JPH09235910A - Damper of building - Google Patents

Abstract

PROBLEM TO BE SOLVED: To miniaturize and simplify a by dividing damping hydraulic cylinders provided to every floor into a plurality of blocks to control, and controlling the blocks uniformly based on signals from an earthquake sensor to damp great and small earthquakes. SOLUTION: Hydraulic cylinders 7 in every floor are controlled by control sections 13 equipped with main pipe lines 14, branch pipe lines 15, servo valves 16, controllers 17, etc., block by block to make it correspond to both great and small vibrations. Based on output from an earthquake sensor consisting of an acceleration sensor or a displacement sensor, operations of a state of vibration are performed by an operation device 18, and the controllers 17 are operated with the value to be obtained. In the case of small vibration caused by wind or small earthquake, oil pressure to the hydraulic cylinders 7 is controlled, and the hydraulic cylinders 7 are operated as actuators to damp actively the vibration. In the case of a great earthquake, the servo valves (selector valves and throttle valves) 16 are operated to use the cylinders 7 as a damper. By the constitution, the damper can be miniaturized at a low cost.

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 for a building, and more particularly to a vibration damping device for improving rolling comfort and safety by reducing rolling of a high-rise building due to wind or an earthquake. It is a thing.

[0002]

2. Description of the Related Art A conventional vibration damping device of this type is as follows.

(1) Tuned mass damper (TMD),
Active mass damper (AMD) As shown in FIG. 10, a reciprocatingly movable weight b is provided on or near the top floor of the building a, and the movement of the weight b is intended to suppress the vibration of the building a. . As in the illustrated example, the spring b and the damper d are added to the weight b to move the weight b exclusively and passively in accordance with the shaking of the building a. The TMD is active, and the weight b is positively active by the actuator. The thing that moves to is AMD.

(2) Bearing of laminated rubber This is to support the entire building a on a foundation d from the bottom by a laminated rubber e which is elastically deformable, as shown in FIG.

(3) Inter-level damper or actuator As shown in FIG. 12, each level of the building a (between slabs) is connected by a damper f, and the lateral relative movement between the levels is attenuated to reduce the building. a) The vibration is suppressed as a whole. An elasto-plastic damper, a friction damper, an oil damper or the like is used as this damper. In this case, the damper receives an external force and absorbs the energy, so that the damper becomes a passive damper. On the other hand, if an actuator is used instead of the damper and a reaction force is applied to the energy, an active damper that actively suppresses vibration is obtained.

[0006]

However, such a conventional device has the following drawbacks.

(1) TMD and AMD The main purpose of these is to reduce swaying due to wind and improve habitability, and it is possible to cope with small earthquakes that generate swaying to the same extent as wind, but We cannot respond to earthquakes due to lack of capacity. Also, if it is attempted to cope with this, the device becomes large-scale and it is not economically feasible. Therefore, it cannot be expected to improve safety against earthquakes.

(2) Bearing of laminated rubber This is often used for the floor of a room with important equipment, but when bearing the whole building, it is not suitable for high-rise or large-scale ones, and it is a soft ground. Also has no effect. Furthermore, because the building will be floating above the ground,
The usage range is naturally limited because the wiring and piping for electricity, water, gas, etc. are also required to be flexible.

(3) Damper or actuator between layers First, in the case of a passive damper, the relative displacement between layers is as small as a few mm or less when there is a small shake due to wind or the like, and there is some play in the damper. In this case, the damping effect cannot be expected and the habitability cannot be improved. Therefore, the conventional products are mainly intended to improve safety in the event of a medium-sized earthquake. Moreover, since the characteristics of the conventional product are mechanically determined, it is difficult to give desired characteristics arbitrarily.

On the other hand, an active damper using an actuator is effective for small swings and can improve habitability, but like AMD, cannot cope with large swings and cannot improve safety.

As described above, it is difficult for the conventional vibration control device to control both small vibrations caused by wind and small earthquakes and large vibrations caused by medium and large earthquakes. It was difficult to achieve both.

[0012]

A vibration damping device for a building according to the present invention controls a fluid pressure cylinder for connecting between floors of a building and a fluid pressure control for the fluid pressure cylinder when the shaking of the building is small. Cylinder control means for appropriately narrowing and communicating the fluid chambers of the fluid pressure cylinders when the building shakes significantly.

In this structure, the cylinder control means is
When the sway of the building is small, fluid pressure control to the fluid pressure cylinder is performed to actively dampen the sway of the building. On the other hand, when the vibration is large, the fluid chambers of the fluid pressure cylinder are appropriately squeezed to communicate with each other, and the fluid pressure cylinder is made to function as a passive damper. In particular, at this time, the diaphragm amount is changed according to the shake to generate the optimum damping force according to the shake.

[0014]

Preferred embodiments of the present invention will be described below in detail with reference to the accompanying drawings.

FIG. 1 is a block diagram showing a vibration damping device according to the present invention. As shown in the drawing, a building 1 as a vibration damping target has a steel structure having a frame 4 composed of columns 2 and beams 3. It is a 7-story building. Brace 5 fixed to each beam 3 hangs down in a V shape, but the lower end of brace 5 is not connected to beam 3 below. The beams 3 partition the layers (floors) of the building 1. For example, in the uppermost 7th floor, the upper side (ceiling side) is partitioned by the beams 3a, and the lower side (floor side) is partitioned by the beams 3b.

The vibration damping device 6 has a hydraulic cylinder 7 (fluid pressure cylinder) that connects the lower end of the brace 5 and the lower beam 3 to each other. Here, one hydraulic cylinder 7 is provided in each layer, but a plurality of hydraulic cylinders 7 may be provided separately. The hydraulic cylinder 7 is simply composed of a piston 8 and a cylinder 9. The cylinder 9 is densely filled with working oil (working fluid), and the oil chambers 10a and 10b (fluid chamber) with the piston 8 as a boundary are formed. It is compartmentalized. The hydraulic cylinder 7 is arranged horizontally, with its piston 8 connected to the brace 5 and the cylinder 9 to the beam 3. As a result, the hydraulic cylinder 7 connects the layers of the building 1 and attenuates the horizontal relative movement of the upper and lower beams 3 caused by the shaking of the building 1.

Further, the vibration damping device 6 is composed of these hydraulic cylinders 7.
Cylinder control means 11 is provided for controlling the above according to the shaking of the building as described later. The cylinder control means 11 is
The hydraulic pressure (fluid pressure) from the hydraulic pressure source 12 (fluid pressure source) is supplied to each hydraulic cylinder 7 via the hydraulic pressure control unit 13. The hydraulic pressure source 12 discharges the hydraulic oil stored in the oil tank from one port P by a hydraulic pump and returns it from the other port T.

Here, the hydraulic cylinders 7 provided in each layer
Among them, the continuous ones on the 1st to 4th floors and the continuous ones on the 5th to 7th floors are set as one set, and the one set is controlled to be the same. That is, one hydraulic control unit 13 is provided for each set, and in each hydraulic control unit 13, a pair of main pipes 14, 14 is provided with a branch pipe communicating with the oil chambers 10a, 10b of the hydraulic cylinders 7. The paths 15, 15 are respectively connected. Therefore, the piston 8 of the hydraulic cylinder 7
If there is a hydraulic pressure difference between the main pipes 14, 14, they will move in the same direction based on this.

The main lines 14, 14 extend from the hydraulic source 12, in which a servo valve 16 is provided in front of the branch lines 15, 15 in a four-way valve connection. This servo valve 1
6, which will be described in detail later, is controlled by the controller 17 to switch between the main conduits 14 and 14 and adjust the internal throttle. In other words, the servo valve 16 has both functions of a switching valve and a throttle valve.
The controller 17 electrically operates the servo valve 16 based on the output value from the arithmetic unit 18. Arithmetic unit 18
Calculates the output to the controller 17 based on the output from the sensor 19 installed on the rooftop floor of the building 1. The sensor 19 is an acceleration sensor or a displacement sensor, and by converting the acceleration or displacement signal into a velocity signal, the arithmetic unit 18 can know the representative velocity of the building 1 and the shaking state of the building 1 from this. When the sensor 19 is a speed sensor, the representative speed of the building 1 can be directly known.

A pressure sensor 20 is provided in each of the main pipes 14, 14 between the servo valve 16 and the branch pipe 15, and the pressure value detected by these is output to the controller 17. Then, the controller 17 reads the generated force of the hydraulic cylinder 7 from the pressure difference, compares it with the control target value from the arithmetic unit 18, and feedback-controls the hydraulic cylinder 7.

On the other hand, a first stop valve 22 is provided in a portion between the servo valves 16 and the hydraulic power source 12 of the main pipelines 14, 14, respectively, and the first stop valve 22 and the servo valve 1 are provided.
The portions between 6 are communicated with each other by a communication conduit 23, and the communication conduit 23 is provided with a second stop valve 24. The first and second stop valves 22 and 24 are simply opened or closed by the controller 17.

In the figure, the portion surrounded by the alternate long and short dash line constitutes the hydraulic pressure control section 13, that is, the hydraulic pressure control section 13 includes the main pipeline 14,
14, the branch lines 15 and 15, the servo valve 16, the first and second stop valves 22 and 24, the communication line 23, the controller 17, and the pressure sensor 20. And 2
A sensor 19 and an arithmetic unit 18 are provided for the two hydraulic control units 13.
And the hydraulic power source 12 are common. Other than the hydraulic cylinder 7 including all of them, the cylinder control means 11 is configured.

Next, the operation of such a device will be described.

First, the sensor 19 outputs a signal such as acceleration according to the shaking of the building 1. In response to this, the arithmetic unit 18 calculates a velocity value based on the acceleration value and the like,
The shaking speed of the building 1 or the relative speed between floors is determined.
Then, the target value of the generated force of the hydraulic cylinder 7 is calculated according to this speed and is output to the controller 17. The controller 17 compares this target value with the value of the actual generated force of the hydraulic cylinder 7 based on the detection value of the pressure sensor 20,
In order to eliminate these deviations, the servo valve 16 and the first and second stop valves 22 and 24 are controlled as follows.

When it is determined from the output from the sensor 19 that the shaking of the building 1 is small, that is, when the target value calculated by the calculation device 18 is relatively small and there is only a small deviation from the actual generated force. , As shown in FIG. 2 (a), the first
The stop valve 22 is opened and the second stop valve 24 is closed so that the servo valve 16 and the hydraulic source 12 are connected to each other.
Is the oil pressure from the oil pressure source 12 and the oil chambers 1 of the hydraulic cylinder 7.
0a and 10b are appropriately supplied. For example, in the upper part of the figure, the hydraulic pressure or hydraulic oil from the hydraulic pressure source 12 is the servo valve 16
Port P, and push the piston 8 of the hydraulic cylinder 7 to move between C ₂ on the left side of. Further, when it is desired to push the piston 8 to the opposite side, the ports P and C ₁
The servo valve 16 is switched so that the two communicate with each other. By such switching, the direction of the generated force of the hydraulic cylinder 7 is
The direction can be appropriately changed to a direction suitable for damping the building 1, more specifically, a direction opposite to the direction of shaking.

At this time, the port P of the servo valve 16
Since the two communication passages connecting T and the ports C ₁ and C ₂ have the variable throttle 21 whose opening is proportional to the magnitude of the input signal, the throttle amount of this throttle 21 should be optimally adjusted or controlled. Thus, in addition to the above direction control, the operating speed of the hydraulic cylinder 7 can be optimally controlled.

In this way, when the building 1 shakes a little due to wind or a small earthquake, the cylinder control means 11 controls the hydraulic cylinder 7 hydraulically so that the hydraulic cylinder 7 acts as an actuator to activate the shaking of the building 1. Decays to.

Next, the building 1 is controlled by the output from the sensor 19.
When it is determined that the vibration of the hydraulic pressure is large, the first stop valve 22 is closed and the second stop valve 24 is opened to cut off the hydraulic pressure supply from the hydraulic power source 12, as shown in FIG. 2B. Then, the hydraulic pressure sent from the hydraulic cylinder 7 passes through the servo valve 16 as it is, and reciprocates between the oil chambers 10a and 10b of the hydraulic cylinder 7 through the communication pipe line 23.
At this time, the port P of the servo valve 16 communicates with C ₂ and the port T communicates with C ₁ (or vice versa), and the servo valve 1
The switching control of 6 is not performed, and the servo valve 16 functions only as a throttle valve. According to this, the hydraulic cylinder 7 can now freely move according to the shaking of the building 1. However, since this operation oil passes through the throttle 21 of the servo valve 16, this operation is surely restricted or limited by the flow path resistance generated at that time. Thus, when the shake of the building 1 is large, the hydraulic cylinder 7 acts as a damper to passively dampen the shake of the building 1. At this time as well, the throttle amount of the throttle 21 is controlled in the same manner as described above, and the generated force (damping force) of the hydraulic cylinder 7 is optimally controlled.

The advantages of this device are as follows. First, since the hydraulic cylinder 7 is used as an actuator only when the shake of the building 1 is small, and is not used as an actuator when the shake is large, the hydraulic source 12 is particularly small so that the operation of the hydraulic cylinder 7 can be controlled only when the shake is small. The scale can be made small, and the small one can surely damp the shaking. Also, when the building 1 shakes significantly, the hydraulic cylinder 7 is used as a damper,
Since the hydraulic pressure source 12 is not used, a large amount of energy can be surely absorbed even if the hydraulic pressure source 12 is small. As described above, even if the hydraulic power source 12 is small, both small vibrations due to wind and small earthquakes and large vibrations due to medium and large earthquakes can be damped, thereby improving comfortability and safety. It becomes possible to achieve both.

Especially when used as a passive damper,
Since the damping force can be arbitrarily changed by controlling the diaphragm 21, the characteristic is greatly improved even in that case, and the vibration damping capability can be improved.

In this device, since a plurality of hydraulic cylinders 7 are controlled in the same manner, the device can be greatly simplified and the cost can be reduced.

This is due to the following points. That is, conventionally, the actuators (hydraulic cylinders) of each layer
However, in actuality, the vibration mode of the building is usually from the 1st to the 2nd order, and there are blocks where the displacement and direction of the relative movement are the same between consecutive or adjacent floors. Within the block, the control eventually became the same, resulting in an excess of equipment.

In view of this, in the present device, the excess of such devices is prevented, the building is divided into a plurality of blocks or each of a plurality of layers, and the individual hydraulic cylinders are controlled to be the same in each block. I try to get the performance of a simple device.

In the same manner, a plurality of hydraulic cylinders 7 may be provided in one layer and the hydraulic cylinders 7 may be controlled in the same manner to obtain the same effect.

Further, since the servo valve 16 different from the hydraulic cylinder 7 has the throttle 21, it is not necessary to provide the hydraulic cylinder 7 with a throttle, a check valve, an air chamber, etc. like a normal oil damper, and it is simple. There is also an advantage that an inexpensive structure can be used.

Next, another embodiment will be described. It should be noted that the same configurations are denoted by the same reference numerals in the drawings and description thereof will be omitted.

As shown in FIG. 3, the configuration of the hydraulic control unit 13 is different in this embodiment. That is, the first and second
The stop valves 22 and 24 and the communication conduit 23 are not provided,
A portion of the main pipelines 14, 14 between the pressure sensor 20 and the servo valve 16 is communicated with each other by a communication pipeline 25, and the communication pipeline 25 is provided with a second servo valve 26. Unlike the servo valve 16, the second servo valve 26 has a two-way valve connection. Similarly, the aperture control is performed by the controller 17 as well.

When the building shakes slightly due to wind or small earthquake,
In the above-mentioned form, complete active damping was performed,
In the case of this embodiment, while passive damping is basically used, active damping is supplemented only when necessary. That is, in the case of active vibration control, power is required, and if it is always active in order to cope with normal shaking, the power cost will be high, but in the present embodiment, it is always passive to greatly reduce the power cost. .

Specifically, it is as follows. First, when the building shakes, as shown in FIG. 4A, the throttle 2 of the second servo valve 26 is controlled so that the hydraulic pressure required for the hydraulic cylinder 7 is generated.
7 is controlled. At this time, the other servo valve 16 has a throttle 2
1 is fully closed and hydraulic pressure is not supplied. Here, if the generated force of the hydraulic cylinder 7 is insufficient, the opening degree of the throttle 27 is reduced, but if the hydraulic pressure is still insufficient even when the throttle 27 is completely closed, as shown in FIG. The opening of the throttle 21 of the other servo valve 16 is adjusted to supply the hydraulic pressure from the hydraulic pressure source 12 so as to compensate for the insufficient hydraulic pressure. That is, when the hydraulic pressure is not insufficient due to the passive damping, the servo valve 16 is closed and only the servo valve 26 is open. Conversely, the servo valve 16
When is open, the servo valve 26 is closed. Such switching between the two valves can be easily performed from a signal inside the controller 17. That is, an opening command of the servo valve 26 is generated inside the controller 17, but when this command value becomes a negative value, a command signal of zero opening is sent to the servo valve 26, and at the same time the opening is proportional to the command value. Thus, the opening command signal is sent to the servo valve 16. On the contrary, while the opening command value for the servo valve 26 made inside the controller 17 is a positive value, the servo valve 26 opens according to the command, but a command of zero opening is sent to the servo valve 16.

In this way, when the shaking of the building is small, the necessary hydraulic pressure is not generated even if the servo valve 26 is throttled due to backlash of the mounting of the hydraulic cylinder 7 or the like, so the servo valve 16 operates naturally. Active control. On the other hand, when the shaking of the building is large, the influence of rattling is relatively small, so passive control is performed. The servo valve 16 is intermittently opened to perform active control only when the passive control causes a slight shortage, but at this time, a large amount of power is not consumed because only the shortage is compensated.

FIGS. 5 and 6 are graphs showing the state of control in the present embodiment. FIG. 5 shows the state in the case of complete passive control, and FIG. 6 shows the case where active control is supplementarily performed with the configuration of FIG. The situation is shown.

In the graph, time t is plotted on the horizontal axis.
(A) shows the shaking of the building by amplitude, and from L _{1 of} FIG.
L _{2 of} is a large value. In (b), the upper stage shows the opening degree of the throttle 27 of the second servo valve 26, and the lower stage shows the switching direction of the servo valve 16 and the opening degree of the throttle 21. The MAX at the center indicates the maximum opening, and especially in the lower row, swaying from the MAX toward the plus (+) side will cause shaking toward the minus (-) direction of the building, and squeezing to the minus (-) side will cause the building plus (+). The sway toward each direction will be attenuated. However, in the case of the upper stage, since only the opening control of the throttle 27 of the second servo valve 26 is performed, the operation is performed only on the plus (+) side. (C) shows the generated force of the hydraulic cylinder 7 that substantially damps the sway of the building. The sway of the building in the positive (+) direction is the force on the negative (-) side, and the sway in the negative (-) direction. Vibration is damped by the force on the plus (+) side. (D) is the pressure sensor 20
Oil chambers 10a, 10b of the hydraulic cylinder 7 based on the detected value of
The pressure deviation between the two is shown.

In FIG. 5B, since it is assumed that only passive control is performed, only the opening control of the second servo valve 26 is executed and the servo valve 16 is not operated. Also the second
The opening of the servo valve 26 is appropriately adjusted according to the amplitude of the building. The shaking of the building is gradually attenuated in the early stage when the amplitude is large, but when the amplitude becomes small, even if the opening is reduced to zero, the necessary hydraulic pressure is generated due to the looseness of the mounting of the hydraulic cylinder 7. It does not decay easily. On the other hand, it can be seen from FIG. 6B that, in addition to the opening control of the second servo valve 26, the switching control of the servo valve 16 and the throttle control are simultaneously performed. For this reason, compared with FIG. 6A, the vibrations are damped faster especially in the range where the amplitude is small. As described above, the servo valve 16 is the second servo valve 26.
It is operated only when the generated force is insufficient even when the opening of is zero. In this way, the servo valve 16 is operated intermittently, so that the power can be greatly reduced.

Next, the structure of the hydraulic control unit 13 is different even in the further embodiment shown in FIG. This is because the first and second servo valves 22 and 24, the second servo valve 26, and the like in the above-described embodiment are omitted, and only the servo valve 16 is provided. In this case, in this state, only active vibration suppression control corresponding to a small shake is possible, that is, only switching control and throttle control of the servo valve 16 as shown in FIG. 8 are performed.

However, as shown in FIG. 9, if the connection of the conduit to the servo valve 16 is changed, it can be used exclusively for the pasig which covers from small shaking to large shaking. In this case, the hydraulic pressure source 12 is not connected to the servo valve 16, and the respective main pipe lines 14, 14 are connected to the P and C ₂ ports. The T and C ₁ ports are closed with blind plugs. Then, the P and C ₂ ports are communicated with each other via the diaphragm 21, and the switching control is not performed but only the diaphragm control is performed. In this case, only the passive control in which the diaphragm amount is variable is performed, but since the damping force can be optimally adjusted even in this case, it is effective in improving the characteristics. In this way, depending on the purpose of use, the situation of use, etc., it is possible to selectively use active and passive only by changing the connection of the conduit.

Although the preferred embodiments of the present invention have been described above, the present invention is not limited to these embodiments and various embodiments are possible. For example, instead of the servo valve 16, a switching valve and a throttle valve may be separately provided, and fluid pressure other than hydraulic pressure may be used. Further, the controller 17 may include the arithmetic unit 18. The number of sensors 19 and hydraulic cylinders 7 and the installation method can be arbitrarily changed.

[0047]

The present invention exhibits the following excellent effects.

(1) Vibration control of large and small shaking of a building can be realized by a small-scale facility, which makes it possible to achieve both comfort and safety.

(2) By controlling a plurality of fluid pressure cylinders in the same manner, it is possible to greatly simplify the apparatus and reduce the cost.

[Brief description of drawings]

FIG. 1 is a configuration diagram showing an embodiment of a vibration damping device according to the present invention.

FIG. 2 shows a hydraulic pressure transmission path around a servo valve, (a)
Shows the case where the shaking of the building is small, and (b) shows the case where it is large.

FIG. 3 is a partial configuration diagram showing another mode of the vibration damping device according to the present invention.

FIG. 4 shows a hydraulic pressure transmission path around the servo valve in the configuration of FIG. 3, where (a) is a case where the building shake is small, (b)
Is a big case.

FIG. 5 is a graph showing how control is performed in the form of FIG. 3, in the case of a small small shake.

FIG. 6 is a graph showing how control is performed in the form of FIG. 3, in the case of a large small shake.

FIG. 7 is a partial configuration diagram showing still another form of a vibration damping device according to the present invention.

8 shows a hydraulic pressure transmission path around the servo valve in the configuration of FIG.

FIG. 9 is a partial configuration diagram showing an example of changing the connection of a pipeline to a servo valve.

FIG. 10 is a schematic diagram showing a conventional vibration damping device, which shows a TMD (A
MD).

FIG. 11 is a schematic view showing a conventional vibration damping device, showing a laminated rubber bearing.

FIG. 12 is a schematic diagram showing a conventional vibration damping device, showing a damper (actuator) between layers.

[Explanation of symbols]

 1 Building 6 Vibration Control Device 7 Hydraulic Cylinder (Fluid Pressure Cylinder) 10a, 10b Oil Chamber (Fluid Chamber) 11 Cylinder Control Means 12 Hydraulic Source (Fluid Pressure Source) 16 Servo Valve (Switching Valve and Throttle Valve) 17 Controller

Claims (4)

[Claims] 1. A fluid pressure cylinder for connecting between floors of a building, and a fluid pressure control for the fluid pressure cylinder when the vibration of the building is small, and a fluid pressure control of the fluid pressure cylinder when the vibration of the building is large. A vibration damping device for a building, comprising: a cylinder control means for communicating by appropriately narrowing fluid chambers. 2. The cylinder control means outputs a predetermined signal according to the shaking of the building, and the fluid pressure cylinder and the fluid pressure source or the fluid pressure based on the output signal from the controller. 2. The vibration damping device for a building according to claim 1, comprising a switching valve that is switched so as to connect the fluid chambers of the cylinders to each other, and a throttle valve that appropriately throttles the communication passages. 3. The vibration damping device for a building according to claim 1, wherein the fluid pressure cylinders are provided between a plurality of consecutive floors of the building, and the cylinder control means controls the fluid pressure cylinders in the same manner. 4. A vibration damping system for a building according to claim 1, wherein a plurality of the fluid pressure cylinders are provided in one floor of the building, and the cylinder control means controls the fluid pressure cylinders in the same manner. apparatus.