodies is provided in the sealed container 1, and these weights 7 are integrated by a plurality of reamer bolts 9 with the adjustment weight 8 in contact with the outer surface side thereof. It has become. At this time, the weight 7 has a ring shape, and is provided so as to be movable in the length direction of the sealed container 1 by being externally fitted to the central guide shaft 6 via a ball spline 10. Further, the outer diameter of the weight 7 is formed to be slightly smaller than the inner diameter of the tube body 2, so that the outer peripheral surface of the weight 7 can be slidably contacted with the inner peripheral surface of the tube body 2. Thus, the inside of the sealed container 1 is partitioned into the first space 11A and the second space 11B, and only the sealed container 1 and the weight 7 constitute an air damper.

  Compression springs (examples of urging bodies) 12A and 12B are provided between the head cover body 3 and the weight 7 so as to be fitted on the end guide shaft 5 and the central guide shaft 6, respectively. 12A and 12B are configured to urge the weight 7 in the moving direction. A plurality of stoppers 13 are provided on the outer surface side of the weight 7, respectively, and these stoppers 13 are configured to be able to contact the inner end surface of the end guide shaft 5.

  A fluid flow rate control means 20 is provided in communication with at least one space, and the damping coefficient can be adjusted by controlling the fluid flow rate control means 20. Here, the fluid flow rate control means 20 includes a bypass pipe 21 provided between the first space 11A and the second space 11B, and an openable / closable control valve (an example of a variable valve) provided in the bypass pipe 21 portion. ) 22 and a computer (an example of a control unit) 25 for controlling the control valve 22.

  That is, the both head cover bodies 3 are formed with recessed communication passages 23 communicating with the first space 11A or the second space 11B, respectively. 3 are each provided with a connecting body 24. The bypass pipe 21 is disposed outside the tube body 2, and one end thereof is connected to one connection body 24, and the other end is connected to the other connection body 24 via the control valve 22. The control valve 22 is controlled to open and close by a control signal 25a from the computer 25, so that the attenuation coefficient can be adjusted.

Each of the head cover bodies 3 is provided with mounting legs 26, and the hermetic container 1 is configured to be installed (attached) to the structure 30 side via these mounting legs 26.
Hereinafter, the operation in the first embodiment will be described.

  In FIG. 1, when the amplitude (vibration) AB acts on the structure 30 and the integral hermetic container 1, the compression springs 12B and 12A on the opposite side to the direction of the amplitude AB are compressed. Thus, the sealed container 1 is moved with respect to the weight 7, and at this time, the weight 7 oscillates (vibrates) in the direction of amplitude AB with a delay, and is relative to the structure 30. A damping force resulting from the speed is generated. Furthermore, since the vibrations of the structure 30 and the weight 7 are adjusted so as to be substantially synchronized, the structure 30 and the weight 7 vibrate substantially in combination. The damping force exhibits an effect of suppressing the coupled vibration, and consequently contributes to the vibration suppression of the structure 30. At this time, the spaces 11B and 11A opposite to the direction of the amplitude AB are also compressed (reduced), so that the air in the spaces 11B and 11A flows through the bypass pipe 21 and the like ab. Thus, it flows into the spaces 11A and 11B expanded (enlarged) in the direction of the amplitude AB.

  Therefore, by controlling the opening and closing of the control valve 22 by the control signal 25a from the computer 25 according to the movement of the weight 7, the flow rate of air through the bypass pipe 21 and the like is controlled, and the optimum attenuation rate is realized. Thus, the attenuation characteristic can be changed from moment to moment. That is, when the weight 7 has a small amplitude, the additional attenuation can be reduced by opening the control valve 22, and when the amplitude is large, the additional attenuation can be increased by closing the control valve 22.

  As described above, by storing the weight 7 and the compression springs 12A and 12B in the sealed container 1, the entire vibration damping device can be downsized (compact) and configured at low cost. Therefore, it is possible to avoid the necessity of maintenance associated with corrosion as much as possible. Further, the vibration damping device can control the control valve 22 with the computer 25 to realize an arbitrary opening degree from moment to moment, while being a simple device configuration, and can be realized with power saving. In addition, even if the control valve 22 is damaged or a power failure occurs, the function as a tuned mass damper can be maintained, and a fail-safe function for an emergency failure is provided.

  Since it can be configured more compactly, as shown in FIG. 2, it can be easily installed in a limited narrow space such as the inside of a box girder bridge in a bridge as an example of the structure 30. 2 has the same mechanism as the device shown in FIG. 1, but FIG. 1 is intended for horizontal vibration, whereas FIG. 2 shows that the vibration damping device is set up in the vertical direction. It is intended for vertical vibrations (vertical vibrations), and can handle such vertical vibrations.

Hereinafter, the vibration control method in the first embodiment will be described.
FIG. 3 shows a relationship diagram (conceptual diagram) between amplitude and attenuation. The figure shows the relationship (conceptual diagram) between nonlinear damping and optimum damping due to friction damping.

  In conventional tuned mass dampers, the amplitude dependence of the damping occurs due to the effect of frictional damping of the device drive unit, and when a normal attenuator (oil damper, air damper, magnetic damper, etc.) is used, it is shaded As shown, the effect of nonlinearity due to frictional damping cannot be avoided. On the other hand, by using the variable damping function of the vibration damping device of the present invention, the damping characteristic can be changed from moment to moment according to the movement of the weight 7 so as to realize the optimum damping rate. Specifically, when the amplitude of the weight 7 is small, the control valve 22 is opened to reduce the additional attenuation, and when the amplitude is large, the control valve 22 is closed to increase the additional attenuation. Non-linearity can be avoided.

  Further, the theoretical value of the optimum attenuation also changes according to the disturbance. Similarly, the optimum attenuation according to the disturbance can be realized by using the variable attenuation function. A control concept for realizing this optimum attenuation is shown in FIG. In FIG. 4 (FIG. 5 to be described later), 32 indicates a weight side accelerometer, 33 indicates a structure side accelerometer, and ТMD is an abbreviation for a tuned mass damper. As shown in FIG. 4, the optimum damping force assumed in advance can be realized by arbitrarily varying the bypass opening, that is, the opening of the control valve 22 by the control based on the calculation of the computer 25.

  Further, as shown in FIG. 5, the control law (optimal control theory, sliding mode control, etc.) with the response amount (response speed and response displacement) of the main body of the structure 30 and the tuned mass damper (weight 7) as a state quantity. The vibration control can also be performed by varying the opening of the control valve 22 so as to simulate the control force (for example, by applying the clipped optimal rule) so as to simulate the control force.

FIG. 6 shows a numerical simulation based on the sliding mode control law. As shown in FIG. 6, by using a semi-active tuned mass damper in which a variable damping function is added to the tuned mass damper, a greater vibration damping effect than that of a conventional tuned mass damper can be exhibited.
[Embodiment 2]
Next, a second embodiment of the present invention will be described with reference to FIG.

  In the second embodiment, a variable valve is installed without using a bypass pipe in a form using an air damper. In other words, the control valve 22 is directly installed on the other head cover body 3, and the control valve 22 communicates with the second space 11 </ b> B via the communication path 23.

As a result, it is possible to realize a compact vibration damping device, and further, by controlling the control valve 22 by the computer 25, an arbitrary opening degree can be realized every moment. However, in this case, since air enters and exits between the sealed container 1 and the outside air, it may be somewhat disadvantageous against corrosion in the sealed container 1. Note that the control valve 22 may be in the form of communicating with the first space 11 </ b> A via the communication path 23.
[Embodiment 3]
Next, Embodiment 3 of the present invention will be described with reference to FIG.

  The third embodiment is a modification of the first embodiment, and the magnetorheological fluid 28 is filled in the bypass pipe 21 from both the spaces 11A and 11B. In this case, a variable magnetic field body 29 is provided in the bypass pipe 21 instead of the variable valve, and by controlling the magnetic field of the variable magnetic field body 29 by the computer 25, it can be changed to an arbitrary magnetic field every moment. Thus, a variable attenuation function can be realized.

  As a modification of the third embodiment, a form in which the electrorheological fluid is filled in the bypass pipe 21 from both the spaces 11A and 11B is also possible. In this case, the variable attenuation function can be realized by making the applied voltage variable under the control of the computer 25.

In each of the above-described embodiments, the coiled compression springs 12A and 12B are used as the urging body, but this may be a tension spring or a leaf spring.
In the above-described embodiment, the weight 7 composed of a pair of divided bodies is used. However, this may be a weight composed of three or more divided bodies or a type in which one weight is used. May be.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partially cutaway front view of a structure damping device according to a first embodiment of the present invention. It is explanatory drawing in the state which installed the damping device in the bridge. It is a conceptual diagram of the variable attenuation function. It is control explanatory drawing for implement | achieving the optimal attenuation | damping by the variable valve in the damping device of the structure. It is control explanatory drawing of the semi-active control using the control theory in the damping device of the structure. It is a numerical simulation figure of the damping effect in the damping device of the structure. FIG. 9 is a partially cutaway front view of a structure damping device according to a second embodiment of the present invention. FIG. 7 is a schematic front view of a structure damping device according to a third embodiment of the present invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Sealed container 2 Tube body 3 Head cover body 5 End guide shaft 6 Center guide shaft 7 Weight 10 Ball spline 11A 1st space 11B 2nd space 12A Compression spring (biasing body)
12B Compression spring (biasing body)
20 Fluid flow rate control means 21 Bypass pipe 22 Control valve (variable valve)
23 Communication path 24 Connection body 25 Computer (control part)
25a Control signal 28 Magnetorheological fluid 29 Variable magnetic body 30 Structure 32 Weight side accelerometer 33 Structure side accelerometer

AB Amplitude direction ab Air flow direction

Claims (2)

  A sealed container installed in the structure, a weight movably provided in the sealed container so as to partition the sealed container into a first space and a second space, and moving the weight A fluid flow control means provided in communication with at least one space, and the damping coefficient can be adjusted by controlling the fluid flow control means. Structure damping device. The fluid flow rate control means comprises a bypass pipe provided between the first space and the second space, a variable valve provided in a portion of the bypass pipe, and a control unit for controlling the variable valve, 2. The structure damping device according to claim 1, wherein the damping coefficient is adjustable by controlling the variable valve.

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