JPH09264379A - Vibration damping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve various kinds of problems by oscillating a guide member having an arc-shaped guide surface which is projected downward in a sea-saw manner. SOLUTION: When a structure 17 is oscillated, a weight 22 starts the pendulum motion with the phase delay along an arc-shaped guide surface of a guide member 16 so that the structure 17 is damped by the effect of the inertia reaction and the gravity. To greatly improve the control performance, an active damping mechanism 21 such as a cylinder which is interposed between each end part of the guide member 16 and the structure 17 and expandable approximately in the vertical direction is expanded/contracted to oscillate the guide member 16 around a shaft 20 to pivotably support its center part, and the energy of the pendulum motion of the arc-shaped weight 22 is replenished to perform the effective damping with small energy to be charged.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration damping device.

[0002]

2. Description of the Related Art Vibration control devices have been developed to protect structures such as buildings and bridges from shaking such as earthquakes and wind forces.

The background of the development of the vibration damping device will be briefly described below.

In the initial stage, as shown in FIG. 7, a weight 2 having a natural period equal to or close to the natural period of the structure 1 is provided, and the weight 2 is provided on the structure 1. A vibration damping device having a structure in which the structure 1 and the weight 2 are arranged so as to be capable of reciprocating along a horizontal guide 3 extending in the direction of swaying, and a spring 4 such as a coil spring extending in the direction is connected between the structure 1 and the weight 2. Was considered.

In the above vibration control device, when the structure 1 shakes due to an earthquake or the like, the weight 2 tries to stay in place due to inertia, but the structure 1 and the weight 2 are connected by the spring 4. Because of the dynamic balance, the weight is 2 due to the dynamic balance.
Starts oscillating with a phase delay with respect to the structure 1. As a result, the inertial reaction force of the vibration of the weight 2 acts on the structure 1, the energy of the swing of the structure 1 is attenuated, and the structure 1 is damped.

However, in order to set the natural period of the weight 2 to be optimal with respect to the sway of the structure 1 due to an earthquake or wind force, a very long and soft spring 4 is required. I found it difficult to make,
As shown in FIG. 8, the frame 5 is assembled in the shape of a tower, the weight 2 is pendulum-type suspended from the top of the frame 5 by using the arm 6, and gravity 2 is used instead of the spring 4 so that the weight 2 performs a pendulum motion. It was examined that the energy of the swing of the structure 1 is attenuated by adopting such a structure.

However, even in such a case, in order to set the natural period of the weight 2 to be optimal with respect to the sway of the structure 1 caused by an earthquake or wind force, the arm 6 is set to 10 to 10.
Since it requires a length of 20 m, it is not practical.
As shown in FIG. 3, a downwardly convex arcuate weight 7 having a required radius of curvature is formed, and the lower surface of the arcuate weight 7 is supported by a roller 8 so that the arcuate weight is not used. 7 has been improved to be able to move the pendulum by itself, and has been downsized.

The vibration damping device using the arcuate weight 7 is
It was manufactured as an actual machine and was able to deliver good results. Further, due to the miniaturization, it can be mounted not only on a large structure 1 such as a building or a bridge but also on a relatively small structure 1 such as a crane or a ship.

In order to improve the performance of the vibration damping device using the arcuate weight 7, in an actual machine, an arcuate rack 9 is attached to the arcuate weight 7, and the rack 9 is not shown via the pinion 10. By connecting a motor and replenishing the energy by the motor, it is possible to effectively suppress vibrations with a light weight 7 and a small amount of input energy.

However, since the arcuate weight 7 is formed by a curved line, it is difficult to manufacture, and the axial center of the roller 8 or the pinion 10 is properly adjusted with respect to the arcuate weight 7 that performs the pendulum motion. There was a problem that the structure was complicated when it was placed in a position. In addition, when the arcuate rack 9 is attached to the arcuate weight 7, it is difficult to manufacture the arcuate rack 9 as an integral unit with high accuracy, and it is costly to make such a rack. However, in practice, many small piece-shaped racks 9 are made and connected together. However, in this case, the play between the rack 9 and the pinion 10 becomes large and control is performed. There is also a problem that the performance is lowered and noise is easily generated.

Therefore, the shape of the weight 7 which was arcuate is changed to V
By making the shape like a letter, improvements such as making the whole straight and facilitating the manufacture have been made, and it has reached the present. Or,
As shown in FIG. 10, a downwardly convex arcuate guide 11 having a required radius of curvature is created, and the arcuate guide 11 is formed.
A weight 12 having a natural period equal to or close to the natural period of the structure 1 is provided on the above, and the weight 12 is pendulum-moved along an arc-shaped guide 11.

Reference numeral 13 restricts the movable range of the weight 12 attached to both ends of the arc-shaped guide 11, and the weight 1
A buffer for buffering the collision force of 2 and a cable bear 14 for supplying electric power to a motor (not shown) attached to the weight 12.

As described above, the weight 12 is pendulum-moved on the arc-shaped guide 11 and the energy can be replenished by the motor.
It becomes possible to obtain the same function as that of FIG. 9 using the arcuate weight 7.

[0014]

However, the vibration damping device using the arc-shaped guide 11 has the following problems.

That is, in order to supply electric power for control to a motor (not shown) incorporated in the weight 12 for supplementing energy, a cable bear 14 or the like is required. This is not a problem because it is not operated very often when the vibration damping device is attached to a structure 1 such as a building or a bridge to suppress vibrations caused by an earthquake or wind. When the vibration control device is mounted on a ship or the like to suppress the vibration of the hull due to waves, the vibration control device is frequently activated because the waves are generated all the time. There is a problem that the cable carrier 14 is required to have high durability against repeated use.

Further, as in the case of FIG. 9, the arc-shaped rack 9 is used.
Since it is difficult to manufacture these as an integrated unit with high precision, there is a problem that the cost will be high if it is attempted to make such a product. Actually, a large number of small piece racks 9 are made and connected together. However, in such a case, there is a problem that rattling between the rack 9 and the pinion 10 becomes large, control performance is deteriorated, and noise is easily generated.

Further, when an excessive hull motion occurs due to a large wave, the weight 12 cuts off the control force of a motor (not shown) and collides with the buffer 13 in an attempt to go beyond the stroke end by the arc-shaped guide 11. Therefore, a large-scale buffer 13 must be provided in preparation for a collision, or the weight 1 is used to prevent a collision from occurring.
The arc-shaped guide 11 must be lengthened so that the stroke 2 can be sufficiently secured.

Further, since the hull leans when the hull turns, a weight (not shown) of a motor (not shown) incorporated in the weight 12 prevents the weight 12 from moving in the tilt direction of the hull by its own weight. Although the weight 12 is forcibly stopped at the neutral point by utilizing the control force, the motor is required to have a considerably higher torque than that required for damping.

In view of the above situation, it is an object of the present invention to provide a vibration damping device which can solve the above problems by making the inclination of the arc-shaped guide variable. .

[0020]

SUMMARY OF THE INVENTION According to the present invention, a guide member having a downwardly convex arcuate guide surface is attached to a structure so that the central portion of the guide member can swing in a seesaw manner, and the guide member is also provided. Between the end of the structure and the structure, a passive damping mechanism, which is composed of a spring and a damper connected in parallel and is capable of expanding and contracting in a substantially vertical direction, is interposed. Alternatively, the present invention relates to a vibration damping device characterized in that a weight having a close natural period is movably installed along an arcuate guide surface.

Further, according to the present invention, a guide member having a downwardly convex arcuate guide surface is attached to a structure so that the central portion of the guide member can swing in a seesaw manner, and an end portion of the guide member is provided. An active damping mechanism capable of extending and contracting in a substantially vertical direction is interposed between the structure and the guide member, and an arc-shaped guide having a weight having a natural period equal to or close to the natural period of the structure is attached to the guide member. The present invention relates to a vibration damping device characterized by being installed movably along a surface.

Further, according to the present invention, a guide member having a downwardly convex arcuate guide surface is attached to a structure so that the central portion of the guide member can swing in a seesaw manner, and an end portion of the guide member is provided. Between the structure and the structure, a passive damping mechanism that is elastically movable in the up-and-down direction by connecting a spring and a damper in parallel, and an active damping mechanism that can be driven to extend and retract in the up-and-down direction are installed at the same time. The present invention relates to a vibration damping device, wherein a weight having a natural period equal to or close to a natural period of a structure is installed on a guide member so as to be movable along an arcuate guide surface.

In this case, the guide member may have a natural period equal to or close to the natural period of the structure.

According to the above means, the following effects can be obtained.

When the structure shakes, the weight tries to stay in place due to inertia. However, since the weight is movably installed below the guide member along the convex arcuate guide surface, the dynamics Due to the physical balance, the weight starts the pendulum movement along the arc-shaped guide surface of the arc-shaped guide member with a phase delay with respect to the structure. As a result, gravity acts on the structure due to the inertial reaction force of the pendulum motion of the weight and the movement of the center of gravity, and the structure is damped.

Further, a passive vibration damping mechanism, which is interposed between both ends of the guide member and the structure due to the vibration of the structure, is composed of a spring and a damper connected in parallel and is capable of expanding and contracting in a substantially vertical direction. Is driven to expand and contract, the guide member is oscillated in a seesaw manner around the center portion thereof, and the oscillation of the weight is amplified, so that the vibration is effectively suppressed.

Alternatively, an active damping mechanism such as a cylinder, which is interposed between both ends of the guide member and the structure and is capable of expanding and contracting in a substantially vertical direction, is driven to expand and contract to move the guide member to the central part. It swings like a seesaw as the center,
By replenishing energy, it is possible to effectively suppress vibration with a small amount of input energy.

Alternatively, the vibration damping can be performed more effectively by the synergistic action of the passive vibration damping mechanism and the active vibration damping mechanism.

As described above, according to the present invention, the weight is pendulum-moved along the guide surface having a downwardly convex arcuate shape of the guide member, so that a simple and compact structure can be achieved effectively. Vibration can be suppressed.

Moreover, in order to replenish the energy, the guide member side is oscillated in a seesaw type by a passive vibration damping mechanism or an active vibration damping mechanism.
Since it is not necessary to attach a cable bear or the like to the weight, the durability problem of the cable bear or the like against repeated use is solved. A pipe system is required for the active vibration damping mechanism or the like instead of the cable bear, but since the active vibration damping mechanism hardly swings to the left or right, the durability problem with repeated use hardly occurs.

In order to replenish the energy, the guide member side is oscillated in a seesaw type by a passive vibration damping mechanism or an active vibration damping mechanism, so that it is not necessary to attach an arcuate rack to the guide member. ,
Problems of manufacturing an arcuate rack and noise caused by rattling with a pinion due to manufacturing error are solved.

Further, when the active vibration damping mechanism is used, even if the structure is excessively shaken, the weight of the guide member is increased by temporarily increasing the inclination of the guide member accordingly. It becomes possible to easily prevent the weight from going over the end, or to suppress the force that the weight tries to pass over the stroke end of the guide member, eliminating the need to provide a large buffer in case of a weight collision. It is possible to do so with a small buffer. Alternatively, it is not necessary to elongate the guide member so as to secure a sufficient stroke of the weight in order to make the collision less likely to occur, and sufficient controllability can be secured even with a short guide member.

Further, in the case where the structure is a ship, when the hull is turned, the guide member is held horizontally by the active vibration damping mechanism, so that the weight can easily and freely move in the direction of inclination of the hull. You can prevent it from moving.

As described above, the vibration damping device suitable for application to a ship can be obtained.

In addition, since the guide member is oscillated in a seesaw manner to replenish the energy, it is possible to control the pendulum motion of the weight only by slightly expanding and contracting the active vibration damping mechanism. Next to
The control amount can be significantly reduced compared to the case where the pendulum movement of the weight along the arcuate rack is directly controlled.
This makes it possible to reduce the capacity of the active vibration damping mechanism and improve the control response.

Further, since the guide member is swung to control it, if the guide member has a proper natural period, in addition to the damping effect of the weight, the damping effect of the guide member can be obtained. .

[0037]

Embodiments of the present invention will be described below with reference to the drawings.

FIGS. 1 and 2 show a first embodiment of the present invention, which will be described as applied to a ship.

As shown in FIG. 1, a guide member 16 having a guide surface 15 in the shape of a convex arc downward of the required radius of curvature.
(Hereinafter, referred to as an arc-shaped guide member 16) is provided, and the arc-shaped guide member 16 is arranged in the left-right direction 18 (direction in which shaking occurs) of a structure 17 such as a ship (hereinafter referred to as a ship 17), The center portion of the arc-shaped guide member 16 in the left-right direction 18 is attached to the upper end portion of the support column 19 attached to the ship 17.
A seesaw type swingably pivots left and right around a shaft 20 extending in the front-rear direction of the ship 17.

A spring 45, such as an air spring or a coil spring, and a damper 46, such as an oil damper, are connected in parallel between at least one end of the arc-shaped guide member 16 and the ship 17, and are arranged in a substantially vertical direction. One or both of the passive vibration damping mechanism 47 that can freely expand and contract, and the active vibration damping mechanism 21 such as a cylinder that can be expanded and contracted substantially vertically can be interposed.

The arc-shaped guide member 16 is used for the structure 17
A natural period equal to or close to the natural period of

A weight 22 having a natural period equal to or close to the natural period of the structure 17 is movable on the arc-shaped guide member 16 along the arc-shaped guide surface 15 of the arc-shaped guide member 16. To install.

Reference numeral 23 is a buffer for restricting the movable range of the weight 22 attached to both ends of the arc-shaped guide member 16 and buffering the collision force of the weight 22.

As shown in FIG. 2, a sway sensor such as an angular velocity meter 24 is attached to the ship 17, and a displacement sensor 2 is attached to each of the active vibration damping mechanism 21 such as a cylinder and the weight 22.
With an operation detection sensor such as 5, 41, the angular velocity meter 2
4, the angular velocity signal 26 from 4, the angular displacement signal 28 obtained by integrating the angular velocity signal 26 by the integrator 27, the displacement signals 29 and 42 from the displacement gauges 25 and 41, and the velocity signal 31 obtained by differentiating them from the differentiators 30 and 43. 44, and based on these and the previously determined control gain, the calculation unit 35 performs a predetermined calculation,
An arithmetic and control unit 34 for sending a control signal 33 to a control system 32 such as a hydraulic servo system of the active vibration damping mechanism 21 is provided.

Next, the operation will be described.

When the ship 17 is shaken by the waves, the weight 22
Tries to stay in place due to inertia, but the weight 22
Is movably installed along the arc-shaped guide surface 15 of the arc-shaped guide member 16, so that the weight 22 has a phase lag with respect to the vessel 17 due to the dynamic balance, and thus the weight 22 has a circle. The pendulum movement along the arc-shaped guide surface 15 is started. As a result, the inertial reaction force of the pendulum motion of the weight 22 and the gravity due to the movement of the center of gravity of the weight 22 act on the ship 17, and the ship 17 is shaken.

Further, due to the shaking of the hull, a spring 45 such as an air spring or a coil spring and a damper 46 such as an oil damper, which are interposed between both ends of the arc-shaped guide member 16 and the ship 17, are connected in parallel. By expanding and contracting the passive damping mechanism 47, which is substantially vertically movable by
The arcuate guide member 16 is moved up and down around the shaft 20 pivotally supporting the central portion of the guide member 16, and the swinging of the weight 22 to the left and right is amplified, so that the swinging is performed more effectively.

Alternatively, the active vibration damping mechanism 21 such as a cylinder, which is interposed between the both ends of the arc-shaped guide member 16 and the ship 17 and is capable of expanding and contracting substantially vertically, is expanded and contracted to replenish the energy. The arc-shaped guide member 16
Is moved up and down around the shaft 20 that pivotally supports the central portion thereof, and the weight 22 is swung left and right, so that the swing can be performed more effectively with less input energy.

Alternatively, the passive damping mechanism 47 and the active damping mechanism 21 are synergistically adapted to further effectively reduce the vibration.

When the active vibration control mechanism 21 is operated, as shown in FIG. 2, the angular velocity meter 2 attached to the ship 17 is used.
A vibration sensor such as No. 4 detects the vibration of the ship 17 and generates an angular velocity signal 26, and at the same time, the active vibration control mechanism 21 and the operation detection sensors such as the displacement gauges 25 and 41 attached to the weight 22 act as the active vibration control mechanism 21. Expansion and contraction amount and weight 22
The position signals of the positions are detected to generate displacement signals 29 and 42, the angular velocity signal 26 and the displacement signals 29 and 42 are input to the arithmetic and control unit 34, and the angular velocity signal 26 is integrated by the integrator 27 in the arithmetic and control unit 34. And the angular displacement signal 28 is obtained, the displacement signals 29 and 42 are differentiated by the differentiators 30 and 43 to obtain velocity signals 31 and 44, and these are calculated in advance and the control gain obtained in advance. A predetermined calculation is performed in the unit 35, a control signal 33 is obtained, the control signal 33 is sent to a control system 32 such as a hydraulic servo system of the active vibration damping mechanism 21, and the active vibration damping mechanism 21 is controlled.

As described above, according to the present embodiment, the weight 22 is pendulum-moved along the guide surface 15 of the arcuate guide member 16, so that the weight 22 is effectively controlled with a simple and compact structure. It can be shaken.

Moreover, since the side of the arc-shaped guide member 16 is swung to the left and right by the passive damping mechanism 47 and the active damping mechanism 21 in order to replenish the energy, the weight 22 is shown in FIG. It is not necessary to attach a special cable bear 14 or the like, and the problem of durability of the cable bear or the like against repeated use is solved.
A pipe system is required for the active vibration control mechanism 21 and the like instead of the cable bear, but since the active vibration control mechanism 21 hardly swings to the left or right, the durability problem with repeated use hardly occurs.

In order to replenish the energy, the side of the arc-shaped guide member 16 is swung left and right by the passive vibration damping mechanism 47 and the active vibration damping mechanism 21. It is no longer necessary to mount the arc-shaped rack 9 as shown in FIG. 1, and the problems of manufacturing the arc-shaped rack and the problems of control performance deterioration and noise due to rattling with the pinion due to manufacturing error are solved. To be done.

In addition, when the active vibration damping mechanism 21 is used, even if an excessive hull motion occurs due to a large wave, the inclination of the arc-shaped guide member 16 is temporarily increased in response to this, whereby the weight is reduced. It is possible to easily prevent 22 from exceeding the stroke end of the arc-shaped guide member 16, or alternatively, the weight 22 is arranged so that the weight 22 is in the arc-shaped guide member 16.
It becomes possible to suppress the force of going over the stroke end of the above, and it is possible to eliminate the need to provide a large buffer 23 in preparation for a collision of the weight 22, and it is possible to use a small buffer 23. . Or,
It is not necessary to elongate the arc-shaped guide member 16 so that the stroke of the weight 22 is sufficiently secured in order to make the collision less likely to occur, and sufficient control performance can be secured even with the short arc-shaped guide member 16.

Further, according to the active vibration damping mechanism 21,
Even when the hull turns, by tilting the arc-shaped guide member 16 to the side opposite to the tilt of the hull, the weight 22 does not easily move in the direction of the hull tilt by its own weight. You can

As described above, a vibration damping device suitable for application to the ship 17 can be obtained.

In addition, since the arcuate guide member 16 is swung to the left and right in order to replenish the energy, the pendulum motion of the weight 22 is controlled only by slightly expanding and contracting the active vibration damping mechanism 21. This makes it possible to significantly reduce the control amount as compared with the case where the pendulum movement of the weight 22 along the arcuate rack 9 is directly controlled as shown in FIG. This makes it possible to reduce the capacity of the active vibration control mechanism 21 and improve the control response.

Further, since the arcuate guide member 16 is swung to control it, if the arcuate guide member 16 has a natural period equal to or close to the natural period of the structure 17, the weight 22 is used. In addition to the vibration damping effect, the vibration damping effect of the arc-shaped guide member 16 can be obtained.

If a linear guide member is used instead of the arc-shaped guide member 16, the spring 22 as shown in FIG. 7 should be attached to the weight 22 (however, since such a spring is difficult to manufacture). It is the same as the case of FIG. 7 that has almost no possibility of realization), or the active vibration damping mechanism
It is not possible to cause the weight 22 to vibrate and to exert the vibration damping effect unless the linear guide member is positively driven by expanding and contracting. Therefore, even if the guide member is not rocked, it is essential to use the arc-shaped guide member 16 so that the weight 12 naturally starts the pendulum motion due to the rocking and the vibration damping effect is exhibited.

FIG. 3 shows a second embodiment of the present invention. In order to swing the arc-shaped guide member 16, instead of using a cylinder, an electric motor 37 having a ball screw 36 on its drive shaft is shown. The active vibration damping mechanism 40 is composed of a nut 39 pivotally supported by the arc-shaped guide member 16 via a pin 38 parallel to the shaft 20.

According to the present embodiment, when the electric motor 37 is driven, the ball screw 36 rotates and the screwing position of the ball screw 36 and the nut 39 is changed, so that the arc-shaped guide member 16 is swung. It can be moved.

Except for the above, it has the same configuration as that of the above-described embodiment, and the same operation and effect can be obtained.

4 and 5 show a third embodiment of the present invention, in which the damping mechanism 4 is provided between the guide member 16 and the weight 22.
8 is provided.

As the damping mechanism 48, for example, as shown in FIGS. 4 and 5, a guide wall 49 made of a conductor such as copper or aluminum is provided on the guide surface 15 side, and a guide wall is provided on the weight 22 side. A magnetic damper structure is provided in which both side surfaces of 49 are provided with an attenuating body 50 made of a permanent magnet having a small gap and sandwiched by different magnetic poles.

In the damping mechanism 48, when the weight 22 moves, an eddy current is generated in the guide wall 49 by the action of the magnetic field of the permanent magnet, and the eddy current and the magnetic field of the permanent magnet cause the eddy current to move in the opposite direction. Force is generated and damping is performed.

A frictional force normally acts between the guide member 16 and the weight 22, but the surface of the guide surface 15 of the guide member 16 is roughened so that the frictional force becomes large. It is also possible to use a damping mechanism (friction damper) equivalent to the damping mechanism 48 of the magnetic damper structure.

Except for the above, the configuration is the same as that of each of the above-described embodiments, and the same operation / effect can be obtained.

[0068]

EXAMPLE FIG. 6 is a graph summarizing the results of an experiment investigating the effect of the present invention, in which the vertical axis represents the actuator power and the horizontal axis represents the forced frequency ratio (= wave frequency / ship natural vibration). Number).

In the experiment, a ship having a drainage of about 2 tons and a natural period of about 2 seconds was used as the structure 17, and the weight was 40 k.
The device of the present invention (line a) in which the active damping mechanism 21 and the passive damping mechanism 47 are used together by using the weight 22 of g.
And the device (line B) in FIG. 9 were compared.

According to FIG. 6, it was actually confirmed that the present invention can significantly reduce the actuator power of the active vibration damping mechanism 21.

The present invention is not limited to the above-described embodiment, but is not limited to the ship 17, and may be attached to a building, a bridge, a crane or other structures, for convenience of drawings and description. The weight 22 has a dolly shape and is moved along the arcuate guide surface 15 formed on the upper surface of the arcuate guide member 16, but the present invention is not limited to such a structure, and a pair of circles is used. Arc-shaped guide member 1
6, the guide surfaces 15 in the shape of arc grooves facing each other are formed on the inner surface of 6, and the weight 22 is fitted with the guide surfaces 15 in the shape of arc grooves so that sliding projections are projected.
It goes without saying that the structure can be any structure and that various changes can be made without departing from the scope of the invention.

[0072]

As described above, according to the vibration damping device of the present invention, the following excellent effects can be obtained.

(1) Since the guide member side is made to oscillate in a seesaw manner by a passive vibration damping mechanism or an active vibration damping mechanism in order to supplement energy, it is not necessary to attach a cable bear or the like to the weight. Durability problems such as cable bears for repeated use are solved.

(2) Since the guide member side is oscillated in a seesaw manner by the active vibration damping mechanism in order to replenish the energy, it is not necessary to attach an arcuate rack to the guide member, and the arcuate rack is eliminated. Problems of manufacturing the rack, deterioration of control performance and noise due to rattling with the pinion due to manufacturing error are solved.

(3) When an active vibration damping mechanism is provided,
Even when the structure is excessively shaken, the inclination of the guide member is temporarily increased in response to this, thereby easily preventing the weight from exceeding the stroke end of the guide member, or It is possible to suppress the force that the weight tries to pass over the stroke end of the guide member, it is possible to eliminate the need to provide a large buffer in preparation for a collision of the weight, and it is possible to use a small buffer. Become. Alternatively, it is not necessary to elongate the guide member so as to secure a sufficient stroke of the weight in order to make the collision less likely to occur, and sufficient control performance can be secured even with a short guide member.

(4) When the structure is a ship, the hull inclines when the hull turns. Therefore, by holding the guide member horizontally using an active vibration control mechanism, the weight can be easily adjusted by its own weight. Therefore, it is possible to prevent the hull from moving in the direction of inclination.

(5) Since the guide member is oscillated in a seesaw manner to replenish the energy,
It is possible to control the pendulum motion of the weight by only slightly expanding and contracting the active vibration control mechanism, and the control amount is greatly reduced compared to the case where the pendulum motion of the weight along the arc-shaped rack is directly controlled. be able to. This makes it possible to reduce the capacity of the active vibration damping mechanism and improve the control response.

(6) Since the guide member is oscillated in a seesaw manner to control it, if the guide member has a natural period equal to or close to the natural period of the structure, the damping effect by the weight will be obtained. In addition, the damping effect of the guide member is also obtained.

[Brief description of drawings]

FIG. 1 is an overall schematic side view of a first embodiment of the present invention.

FIG. 2 is a control system diagram of FIG.

FIG. 3 is a partially enlarged side view of the second embodiment of the present invention.

FIG. 4 is an overall schematic side view of a third embodiment of the present invention.

FIG. 5 is a view taken in the direction of arrows VV in FIG. 4;

FIG. 6 is a graph showing the relationship between actuator power and forced frequency ratio, which summarizes the results of experiments conducted to investigate the effects of the present invention.

FIG. 7 is an overall schematic side view of a spring-type vibration damping device that was initially considered.

FIG. 8 is an overall schematic side view of a pendulum type vibration damping device.

FIG. 9 is an overall schematic side view of a conventional vibration damping device using an arcuate weight.

FIG. 10 is an overall schematic side view of a conventional vibration damping device using an arc-shaped guide.

[Explanation of symbols]

 15 Guide Surface 16 Guide Member 17 Structure 21, 40 Active Vibration Control Mechanism 22 Weight 45 Spring 46 Damper 47 Passive Vibration Control Mechanism

Continuation of the front page (72) Inventor Katsuo Mutaguchi 3-15-1, Toyosu, Koto-ku, Tokyo Ishikawajima Harima Heavy Industries Co., Ltd. Toni Technical Center

Claims (4)

[Claims] 1. A guide member having a downwardly convex arc-shaped guide surface is attached to a structure such that the central portion thereof can swing in a seesaw manner, and the end portion of the guide member and the structure are In between, a passive damping mechanism, which is composed of a spring and a damper connected in parallel and is capable of expanding and contracting almost vertically, is interposed.
A vibration damping device, wherein a weight having a natural period equal to or close to a natural period of a structure is movably installed on a guide member along an arc-shaped guide surface. 2. A guide member having a downwardly convex arc-shaped guide surface is attached to a structure such that the central portion thereof can swing in a seesaw manner, and the end portion of the guide member and the structure. In between, an active damping mechanism capable of expanding and contracting in a substantially vertical direction is interposed, and a weight having a natural period equal to or close to the natural period of the structure is attached to the guide member along the arc-shaped guide surface. A vibration damping device that is installed so that it can move freely. 3. A guide member having a downwardly convex arc-shaped guide surface is attached to a structure such that the central portion thereof can swing in a seesaw manner, and the end portion of the guide member and the structure. In the meantime, a passive vibration damping mechanism that is capable of expanding and contracting in a substantially vertical direction, which is formed by connecting a spring and a damper in parallel, and an active vibration suppressing mechanism that is capable of expanding and contracting in a substantially vertical direction are installed at the same time. A vibration damping device, wherein a weight having a natural period equal to or close to a natural period of a structure is movably installed along an arc-shaped guide surface. 4. The vibration damping device according to claim 1, wherein the guide member has a natural period equal to or close to the natural period of the structure.