JP2002081492A - Vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To secure a mass required for vibration modes and effectively control vibration in two vibration modes while reducing the sum of the whole mass of bodies of mass of active vibration absorbers by independently operating the pair of active vibration absorbers as separated into two parts on two vibration modes different in natural vibration frequency or operating them in an integral manner. SOLUTION: This vibration damping device comprises the pair of first and second active vibration absorbers 12, 13 arranged in a building in spaced relation and harmonized to the natural vibration frequency of one of vibration modes of the building having a lower natural vibration frequency, displacement extracting means 24 for extracting the displacement of the body of mass 17 for each of active vibration absorbers in the vibration mode of the building having a higher natural vibration frequency, and a spring member 25 mounted between the bodies of mass of the active motion vibration absorbers for transmitting spring force corresponding to a difference in displacement extracted by the displacement extracting means between the bodies of mass to make these active vibration absorbers integrally harmonized to the natural vibration frequency of the vibration mode of the building having a higher natural vibration frequency.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention provides a hybrid active dynamic vibration absorber comprising a TMD comprising a mass, an elastic bearing and a damping member, and an active control device for controlling the movement of the mass of the TMD. The present invention relates to a vibration damping device for damping an object to be damped.

[0002]

2. Description of the Related Art Conventionally, various vibration damping devices have been proposed.
Among them is a vibration damping device having a TMD (tuned mass damper) structure. The TMD is provided with a mass body, an elastic support body, and a damping member. The mass body is attached to the vibration damping object via the elastic support body, and the damping member is acted on. The (damping region) is tuned in advance to the natural frequency of the object to be damped. As a result, the mass body is vibrated by the vibration of the vibration damping object, and the vibration of the vibrated mass body is delayed and transmitted to the vibration damping object, thereby canceling the vibration of the vibration damping object. It can be damped.

[0003] Further, the TMD may be provided with an active control device to constitute a hybrid type active dynamic vibration absorber. This active dynamic vibration absorber can actively control the movement of the mass body of the TMD by the active control device, and can more precisely control vibration from small amplitude to large amplitude vibration.

By the way, when the object to be damped is a building,
In general, many buildings have a flat rectangular shape, and in this case, the building experiences translational vibration that oscillates parallel to the short side direction and torsional vibration that oscillates around the vertical axis in the rotational direction. It is desirable to be excited and dampen both these translational and torsional vibrations. Here, the reason for limiting the short side direction of the building as the translational vibration is that the natural frequency in the short side direction is lower than that in the long side direction, and the vibration external force such as strong wind or earthquake is input to the building. In such a case, the short side direction is likely to swing.

[0005] When the vibration mode of both the translational vibration and the torsional vibration is damped as described above, it is necessary to provide the hybrid type active dynamic vibration absorber individually corresponding to each vibration mode. And an active dynamic vibration absorber for damping torsional vibration.

[0006]

However, the mass of the mass of the active dynamic vibration absorber required for damping the building is about 3.5% as a damping constant in passive damping by TMD.
In order to set the additional attenuation of the building, a large mass of about 1% of the effective mass of the building is required at a minimum. For this reason,
To control two vibration modes, translational vibration and torsional vibration, it is necessary to provide two active dynamic vibration absorbers. Therefore, an additional mass twice as large as that required to control one vibration mode is required. .

[0007] For this reason, not only does the manufacturing cost of each mass body greatly increase, but also at the minimum mass of about 1% of the effective mass, when a large-amplitude vibration such as a large earthquake is input, the mass mass of the mass body increases. Although it is necessary to significantly increase the travel distance, it is difficult to secure the large travel distance in terms of space and structure.In the case of a large earthquake, the movement of the mass body is generally restricted by stoppers and brakes. is there.
In this case, the mass body whose movement is restricted will act as a simple weight of the building, and the load on the roof where the active dynamic vibration absorber is usually installed will be increased, and the swing amount during an earthquake will be further amplified. become.

[0008] Therefore, in consideration of the case where movement of the mass body during a large earthquake is restricted, it is desirable that the mass body of the active dynamic vibration absorber installed on the rooftop of the building be as light as possible, but on the other hand, strong wind and allowable amplitude. It is desirable to make the mass as heavy as possible in order to exhibit the original vibration damping function provided by the active dynamic vibration absorber when the earthquake falls within the range, and there are conflicting requirements for the mass between the two. Will occur.

Therefore, the present invention has been made in view of such a conventional problem, and a pair of active dynamic vibration absorbers which are divided into two independently act on two vibration modes having different natural frequencies. Or by acting as one, securing the mass required for each vibration mode while reducing the overall mass sum of the mass body of each active dynamic vibration absorber,
Accordingly, it is an object to provide a vibration damping device that effectively damps two vibration modes.

[0010]

In order to achieve the above object, the present invention comprises a TMD comprising a mass, an elastic bearing and a damping member, and an active control device for controlling the movement of the mass of the TMD. Equipped with a hybrid type active dynamic vibration absorber, two modes of translational vibration mode and torsional vibration mode
A vibration damping device for damping a vibration damping object in which two vibration modes are excited, wherein the vibration damping device is arranged at a distance from the vibration damping object, and includes a translational vibration mode and a torsional vibration mode. A pair of active dynamic vibration absorbers set in synchronization with the natural frequency of one of the lower vibration modes of the natural object, and a pair of active vibration absorbers of the higher natural mode of the vibration damping object A displacement amount extracting means for extracting a displacement of each mass body of the active dynamic vibration absorbers, and a pair of active dynamic vibration absorbers interposed between the mass bodies of the pair of active dynamic vibration absorbers. A spring member for transmitting a spring force according to the displacement difference extracted by the displacement amount extracting means between the mass bodies in order to tune to a natural frequency of a vibration mode having a higher natural frequency. And

Preferably, the displacement amount extracting means includes a boosting means for reducing the displacement of the mass body and transmitting the displacement to the spring member.

[0012]

Embodiments of the present invention will be described below in detail with reference to the accompanying drawings. 1 to 5 show an embodiment of the vibration damping device of the present invention, and FIG. 1 is a front view of the vibration damping device showing a state where an active dynamic vibration absorber is installed on an object to be damped.
2 is a plan view thereof, FIG. 3 is a side view of an active dynamic vibration absorber installed on an object to be damped, FIG. 4 is an enlarged side view showing displacement amount extracting means provided on the active dynamic vibration absorber, and FIG. FIG. 4 is an enlarged plan view showing a connected state of the displacement amount extracting means.

That is, the vibration damping device 10 of the present embodiment uses the building 11 in which the translational vibration and the torsional vibration are excited as vibration damping targets, and a pair of first active dynamic vibration absorbers on the rooftop 11a of the building 11. 12 and the second active dynamic vibration absorber 13 are provided. The building 11 is a general high-rise building having a flat rectangular shape as shown in FIG. 2, and the building 11 has two vibration modes of translational vibration and torsional vibration as vibrations that appear particularly remarkably. . Translational vibration is specified as vibration that is translated in the short side direction (X). That is, the natural frequency of the building 11 is set to be shorter in the short side direction (X) than in the long side direction (Y), and the short side direction (X) is easily oscillated by vibration input due to wind or earthquake. The translational vibration in the side direction (X) is to be damped.
The building 11 has a short side direction (X) and a long side direction (Y).
Due to the difference in length, the above-mentioned torsional vibration occurs around the axis in the vertical direction due to vibration input, and this torsional vibration becomes more remarkable as the X / Y aspect ratio increases.

The present embodiment basically includes a TMD 14 comprising a mass body 17, an elastic bearing body 16 and a damping member,
A hybrid type active dynamic vibration absorber including an active control device 15 for controlling the movement of the mass body 17 of the MD 14 is provided to control the building 11 in which two vibration modes of a translational vibration mode and a torsional vibration mode are excited. The vibration damping device of the above, is disposed in the building 11 at an interval from each other,
A pair of first and second active dynamic vibration absorbers 12 and 13 set in synchronization with the natural frequency of one of the lower vibration modes of the building 11 of the translational vibration mode and the torsional vibration mode. And a pair of active dynamic vibration absorbers 1 in a vibration mode having a higher natural frequency of the building 11.
Displacement amount extracting means 24 for extracting the displacement of each of the mass bodies 17, and a pair of active dynamic vibration absorbers 12, 13
In order to tune the pair of active dynamic vibration absorbers 12 and 13 integrally with each other in order to tune to the natural frequency of the higher vibration mode of the building 11,
A spring member 25 for transmitting a spring force corresponding to the displacement difference extracted by the displacement amount extracting means 24 between the mass bodies 17, and the displacement amount extracting means 24 includes Is provided as a booster for reducing the displacement of the spring member 25 and transmitting it to the spring member 25.

The first active dynamic vibration absorber 12 and the second active dynamic vibration absorber 13 are each constituted by adding an active control device 15 to the TMD 14 as shown in FIG.

The TMD 14 includes an elastic bearing 16, a mass 17 supported swingably on the elastic bearing 16, and a damping member (not shown). Elastic bearing 1
6, a small laminated rubber 16a is a steel plate 16 as shown in FIG.
b, and is fixed to the above-mentioned rooftop floor 11a via the substrate 18, but the elastic bearing 16 is not limited to the multi-layer laminated rubber, but may be a spring having a restoring force. Any member having a function may be used. Further, the mass body 17 is formed as a rectangular flat plate-shaped concrete block body having a thick wall t, and has a mass corresponding to the effective mass of the building 11 to be damped. At this time, if the material of the mass body 17 is concrete, a predetermined mass can be obtained at low cost, but of course, other materials can be used as long as the required mass can be secured.

The rectangular mass member 17 is stably supported by the elastic bearing members 16 arranged at the four corners, and the vibration of the building 11 is reduced by the elastic bearing member 16, the mass member 17, and the damping member. Is input to the vibration system constituted by the following formula, the mass body 17 swings (vibrates) relatively to the rooftop floor 11a of the building 11. At this time, by tuning the resonance frequency of the vibration system to the vibration mode of the building 11 to be damped, the vibration mode can be damped. In addition, between the mass body 17 and the building 11,
An unillustrated damping member such as the above-described damper is provided to attenuate the swing of the mass body 17.

As shown in FIG. 3, the active control device 15 includes an additional mass 20 that can move the upper surface of the mass body 17 in the short side direction (X) of the building 11, and an actuator 21 that controls the movement of the additional mass 20. It is configured as an additional mass inertial force type. The actuator 21 is a ball screw 22
The ball screw 22 is rotationally driven by a drive source (not shown) such as a motor built in a support frame 23 fixed to the mass body 17. The driving source is driven based on a signal detected by a vibration sensor installed at an appropriate place in the building 11, and the driving causes the ball screw 22 to rotate and the additional mass 20 to move quickly and smoothly. Therefore, the swing of the mass body 17 is controlled by the movement of the additional mass 20, so that the vibration of the building 11 can be precisely controlled.

Here, in this embodiment, the first active dynamic vibration absorber 12 and the second active dynamic vibration absorber 13 are arranged in a direction perpendicular to the vibration direction (X) of the translational vibration of the building 11, that is, the long side. They are arranged at a predetermined distance L in the direction (Y). Then, the mass of each mass body 17 of the first and second active dynamic vibration absorbers 12 and 13 is set to half of the conventionally set mass, that is, the minimum mass of the conventional mass body and the effective mass of the building 11 as the minimum necessary mass. Although the mass is set to about 1%, in the present embodiment, the mass of each mass body 17 is
1 is set to about 0.5% of the effective mass.

Accordingly, the total mass sum of the mass bodies 17 of the first and second active dynamic vibration absorbers 12 and 13 is equal to the building 1
The effective mass is about 1% of the effective mass of one, and the original mass required for damping the building 11 can be obtained by the cooperation of the mass members 17. Further, the elastic support 16 for elastically supporting each mass 17 is also provided in the first active dynamic vibration absorber 1.
The one formed under the same condition by the second and second active dynamic vibration absorbers 13 is used.

The resonance frequency of both the first and second active dynamic vibration absorbers 12 and 13 in an inactive state,
That is, this inactive state is a state in which the active control device 15 is not operated, and the active control device 15
The resonance frequency in a state in which the additional mass 20 is stopped moving is tuned to the lower one of the natural vibrations of the translational vibration and the torsional vibration of the building 11, respectively. It is assumed that the natural frequency is lower than the natural frequency of the torsional vibration, and the resonance frequencies of the first and second active dynamic vibration absorbers 12 and 13 are tuned to the natural frequency of the translational vibration. Therefore, the translational vibration of the building 11 in the short side direction (X) is the first and the second in the inactive state.
The active vibration dampers 12 and 13 cooperate to effectively dampen the vibration.

On the other hand, the first active dynamic vibration absorber 12 and the second active dynamic vibration absorber 13 extract the movement of each mass body 17 as a relative displacement difference when a torsional vibration higher than the natural frequency of the translational vibration occurs. And the two mass bodies 17 are connected via the displacement amount extracting means 24, and a spring member 25 is provided in the middle of the displacement amount extracting means 24 so that the natural frequency is higher. In the vibration mode, a change in the spring force of the spring member 25 is added to the relative displacement movement of both mass bodies 17.

That is, the displacement amount extracting means 24 shown in FIG.
As shown in FIG. 4, the mechanism is configured to take out the displacement amount of the mass body 17 in the X direction, and the displacement amount of the mass body 17 is taken out as the rotation amount of the rotating body 26 as a booster. The rotating body 26 is supported by a support 27 fixed at the center of the substrate 18.
Rotatably supported by the first rotating member 26
Both ends of the cable 28 are the displacement take-out frames 29 of the mass body 17.
, And the rotating body 26 is rotated by the movement of the displacement take-out frame 29 in the X direction. At this time,
The direction in which the first cable 28 is wound around the rotating body 26 is the same in the first active dynamic vibration absorber 12 and the second active dynamic vibration absorber.
Are rotated in the same direction with respect to the movement of each mass body 17 in the same direction.

Both ends 29 in the X direction of the displacement take-out frame 29
a, 29a are attached to a pair of rails 30, 30 fixed to the lower surface of the mass body 17 in the Y direction so as to be relatively movable in the Y direction via a first linear bearing 31, and the displacement take-out is performed. Both sides 29b, 2 in the Y direction of the frame 29
9b is supported by the support 27 via a second linear bearing 32 so as to be movable in the X direction. The mounting portion between the first linear bearing 31 and the displacement take-out frame 29 is vertically movably mounted via a third linear bearing 33 so as to absorb the vertical deformation of the mass body 17.

Accordingly, with respect to the displacement of the mass body 17 in the X direction, the rail 30 is locked to the first linear bearing 31 and the two are integrated to move the displacement take-out frame 29 to the mass body 1.
7 to rotate the rotating body 26.
On the other hand, with respect to the displacement of the mass body 17 in the Y direction, the rail 30 is moved to the first linear bearing 31 while the displacement take-out frame 29 is restricted from moving by the second linear bearings 32 on both sides.
, The displacement take-out frame 29 is prevented from being moved in the X and Y directions, and the rotating body 26 is stopped without being rotated.

The first and second active dynamic vibration absorbers 12,
13, a large diameter portion 26a and a small diameter portion 26b are formed on each of the rotating bodies 26, so that the rotating bodies 26 function as booster means, and the first cable 28 is connected to the large diameter section 26a. And the small diameter portions 26b are connected by winding both ends of the second cable 34. At this time, the large-diameter portions 26a and the small-diameter portions 26b of the rotating bodies 26 are formed to have the same diameter. Then, both ends of the second cable 34 are wound around the opposing small-diameter portions 26b as reverse windings, and when each rotating body 26 is rotated in the same direction and at the same rotation angle, the two small-diameter portions 26b are unreeled. At the same time, the fed amount is wound up by the other small diameter portion 26b.

Therefore, when the rotating body 26 is rotated via the first cable 28 by the moving component of the mass body 17 in the X direction, and when the second cable 34 is wound around the rotating body 26 by this rotation, These first cables 28
The difference between the diameters of the winding portions of the second cable 34 causes a leverage between the two cables 28 and 34. For this reason, the displacement amount and displacement force (tensile force) of the mass body 17 input to the first cable 28 can be output to the second cable 34 with a small displacement amount and a large displacement force (tensile force). it can.

The above-described spring member 25 is attached to an intermediate portion of the second cable 34, and a relative difference occurs between the rotation amounts of the rotating bodies 26 of the first active dynamic vibration absorber 12 and the second active dynamic vibration absorber 13. Then, a change in the spring force of the spring member 25 is added to the second cable 34. In the present embodiment, the spring member 25 is constituted by a compression coil spring, and a pretension is added to the spring member 25 in an initial state, and the second cable 34 is always kept in a tension state. By the way, in the present embodiment, the pretension is added to the spring member 25 in the initial state, and this pretension acts on each mass body 17 in the stationary state via the displacement amount extracting means 24. In the state where the pretension is added, the first and second active dynamic vibration absorbers 12 and 13 are provided.
Is set to be tuned to the natural frequency of the translational vibration.

With the above configuration, the vibration damping device 1 of the present embodiment
When the external force due to wind or earthquake is input to the building 11 to cause translational vibration or torsional vibration in the short side direction (X), these two vibration modes are the first active dynamic vibration absorber. The vibration is damped by the vibration damper 12 and the second active dynamic vibration absorber 13. The vibration damping function according to each vibration mode will be described below.

(1) Translational Vibration When the building 11 is translated in the X direction, each of the mass bodies 17 of the first active dynamic vibration absorber 12 and the second active dynamic vibration absorber 13 has a zero effective mass of the building 11. .5%
And the weight is the same, each mass 17
Reciprocate with the same phase. Then, the movement of each mass body 17 is controlled by the displacement extraction frame 2 of the displacement amount extracting means 24.
9, the respective rotating bodies 26 rotate in the same direction with the same amount of rotation. For this reason, the second cable 34 whose both ends are reversely wound around the small diameter portion 26 b of each rotating body 26 is fed out from the small diameter portion 26 b of one rotating body 26, and the amount of this drawn out is the same as that of the other rotating body 26. Small diameter part 2
6b, so that no deformation force acts on the spring member 25. Accordingly, each of the mass bodies 17 of the first active dynamic vibration absorber 12 and the second active dynamic vibration absorber 13 is tuned to the initially set frequency, that is, the translational vibration, without the spring force of the spring member 25 acting. And the oscillating mass at that time is the mass 17 of each of the first and second active dynamic vibration absorbers 12 and 13.
Therefore, the required mass, that is, a mass of about 1% of the effective mass of the building 11 can be secured, and the translational vibration can be effectively damped.

Further, the first and second active dynamic vibration absorbers 1
When the translational vibrations are damped by the vibration control units 2 and 13, the active mass control device 15 is operated based on the signal of the vibration sensor to control the movement of the additional mass 20, so that the translational vibrations are precisely damped and the building is controlled. 11 can be effectively removed.

(2) Torsional Vibration Each of the mass bodies 1 of the first active dynamic vibration absorber 12 and the second active dynamic vibration absorber 13 due to the torsional deformation of the building 11.
7 reciprocates with respect to the building 11 with an opposite phase. Then, the movement of each mass body 17 is performed by the displacement amount extracting means 2.
In order to rotate the respective rotating bodies 26 in the reverse direction via the displacement take-out frames 29 of the fourth cable 4, both ends of the second cable 34 are wound in synchronization with the small diameter portions 26 b of the respective rotating bodies 26, or are synchronously wound. It is paid out. For this reason, the pulling force acts on the spring member 25 when the second cable 34 is wound up in synchronization, and the tension releasing force acts on the spring member 25 when the second cable 34 is fed out in synchronization. That is, the spring member 25 is expanded and contracted, and a change in spring force that is increased or decreased at that time is input to the second cable 34. Then, the change in the spring force at that time acts on each mass body 17 via the rotating body 26 and the displacement amount extracting means 24,
By the addition of the spring member 25, the resonance frequency in which the first active dynamic vibration absorber 12 and the second active dynamic vibration absorber 13 are integrated can be increased, and it can be tuned to the torsional vibration having a high natural frequency. Of course, it goes without saying that the spring constant of the spring member 25 is set in advance so as to be synchronized with the natural frequency of the torsional vibration. Even in this case, the mass body 17 that is moved with the opposite phases of the two active dynamic vibration absorbers 12 and 13 controls the torsional vibration of the building 11 because the respective mass sums act on the torsional vibration. A sufficient mass to shake, that is, about 1% of the effective mass of the building 11 can be secured.

The first and second active dynamic vibration absorbers 1
When the torsional vibrations are controlled by the vibration sensors 2 and 13, the active mass control device 15 is operated based on the signal of the vibration sensor to control the movement of the additional mass 20 so that the torsional vibrations can be controlled precisely. 11 can be effectively removed.

Therefore, as described in (1), each of the mass bodies 17 of the first active dynamic vibration absorber 12 and the second active dynamic vibration absorber 13 has the spring force of the spring member 25 in the vibration damping device 10 of the present embodiment. By swinging in the same phase without any change, translational vibration in the short side direction (X) of the building 11 can be effectively damped,
As described in (2), the torsional vibration of the building 11 can be effectively damped by swinging each mass body 17 with the opposite phase while the spring force of the spring member 25 is acting.

In practice, in many cases, the translational vibration and the torsional vibration of the building 11 coexist due to the input vibration. However, the first active dynamic vibration absorber 12 and the second active dynamic vibration absorbing member have the vibration components of the respective vibration modes. Since the vessel 13 can be operated, even when the respective vibration modes coexist, each of them can be effectively damped. When the translational vibration and the torsional vibration coexist in this manner, each mass body 1
Even when the members 7 move in the same direction, there is a phase difference between them, so that the phase difference causes a change in the spring force of the spring member 25, so that both vibration modes of translational vibration and torsional vibration can be suppressed.

Further, since the pretension is added to the spring member 25, the second cable 34 is always in a tension state, and the responsiveness of a change in the spring force acting on the mass body 17 when damping the torsional vibration is improved. Thus, the vibration damping performance can be improved.

As described above, the two vibration modes of the translational vibration and the torsional vibration can be damped by the first and second two active dynamic vibration absorbers 12 and 13, respectively. The masses 17 of 12 and 13 are set to half of the mass required for damping each vibration mode, and the half mass 17 is operated in cooperation with the target mass, that is, about 1% of the effective mass of the building 11. Is to be secured. Therefore, the two active dynamic vibration absorbers 12,
Despite the provision of 13, the overall mass sum of those masses 17 is equivalent to the mass of one active dynamic vibration absorber conventionally provided, and the two active dynamic vibration absorbers 1
Weight reduction can be achieved when 2 and 13 are installed in the building 11. Therefore, even when the movement of the mass body 17 is restricted by the stopper or the brake when a large amplitude vibration such as a large earthquake is input, an increase in the load applied to the roof portion of the building 11 can be suppressed to a minimum. In addition, the swing amount of the building 11 can be suppressed from increasing.

In the present embodiment, the large diameter portion 26a for winding the first cable 28 and the small diameter portion 26b for winding the second cable 34 are provided around the rotating body 26. A leverage can be created between the portion 26b. Accordingly, the displacement amount and displacement force (tensile force) of the mass body 17 input to the first cable 28 are
Since the amount of displacement can be reduced and the displacement force (tensile force) can be increased and output to the second cable 34, the amount of deformation of the spring member 25 can be reduced, so that the size of the spring member 25 can be further reduced. In addition, this can sufficiently cope with a large swing stroke of the building 11 by appropriately setting the lever ratio (diameter ratio).

FIG. 6 shows another embodiment, in which the same components as those in the above embodiment are denoted by the same reference numerals, and a duplicate description will be omitted. That is, FIG. 6 is an enlarged plan view corresponding to FIG. 3, and in this embodiment, the building 11 is opposite to the above embodiment.
In this case, the natural frequency of the translational vibration generated in the above is higher than the natural frequency of the torsional vibration, and the natural frequencies of the first active dynamic vibration absorber 12 and the second active dynamic vibration absorber 13 in the inactive state are changed to the torsional vibration. In addition to the tuning, the spring force of the spring member 25 acts on the translational vibration when the mass body 17 moves.

Therefore, in this embodiment, the first cable 28 is wound around the displacement extracting means 24 having the displacement extracting frame 29 supported by the first, second, and third linear bearings 31, 25, and 26. A rotating body 26 having a large-diameter portion 26a and a small-diameter portion 26b around which the second cable 34 is wound;
The configuration in which the spring member 25 provided in the middle of the second cable 34 is provided is the same as that of the above-described embodiment.
The difference from the above embodiment is that the direction in which 8 is wound around the large diameter portion 26a is reversed between the first active dynamic vibration absorber 12 and the second active dynamic vibration absorber 13.

That is, in this embodiment, the first cable 28
When the masses 17 move in the same phase due to translational vibration, the opposite ends of the second cable 34 are connected to the small-diameter portions 26b of the rotating bodies 26 by reversing the winding directions around the large-diameter portions 26a. Winding or feeding out in synchronization, the spring force change of the spring member 25 acts on the mass body 17. On the other hand, when each mass body 17 moves with an opposite phase due to torsional vibration, one end of the second cable 34 is connected to one of the rotating bodies 2.
6 and at the same time, the other end is wound around the small diameter portion 26b of the other rotating body 26 so that the mass body 17 is not affected by the spring force.

Accordingly, the first and second two active dynamic vibration absorbers 12 and 13 tune and control the torsional vibration while the spring force of the spring member 25 does not act on the mass body 17. In a state where the spring force of the spring member 25 is acting, the vibration can be controlled in synchronization with the translational vibration.
Even in this case, the mass of each mass body 17 is reduced to half that of the conventional one, and the two active dynamic vibration absorbers 1 are used.
Since the total mass sum of the mass bodies 17 of the two and the thirteenth masses can be reduced, the same function as the above embodiment can be exhibited. Of course, even in this embodiment, the rotating body 2
By providing the large-diameter portion 26a and the small-diameter portion 26b in 6, a lever ratio can be generated between the first cable 28 and the second cable 34.

Also in this embodiment, the first and second
Active control device 1 for active dynamic vibration absorbers 12 and 13
By operating 5, the torsional vibration and the translational vibration can be precisely controlled, and the vibration of the building 11 can be effectively removed.

By the way, in each of the above embodiments, the displacement amount extracting means 24 includes the linear bearings 31, 25, 26
The displacement take-out frame 29 supported by the first member 28 is provided, and the movement thereof is taken out to the rotating body 26 through the first cable 28. However, the structure is not limited to the embodiment and the mass body 1
7 can be freely configured as long as the movement of 7 can be taken out.

FIGS. 7 and 8 show another embodiment, in which the same components as those in the above-described embodiment are denoted by the same reference numerals, and a duplicate description will be omitted. FIG. 7 is a plan view of a vibration damping device showing a state where an active dynamic vibration absorber is installed on an object to be damped, and FIG. 8 is a side view of an active dynamic vibration absorber installed on an object to be damped. The main difference from the embodiment is that another structure is used for the active control device 50.

That is, as shown in FIG. 8, the active control device 50 of this embodiment directly controls the swing of the mass body 17 of the first and second active dynamic vibration absorbers 12 and 13 by the ball screw 51. The ball screw 51 is driven by a driving source (not shown) built in a support frame 52 fixed to the rooftop floor 11a based on a detection signal of a vibration sensor. Therefore, even when the mass body 17 is directly controlled by the active control device 50 in this manner, the vibration of the building 11 can be precisely controlled. In this embodiment, the same function as that of the above embodiment is provided. Can play.

In the active control devices 15 and 50 of the above embodiments, the mass 17 is controlled by the ball screws 22 and 51. The means for controlling the mass 17 is For example, a hydraulic actuator or the like can be used in place of 51. Also, a pair of first and second active dynamic vibration absorbers 1 are provided.
Nos. 2 and 13 show the case where the active control device 15 of the additional mass inertia force type is provided on both sides, or the case where the active control device 50 of the floor reaction force type is provided on both sides.
It is also possible to use an additional mass inertial force type for one of the active dynamic vibration absorbers 12 and 13, and a floor reaction force type for the other.

Further, as a vibration damping object to which the vibration damping device 10 of the present invention is applied, the building 11 described in each of the above embodiments is used.
The present invention is not limited to this, and it is a matter of course that precision equipment and other equipment, devices, and articles that dislike vibration may be used.

[0049]

As described above, according to the vibration damping device of the present invention, a pair of active dynamic vibration absorbers provided on a vibration damping object in which the translational vibration mode and the torsional vibration mode are excited are combined with the natural frequency. Is tuned to the lower vibration mode, so that each active dynamic vibration absorber can control the vibration mode. In addition, for the vibration mode having a higher natural frequency, a pair of active dynamic vibration absorption is performed by a spring member that transmits a spring force between the mass bodies according to a displacement difference of the mass body extracted by using the displacement amount extraction means. Let the vessels work together,
This vibration mode can be damped. In any of the vibration modes, the vibration is damped by the cooperation of the pair of active dynamic vibration absorbers, so that the mass of the mass body of each active dynamic vibration absorber can be halved. Significant weight reduction can be achieved by halving the total mass of the mass body. Further, the active dynamic vibration absorber is provided with an active control device in the TMD, and the active control device operates the vibration mode precisely to effectively remove the vibration of the vibration damping object. Can be.

Further, the amount of displacement and the displacement force of the mass body can be changed between the mass body and the spring member by the booster means. By outputting the spring member, the amount of deformation of the spring member can be reduced to make the spring member more compact,
Further, it is possible to sufficiently cope with a large swing stroke of the vibration damping object.

[Brief description of the drawings]

FIG. 1 is a front view of an installed state of an active dynamic vibration absorber showing one embodiment of a vibration damping device of the present invention.

FIG. 2 is a plan view showing an installed state of an active dynamic vibration absorber showing one embodiment of the vibration damping device of the present invention.

FIG. 3 is a side view showing an installed state of an active dynamic vibration absorber showing one embodiment of the vibration damping device of the present invention.

FIG. 4 is an enlarged side view of a displacement amount extracting means provided in the active dynamic vibration absorber showing one embodiment of the vibration damping device of the present invention.

FIG. 5 is an enlarged plan view of a connected state of a pair of displacement amount extracting means showing one embodiment of the vibration damping device of the present invention.

FIG. 6 is an enlarged plan view of a connected state of a pair of displacement amount extracting means showing another embodiment of the vibration damping device of the present invention.

FIG. 7 is a plan view of a vibration damping device according to another embodiment of the present invention, showing a state in which an active dynamic vibration absorber is installed on an object to be damped.

FIG. 8 is a side view of an active dynamic vibration absorber installed on a vibration damping object, showing another embodiment of the vibration damping device of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Vibration suppression device 11 Building 12 1st active dynamic vibration absorber 13 2nd active dynamic vibration absorber 14 TMD 15, 50 Active control device 16 Elastic bearing 17 Mass body 24 Displacement extraction means 25 Spring member

Claims (2)

[Claims] 1. A hybrid type active dynamic vibration absorber comprising a TMD comprising a mass body, an elastic bearing member and a damping member, and an active control device for controlling the movement of the mass body of the TMD. Vibration mode 2
A vibration damping device for damping a vibration damping object in which two vibration modes are excited, wherein the vibration damping device is disposed at a distance from the vibration damping object, and includes a translational vibration mode and a torsional vibration mode. A pair of active dynamic vibration absorbers set in synchronization with the natural frequency of one of the vibration modes with the lower natural frequency of the object, and a pair of active vibration absorbers with the higher natural frequency of the vibration damping object Displacement amount extracting means for extracting the displacement of the mass body of each of the active dynamic vibration absorbers, and a pair of active dynamic vibration absorbers interposed between the mass bodies of the pair of active dynamic vibration absorbers. A spring member for transmitting a spring force according to the displacement difference extracted by the displacement amount extracting means between the mass bodies in order to tune to a natural frequency of a vibration mode having a higher natural frequency. And vibration control device. 2. The vibration damping device according to claim 1, wherein the displacement amount extracting means is provided with a booster for reducing the displacement of the mass body and transmitting the displacement to the spring member. .