JP2659588B2 - Passive / active switching type vibration damping device - Google Patents

Description

The present invention is applied to a structure such as a high-rise building, a bridge, a steel tower, a chimney, and the like, and a vibration generated in the structure due to a disturbance such as wind applied to the structure. The present invention relates to a vibration damping device for reducing the vibration.

2. Description of the Related Art It is well known that there are two types of vibration control devices of this type, a passive type and an active type. That is, the features of these formats are briefly described as follows.

1) Passive type In this type, as represented by a conventional dynamic vibration absorber, a passive damping element is attached to a structure, and the damping element absorbs vibration energy of the structure, thereby reducing vibration. It is intended.

2) Active type In this type, vibration damping energy is supplied to the structure from the outside to actively reduce the vibration of the structure.

However, each of these formats has the following problems.

1) Passive type a. There is friction in the supporting part of the additional mass, etc., and the additional mass does not vibrate due to a small disturbance, and therefore has no vibration suppression effect. B. Even if the additional mass vibrates due to a large disturbance, The damping effect is limited.

2) Active type a. In the case of a building damping device, the additional mass is several tens tons to several hundreds.
t, and the displacement must be about ± 1 m.b.When all displacements are actively performed by the hydraulic system, the hydraulic system becomes very large and impractical.c. Capacity of the hydraulic system Is insufficient, the displacement of the added mass is suppressed during a large disturbance, and the effect is lower than that of the passive type.
(Several tens of kilograms to several tons) d.

Therefore, an object of the present invention is to solve the problems in these two types and to obtain a vibration damping device capable of switching between these two types. .

Means for Solving the Problems A passive-active switching type vibration damping device according to the present invention is a passive type vibration damping mechanism including an additional mass, a spring, a damping device, and the like. In a passive / active switching type vibration damping device in which a servo mechanism (C) is combined and controlled to a passive type or an active type via the electric / hydraulic servo mechanism (C), the passive type vibration damping mechanism comprises: Structure to be shaken (B)
Base frame (2) adapted to be installed on
An intermediate frame (4) mounted on the base frame (2) so as to be movable in the X-axis direction; and an additional mass mount mounted on the intermediate frame (4) so as to be movable in the Y-axis direction. (11) and an X-direction spring (6) installed between each of the frames (2, 4) or the additional mass base (11);
It has an X-direction damping device (7), an X-direction hydraulic cylinder (8), a Y-direction spring (13), a Y-direction damping device (14), and a Y-direction hydraulic cylinder (15). A passive / active switching type vibration damping device, wherein a cylinder (8) and a Y-direction hydraulic cylinder (15) are controlled via the electric / hydraulic servo mechanism (C). More specifically, an input signal representing the speed of the structure (B), the speed and displacement of the additional mass (M) is processed by a control device (Ra) of a passive / active switching control mechanism (R), The hydraulic oil is supplied or bypassed from a hydraulic source to each of the hydraulic cylinders (8, 15) via at least a servo valve (31) and an electromagnetically operated valve (32) controlled by an output signal of the control device (Ra). This is the configuration.

EXAMPLES Hereinafter, the present invention will be described with reference to FIGS.
This will be described in detail with reference to the drawings.

First, FIG. 1 schematically shows the overall arrangement of the present invention. As shown in FIG. 1, on a ground G, for example, a structure B to be damped is installed. Yes, structure B
A linear motion mechanism L that moves linearly in one direction is provided on the floor, and an additional mass M is placed on the linear motion mechanism L. The structure B and the additional mass M In order to resonate the additional mass M with the structure B when the structure B is disturbed, a spring S and an oil damper, a viscous damper or the like as a damping device D are arranged in parallel. And
In the structure B, a linear motion mechanism L is fixedly arranged with a hydraulic cylinder O in the moving direction. In addition to connecting the piston P to an additional mass M, the hydraulic cylinder O is connected to a passive type and an active type. And an electric / hydraulic servo system C for switching to the operation of. Further, in order to control the electric / hydraulic servo mechanism C, a passive / active switching control mechanism R is provided, and the mechanism R has an input corresponding to the speed of the structure B and the speed and displacement of the additional mass M. Sensor amplifier R1 to receive the electrical signal as a signal, differentiator R2,
A / D for converting this analog signal to digital signal
A converter R3, a control device Ra (computer) for processing a signal from here on, a D / A converter R4 for converting a digital signal from this to an analog signal, a servo for comparing the analog signal with a displacement signal of the additional mass M A signal from the servo amplifier R5 is sent to the hydraulic cylinder O, and the signal is switched between a passive type and an active type.

In the above description, the linear motion mechanism L moves in only one direction in the horizontal direction as viewed in FIG. 1, but in an actual apparatus, the linear motion mechanism L is placed on the linear motion mechanism L. Another linear motion mechanism that is movable in a direction perpendicular to the screen shown in the figure is provided, and the additional mass M is mounted on the linear motion mechanism. Each device corresponding to the spring S, the damping device D, and the hydraulic cylinder O arranged between the movement mechanism L and the structure B is arranged.

That is, FIGS. 2, 3 and 4 show one embodiment of the vibration damping device according to the present invention having two kinds of linear motion mechanisms in such two perpendicular directions (X and Y directions). I have.

As shown in the figure, a base is provided on a floor 1 of a rectangular box having a rectangular outline having sides in the X and Y directions on a floor 1 of a structure to be damped. The frame 2 is installed, and several X-direction rails 3 are installed horizontally on the upper surface symmetrically with respect to the center X-X of the base frame 2 in the X-direction. Similarly, a hollow box-shaped intermediate frame 4 having a rectangular contour and a certain height is fixed to the upper surface of the base frame 2 via several X-direction bearings 5 fixed to the lower surface thereof. Is placed so as to be freely movable in the X direction over a certain space.

In the space between the upper surface of the base frame 2 and the lower surface of the intermediate frame 4, a center 0 of the base frame 2 is provided between appropriate fixed brackets.
Symmetrically, four sets of X-direction springs 6 are installed in a stress-free state in parallel to the center line XX of the base frame 2, and similarly, the X-direction springs of the base frame 2 An X-direction oil damper 7 as a set of X-direction damping devices is installed in parallel with the X-direction spring 6 near the opposing side walls. Further, between the base frame 2 and the intermediate frame 4, a pair of X-direction hydraulic cylinders 8 are provided outside each of the X-direction oil dampers 7, respectively, in parallel with each other.
Is installed. In addition, on the lower surface of the intermediate frame 4,
Four X-direction stoppers 9 are fixed in the X-direction symmetrically with respect to the center 0 thereof, and these X-direction stoppers 9 cooperate with stopper members installed corresponding to the base frame 2. And the base frame 2 and the intermediate frame 4
, The relative movement in the X direction is suppressed.

Further, on the upper surface of the intermediate frame 4, a total of three Y-direction rails 10 are provided in the Y direction, one through the center 0 and one each symmetrically with respect to the center 0. Each Y-direction rail 10 has a hollow box-shaped bottom having a rectangular outline in a plane with a certain space between the Y-direction rail 10 and the upper surface of the intermediate frame 4. An additional mass mount 11 for mounting the additional mass is movably mounted in the Y direction via several sets of Y-direction bearings 12 fixed to the lower surface of the bottom thereof.

In the space between the upper surface of the intermediate frame 4 and the additional mass mount 11, four sets of Y-direction springs 13 are provided with respect to the center 0 of the intermediate frame 4 via brackets attached to the respective spaces. In addition to the symmetrically installed Y-direction oil dampers 14 as a set of Y-direction damping devices and the outside thereof, the symmetrically installed Y-direction damping devices are provided near the Y-direction opposing side walls of the intermediate frame 4. A pair of Y-direction hydraulic cylinders 15 are installed in parallel with each other. Also,
On the upper surface of the intermediate frame 4, a pair of Y-direction stoppers 16 at each corner are installed in the Y-direction, and these Y-direction stoppers 16 cooperate with stopper members installed corresponding to the additional mass mount 11. Then, relative movement in the Y direction between the intermediate frame 4 and the additional mass mount 11 is suppressed.

Note that a predetermined weight of additional mass
17 is placed.

In this manner, the vibration damping device according to the present invention installs the base frame 2 on the structure floor 1, and on the X-direction rail 3 installed on the upper surface thereof, in the X-direction via the X-direction bearing 5. The intermediate frame 4 is movably mounted, and an additional mass mount 11 is movably mounted in the Y direction on a Y-direction rail 10 installed on the upper surface of the intermediate frame 4 via a Y-direction bearing 12. , A predetermined weight of additional mass on the additional mass
Since the additional mass 17 is placed, the additional mass 17 can be freely moved in the X direction and the Y direction with respect to the structure floor 1, and when moving in each direction, X A stress is applied to the directional spring 6 and the Y-directional spring 13 to vibrate the intermediate frame 4 or the additional mass base 11, and the vibration is caused by the X-directional oil damper 7 or the Y-directional oil damper.
To be attenuated by 14.

Further, with these vibrations in the X and Y directions, X
Direction hydraulic cylinder 8 or Y direction hydraulic cylinder 15
A relative vibration is applied to each piston. In this case, these hydraulic cylinders 8, 15 can be switched between an active type and a passive type by the electric / hydraulic servo system C (see FIG. 1).

That is, FIGS. 5 and 6 show a state where the hydraulic circuits are switched so that the hydraulic cylinders 8, 15 are operated as an active type and a passive type, respectively.

This hydraulic circuit mainly includes a servo valve 31 for supplying and discharging the hydraulic pressure of a hydraulic power source and an electromagnetically operated valve 32. The supply of hydraulic pressure to the hydraulic cylinders 8 and 15 via these valves 31 and 32 is performed. When the valves 31 and 32 are switched, the passive / active switching control mechanism R receives the detected speed of the structure B and the speed and displacement of the additional mass 17 as input signals. , These signals to its controller
After processing by Ra, the output signal is given to the servo valve 31 and the electromagnetically operated valve 32 of the electric / hydraulic servo mechanism C, and the hydraulic cylinders 8 and 15 are controlled through the electric / hydraulic servo mechanism C. is there.

Here, hydraulic circuits to the hydraulic cylinders 8 and 15 at the time of each switching are shown in FIGS. 5 and 6, respectively.

1) When active (Fig. 5) At this time, the hydraulic pressure is supplied from the hydraulic pressure source via the servo valve 31.
A → C flows into the hydraulic cylinders 8 and 15, and D → E flows to the hydraulic source. Therefore, the vibration damping device operates as an active type.

2) At the time of passive operation (FIG. 6) At this time, the hydraulic pressure from the hydraulic pressure source is shut off by the servo valve 31, and both cylinder chambers of the hydraulic cylinders 8 and 15 are switched to D → F → E → C bypass circuit, the hydraulic cylinders 8 and 15 can move freely without suppressing the movement of the additional mass 17, and the vibration damping device operates as a passive type Becomes

EXPERIMENTAL EXAMPLE The device of the present invention has the above-described configuration, and includes an electric / hydraulic servo mechanism capable of switching between an active type and a passive type, FIG. 7 shows a result of one calculation performed by installing this device on a certain structure, which has a configuration in which the cylinders 8 and 15 are combined.

In the figure, the horizontal axis represents time (s), and the vertical axis represents acceleration (m / s ² ).
Is a diagram showing each of them, and FIG.
FIG. 4B shows the vibration characteristics of the structure when no vibration damping device is installed, and FIG. 6B shows the vibration characteristics when the vibration damping device is switched between a passive type and an active type. c) shows the vibration state of the structure when a vibration device having the vibration characteristics shown in FIG. 2B is installed on the structure having the vibration characteristics shown in FIG. It is.

In FIG. 4B, when the acceleration is equal to or higher than the specified value and the passive control is switched to the active control, the rated current is exceeded (the hydraulic capacity is exceeded), and when the active control is switched to the passive control, the acceleration is increased. When the acceleration is less than the specified value and the control is switched from the active control to the passive control.

By comparing (a) and (c) in the same figure, the effect of the vibration damping device according to the present invention can be changed to a passive type and an active type, thereby exhibiting an excellent vibration damping effect. It is clear that

Effects of the Invention Since the device of the present invention has the above-described configuration and operation, it can exhibit the following effects.
It is clear.

A vibration damping device with an additional mass of several tens to several hundred tons can be realized with a relatively small capacity hydraulic system.In the case of a small disturbance, it can be operated as an active type. In the case of a large disturbance, it switches to the passive type.
Inexpensive running costs In the event of a power outage, the system automatically switches to the passive type, which ensures the performance of the passive type.

[Brief description of the drawings]

1 is a schematic diagram showing the overall arrangement of the device of the present invention, FIG. 2 is a plan view showing one embodiment of the device of the present invention, FIG. 3 is a cross-sectional view taken along the line III-III of FIG. Fig. 4 shows IV-
FIGS. 5 and 6 are cross-sectional views taken along the line IV. FIGS. 5 and 6 are schematic diagrams showing examples of hydraulic circuits for switching the hydraulic cylinder between an active type and a passive type, respectively. It is a diagram showing an example of an apparatus. DESCRIPTION OF SYMBOLS 1 ... Structure floor, 2 ... Base frame, 3 ... X-direction rail, 4 ... Intermediate frame, 5 ... X-direction bearing, 6 ...
... X direction spring, 7 ... X direction oil damper, 8 ... X direction hydraulic cylinder, 9 ... X direction stopper, 10 ... Y direction rail, 11 ... Additional mass mount, 12 ... Y direction bearing, 13 …
... Y-direction spring, 14 ... Y-direction oil damper, 15 ... Y-direction hydraulic cylinder, 16 ... Y-direction stopper, 17 ... Additional mass, B ... Structure, C ... Electro-hydraulic servo mechanism, D …
... Damping device, G ... Ground, O ... Hydraulic cylinder, L ...
Linear motion mechanism, M ... additional mass, P ... piston, R ...
... Passive / active switching control mechanism.

 ──────────────────────────────────────────────────続 き Continued on the front page (72) Inventor Hiroshi Miyano 1-9-131 Shinonome, Koto-ku, Tokyo Mitsubishi Steel Corporation Tokyo Works (72) Inventor Takashi Fujita 575-28 Nakano Hisagi, Naganoyama-shi, Chiba (56 ) References JP-A-2-190579 (JP, A)

Claims (2)

(57) [Claims] An electric / hydraulic servo mechanism (C) capable of switching between a passive type and an active type is combined with a passive type vibration damping mechanism composed of an additional mass, a spring, a damping device and the like. In a passive / active switching type vibration damping device which is controlled to a passive type or an active type via a mechanism (C), the passive type vibration damping mechanism is installed on a structure (B) to be damped. A base frame (2) adapted to
An intermediate frame (4) mounted movably in the X-axis direction on the base frame (2); and an additional mass mount (11) mounted movably in the Y-axis direction on the intermediate frame (4). ) And an X-direction spring (6) installed between each of the frames (2, 4) or the additional mass mount (11);
It has an X-direction damping device (7), an X-direction hydraulic cylinder (8), a Y-direction spring (13), a Y-direction damping device (14), and a Y-direction hydraulic cylinder (15). A passive / active switching type vibration damping device, wherein a cylinder (8) and a Y-direction hydraulic cylinder (15) are controlled via the electric / hydraulic servo mechanism (C). 2. The speed and the added mass (M) of said structure (B)
An input signal representing the speed and displacement of the motor is processed by a control device (Ra) of a passive / active switching control mechanism (R), and at least a servo valve (31) controlled by an output signal of the control device (Ra) includes an electromagnetic operation device. The passive / active switching type vibration damping device according to claim 1, wherein a pressure oil is supplied to or bypassed from each of the hydraulic cylinders (8, 15) from a hydraulic source via a valve (32).