JP6815688B2 - Vibration suppression device for structures - Google Patents

Description

The present invention relates to a structure vibration suppressing device provided between a first part and a second part in a system including a structure and for suppressing the vibration of the structure, particularly of a semi-active type or an active type. The present invention relates to a vibration suppression device for a structure provided with a fluid damper.

Conventionally, as a vibration suppression device for this type of structure, for example, one disclosed in Patent Document 1 is known. This conventional vibration suppression device includes a semi-active fluid damper, a controller, and a sensor. This fluid damper is provided in the cylinder so as to be slidable in the axial direction in the cylinder, a piston that divides the inside of the cylinder into a pair of hydraulic chambers, oil filled in the pair of hydraulic chambers, and a pair of hydraulic chambers. It has a pair of inflow oil passages and outflow oil passages that communicate with each other, and passive circuits and semi-active circuits connected in parallel to these inflow oil passages and outflow oil passages. The above passive circuit is provided with a relief valve and an orifice that open when the oil pressure reaches a predetermined pressure, and the semi-active circuit is provided with an electric opening / closing control valve. Further, the position of the piston in the cylinder is detected by the above sensor, and the opening / closing operation of the opening / closing control valve is controlled by the above controller based on the detected position of the piston.

In the conventional vibration suppression device having the above configuration, when the applied structure vibrates slightly due to an earthquake or the like, the controller opens the open / close control valve and controls the opening, thereby using the piston. The pressed oil is made to flow between a pair of hydraulic chambers via a semi-active circuit so as to obtain a damping force having a desired damping coefficient. Further, when the structure vibrates greatly, the controller closes the open / close control valve, whereby the oil pressed by the piston is made to flow between the pair of hydraulic chambers via the passive circuit. The damping force with a larger damping coefficient is obtained. As described above, the fail-safe function of the semi-active circuit is not required by obtaining the damping force of the fluid damper by using the passive circuit that does not require power supply at the time of large vibration of the structure.

Japanese Unexamined Patent Publication No. 2004-125803

As described above, in the conventional vibration suppression device, a passive circuit and a semi-active circuit are connected in parallel to each other in a pair of hydraulic chambers of a cylinder via an inflow oil passage and an outflow oil passage. For this reason, the configuration of the vibration suppression device including these hydraulic circuits is very complicated, which increases the manufacturing cost thereof.

The present invention has been made to solve the above problems, and obtains a desired damping force when the vibration of the structure is relatively small, and a larger damping force when the vibration of the structure is relatively large. It is an object of the present invention to provide a vibration suppression device for a structure capable of reducing the manufacturing cost.

In order to achieve the above object, the invention according to claim 1 is provided between a first part and a second part in a system including a structure, and vibration of the structure for suppressing vibration of the structure. A restraining device, a cylinder connected to one of the first and second parts and a cylinder connected to the other of the first and second parts, slidably provided in the cylinder in the axial direction, and inside the cylinder. It is divided into a first fluid chamber and a second fluid chamber, and includes a piston located at a predetermined neutral position in the cylinder when the structure is not vibrating, and the internal space of the cylinder has a neutral position of the piston. When the viscous fluid, which is divided into a predetermined inner section including and a predetermined outer section adjacent to both outer sides of the inner section and is filled in the first and second fluid chambers, and the piston are located in the inner section. By bypassing the piston, it communicates with the first and second fluid chambers, allowing viscous fluid to flow between the first and second fluid chambers, and when the piston is located in the outer section, the piston. To convert the mechanical energy of the electric motor into the kinetic energy of the viscous fluid in the first communication passage, which is provided in the first communication passage and the first communication passage and is powered by the electric motor. Accordingly, the flow rate adjusting mechanism having a pump for adjusting the flow amount of the viscous fluid flowing between the first communication passage and the first and second fluid chamber to the active, adjust the flow amount of the viscous fluid by the flow rate adjustment mechanism In the second passage and the second passage for flowing the viscous fluid between the first fluid chamber and the second fluid chamber, which communicate with the first and second fluid chambers, and the control means for controlling the above. A first pressure regulating valve provided, which closes the second passage when the pressure of the viscous fluid in the first fluid chamber is smaller than the first predetermined value, and opens the second passage when the pressure reaches the first predetermined value. When the pressure of the viscous fluid in the second fluid chamber is smaller than the second predetermined value, the second passage is closed, and when the pressure reaches the second predetermined value, the second passage is closed. a second pressure regulating valve for opening and further comprising a when the piston is located outside the section, and characterized that you function as a passive damper by the first pressure regulating valve and the second control valve is opened To do.

According to this configuration, the cylinder is connected to one of the first and second parts in the system containing the structure, and the piston is connected to the other of the first and second parts. The piston is slidably provided in the cylinder in the axial direction, and the inside of the cylinder is divided into a first fluid chamber and a second fluid chamber, and when the structure is not vibrating, a predetermined neutral position in the cylinder is provided. Is located in. The internal space of the cylinder is divided into a predetermined inner section including the neutral position of the piston and a predetermined outer section adjacent to both outer sides of the inner section. Further, the first and second fluid chambers are filled with viscous fluid, and when the piston is located in a predetermined inner section including the neutral position, between the first fluid chamber and the second fluid chamber. The first communication path for flowing the viscous fluid bypasses the piston and communicates with the first and second fluid chambers.

Further, the first passage is provided with a flow rate adjusting mechanism having a pump for actively adjusting the flow rate of the viscous fluid flowing between the first passage and the first and second fluid chambers . This pump uses an electric motor as a power source and converts the mechanical energy of the electric motor into the kinetic energy of the viscous fluid in the first communication passage, and the adjustment of the flow amount of the viscous fluid by the flow rate adjusting mechanism is a control means. Controlled by. Further, the second communication passage for flowing the viscous fluid between the first fluid chamber and the second fluid chamber communicates with the first and second fluid chambers, and the first and second communication passages have the first and second communication passages. A second pressure regulating valve is provided. By this first pressure regulating valve, the second passage is closed when the pressure of the viscous fluid in the first fluid chamber is smaller than the first predetermined value, and the second passage is opened when the pressure reaches the first predetermined value. To. Further, the second pressure regulating valve closes the second passage when the pressure of the viscous fluid in the second fluid chamber is smaller than the second predetermined value, and the second passage when the pressure reaches the second predetermined value. Is released.

From the above, the relative displacement between the first portion and the second portion generated by the vibration of the structure is transmitted to the cylinder and the piston, whereby the piston slides in the cylinder. When the vibration of the structure is relatively small and thus the piston is sliding in the inner section, as the viscous fluid flows between the first and second fluid chambers and the first communication passage, A vibration damping force corresponding to the difference between the pressure of the viscous fluid in the first fluid chamber and the pressure of the viscous fluid in the second fluid chamber acts on the first and second portions. In this case, the difference between the pressure of the viscous fluid in the first fluid chamber and the pressure of the viscous fluid in the second fluid chamber changes according to the amount of flow of the viscous fluid flowing through the first communication passage. Therefore, when the vibration of the structure is relatively small, the flow rate of the viscous fluid flowing between the first passage and the first and second fluid chambers is activated by the control means via a flow rate adjusting mechanism having a pump. The desired damping force can be obtained by adjusting and controlling the vibration damping force.

Further, when the vibration of the structure is relatively large and the piston slides in the outer section, the first communication passage does not communicate with the first and second fluid chambers, and the viscous fluid becomes the first and first fluid chambers. 2 There is no flow between the fluid chamber and the first communication passage. In this case, when the pressure of the viscous fluid in the first fluid chamber pressed by the piston reaches the first predetermined value, the second communication passage is opened by the first pressure regulating valve, and the viscous fluid becomes the first and second fluids. It flows between the chamber and the second passage, and with the flow, the piston exerts a damping force while moving in the outer section to absorb energy . Further, when the pressure of the viscous fluid in the second fluid chamber pressed by the piston reaches the second predetermined value, the second communication passage is opened by the second pressure regulating valve, and the viscous fluid is released into the first and second fluid chambers. It flows between the and the second passage, and along with the flow, the piston exerts a damping force while moving in the outer section to absorb energy . As described above, when the vibration of the structure is relatively large, it functions as a passive damper, and a larger damping force can be obtained.

Further, as described above, unlike the conventional vibration suppression device described above, the semi-active circuit and the passive circuit are separated from each other without using a complicated hydraulic circuit in which the inflow oil passage and the outflow oil passage are connected in parallel. Since a simpler configuration including the first and second communication passages provided in the above is used, the manufacturing cost of the vibration suppression device can be reduced. Further, even when an abnormality occurs in the flow rate adjusting mechanism having a pump and / or the control means, the viscous fluid can be appropriately flowed between the first and second fluid chambers by the second continuous passage, and also. Since the effect of the abnormality is limited to when the piston is moving in the inner section, it is possible to prevent the vibration damping force of the vibration suppression device from becoming excessive or too small due to the abnormality, and the structure due to the abnormality can be prevented. Damage can be prevented.

In the present specification and claims, the "vibration damping force" is a force that suppresses vibration of a structure, and includes a damping force, a control force, and the like.

The invention according to claim 2 is characterized in that, in the vibration suppression device for the structure according to claim 1, the second communication passage is composed of a plurality of communication holes penetrating in the axial direction of the piston.

According to this configuration, since a plurality of communication holes penetrating in the axial direction of the piston are used as the second communication passage, it can be configured more easily than when a communication passage of the type that bypasses the piston is used. , The manufacturing cost of the vibration suppression device can be further reduced.

The invention according to claim 3 further provides a relative velocity detecting means for detecting the relative velocity between the first portion and the second portion due to the vibration of the structure in the vibration suppressing device for the structure according to claim 1 or 2. The control means is a vibrating fluid by a flow rate adjusting mechanism having a pump according to the detected relative velocity so that the vibration damping force acting on the first and second parts via the cylinder and the piston becomes a predetermined value. It is characterized in that the flow rate control for controlling the adjustment of the flow rate of the above is executed.

According to this configuration, the relative velocity between the first part and the second part due to the vibration of the structure is detected by the relative speed detecting means, and the control acting on the first and second parts via the cylinder and the piston. Flow amount control (flow pressure control) that controls the adjustment of the flow amount of the viscous fluid by the flow rate adjusting mechanism having a pump is executed according to the detected relative velocity so that the vibration force becomes a predetermined value. The damping force of the vibration suppression device is caused by the pressure difference between the viscous fluids in the first and second fluid chambers, as is clear from the above-described configuration. Therefore, when the piston is sliding in the inner section due to the vibration of the structure, the damping force acting on the structure can be controlled to be a predetermined value according to the relative speed.

The invention according to claim 4 further comprises a relative displacement detecting means for detecting the relative displacement between the first portion and the second portion due to the vibration of the structure in the vibration suppressing device for the structure according to the third aspect. The control means starts the flow amount control when the detected relative displacement becomes equal to or more than the predetermined displacement, and then the flow amount when the state in which the relative displacement is smaller than the predetermined displacement continues for the first predetermined time. After the control is finished, the predetermined displacement is set so that the piston slides in the predetermined section inside the inner section when the relative displacement is smaller than the predetermined displacement during the vibration of the structure. It is characterized by being.

According to this configuration, the relative displacement between the first part and the second part due to the vibration of the structure is detected by the relative displacement detecting means, and the detected relative displacement is equal to or more than the predetermined displacement during the vibration of the structure. When becomes, the flow amount control is started. In this case, the predetermined displacement is set so that the piston slides in the predetermined section inside the inner section when the relative displacement is smaller than the predetermined displacement during the vibration of the structure. As described above, it is possible to prevent the flow amount control from being unnecessarily performed when the vibration of the structure is very small and the relative displacement between the first portion and the second portion is smaller than the predetermined displacement. .. Further, after the start of the flow amount control, when the state in which the relative displacement is smaller than the predetermined displacement continues for the first predetermined time, the flow amount control is terminated, so that the vibration of the structure is surely very small. Wait, the flow amount control can be terminated. For the same reason, it is possible to prevent frequent repetition of execution and termination of flow amount control.

The invention according to claim 5 further includes a piston position detecting means for detecting a piston position which is a position of a piston in a cylinder in the vibration suppressing device for a structure according to claim 4, and the control means controls a flow amount. After the start of, the flow amount control is executed when the detected piston position is in the inner section, and the flow amount control is stopped when the piston position is in the outer section .

As described above, the first communication passage communicates with the first and second communication passages when the piston position is in the inner section, and the flow rate adjusting mechanism having a pump is the first communication passage and the first and first communication passages. 2 Adjust the flow rate of the viscous fluid flowing between the fluid chamber. Therefore, the damping force by controlling the flow amount of the control means can be adjusted only when the piston is sliding in the inner section. According to the configuration described above, the piston position, which is the position of the piston in the cylinder, is detected by the piston position detecting means, and the flow amount control is performed when the detected piston position is in the inner section after the start thereof. Is executed and stopped when the piston position is in the outer section . Therefore, the energy used for the flow amount control can be saved.

The invention according to claim 6 further includes a piston position detecting means for detecting the piston position, which is the position of the piston in the cylinder, in the vibration suppressing device for the structure according to claim 4, and the control means controls the flow amount. After the start of, when the detected piston position is in the inner section, the flow amount control is executed, and after the piston position deviates from the inner section to the outer section , the flow amount control is stopped and the flow amount control is performed. It is characterized in that the flow amount control is restarted when the state in which the piston position is in the inner section continues for the second predetermined time during the stop.

As described in the description of the invention according to claim 5, the damping force by controlling the flow amount of the control means can be adjusted only when the piston is sliding in the inner section. According to the above configuration, the piston position, which is the position of the piston in the cylinder, is detected by the piston position detecting means. Further, after the start of the flow amount control, the flow amount control is executed when the detected piston position is in the inner section, and the flow amount control is stopped after the piston position deviates from the inner section to the outer section. At the same time, the flow amount control is restarted when the state in which the piston position is in the inner section continues for the second predetermined time while the flow amount control is stopped.

As a result, after the piston position deviates from the inner section, that is, after the vibration of the structure becomes relatively large, the flow amount control is stopped, and the vibration of the structure is surely reduced. Since the flow amount control can be restarted, the energy used for the flow amount control can be sufficiently saved. For the same reason, it is possible to prevent frequent repetition of execution and stop of flow amount control.

The invention according to claim 7 further includes a piston position detecting means for detecting the piston position, which is the position of the piston in the cylinder, in the vibration suppressing device for the structure according to claim 4, and the control means controls the flow amount. After the start of, the flow amount control is executed when the detected piston position is in the inner section, the flow amount control is stopped after the piston position is located in the outer section , and the flow amount control is stopped. When the state in which the relative displacement is smaller than the predetermined displacement continues for the first predetermined time, the stop of the flow amount control is released and the flow amount control is terminated.

As described in the description of the invention according to claim 5, the damping force by controlling the flow amount of the control means can be adjusted only when the piston is sliding in the inner section. According to the above configuration, the piston position, which is the position of the piston in the cylinder, is detected by the piston position detecting means. Further, after the start of the flow amount control, the flow amount control is executed when the detected piston position is in the inner section, and after the piston position is located in the outer section , the flow amount control is stopped and the flow amount control is stopped. When the relative displacement is smaller than the predetermined displacement for the first predetermined time while the flow amount control is stopped, the stop of the flow amount control is released and the flow amount control is terminated.

As a result, the flow amount control is stopped after the piston position deviates from the inner section, that is, after the vibration of the structure becomes relatively large, and this stopped state is described in the description of the invention according to claim 4. Since the continuation is continued until the above-mentioned end condition of the flow amount control is satisfied, that is, until the vibration of the structure is surely very small, the energy used for the flow amount control can be sufficiently saved. For the same reason, it is possible to prevent frequent repetition of execution and stop of flow amount control. In addition, since the stop of the flow amount control is released when the flow amount control ends, the flow amount control is executed again when the relative displacement becomes equal to or more than the predetermined displacement due to the vibration of the structure increasing again. can do.

It is sectional drawing which shows the vibration suppression apparatus according to 1st Embodiment of this invention. It is sectional drawing which follows the line II-II of FIG. It is a block diagram which shows the control device of the vibration suppression device of FIG. It is a figure which shows roughly the vibration suppression device of FIG. 1 together with a part of a building to which this is applied. It is a flowchart which shows the process executed by the control device of FIG. It is a flowchart which shows the process different from FIG. 5 executed by the control device of FIG. It is a figure which shows the case where the vibration of a building is relatively small, as an example of the relationship between the relative displacement between beams and the vibration damping force in a building and a vibration suppression device of FIG. It is a figure which shows the case where the vibration of a building is relatively large, as an example of the relationship between the relative displacement between beams and the vibration damping force in a building and a vibration suppression device of FIG. It is a flowchart which shows the process executed by the control device of the vibration suppression apparatus according to 2nd Embodiment of this invention. It is a flowchart which shows the continuation of FIG. It is a flowchart which shows the process different from FIG. 9 and FIG. 10 executed by the control device of the vibration suppression apparatus according to 2nd Embodiment of this invention. It is a flowchart which shows a part of the process executed by the control device of the vibration suppression device according to the 3rd Embodiment of this invention. It is a flowchart which shows a part of the process executed by the control device of the vibration suppression device according to 4th Embodiment of this invention. It is sectional drawing which shows the modification of the vibration suppression apparatus.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 shows a vibration suppression device 1 according to the first embodiment of the present invention. The vibration suppression device 1 is configured as a so-called active type fluid damper, and includes a cylinder 2, a piston 3 slidably provided in the cylinder 2 in the axial direction, and a piston rod 4 integrated with the piston 3. It includes a communication passage 5 connected to the cylinder 2 and a flow rate adjusting mechanism 6 provided in the communication passage 5. The cylinder 2 has a cylindrical peripheral wall 2a, and a disc-shaped first side wall 2b and a second side wall 2c provided concentrically at one end and the other end of the peripheral wall 2a in the axial direction, respectively. There is. The space defined by the peripheral walls 2a, the first and second side walls 2b, and 2c is divided into the first fluid chamber 2d and the second fluid chamber 2e by the piston 3, and the first and second fluid chambers 2d and 2e are filled with the viscous fluid HF. The viscous fluid HF is composed of, for example, silicone oil.

Further, the first side wall 2b of the cylinder 2 is integrally provided with convex portions 2f protruding outward in the axial direction concentrically, and the convex portions 2f are first mounted via a universal joint. The tool FL1 is provided. Further, a rod guide hole 2g penetrating in the axial direction is formed at the center of the second side wall 2c in the radial direction. One end of the piston rod 4 is attached to the piston 3, and the piston rod 4 is partially accommodated in the cylinder 2 so as to be movable in the axial direction, and is inserted into the rod guide hole 2g via a seal. It extends outward from 2c. A second attachment FL2 is provided at the other end of the piston rod 4 via a universal joint.

Further, the outer peripheral surface of the piston 3 is in contact with the inner peripheral surface of the peripheral wall 2a of the cylinder 2 via a seal, and a plurality of first ones penetrating in the axial direction at the outer end portion in the radial direction of the piston 3. A communication hole 3a and a second communication hole 3b (only one of each is shown) are formed. The first communication hole 3a is provided with a first pressure regulating valve 15, and the second communication hole 3b is provided with a second pressure regulating valve 16.

The first pressure regulating valve 15 is composed of a valve body and a spring that urges the valve body in the valve closing direction. When the pressure of the viscous fluid HF in the first fluid chamber 2d is smaller than a predetermined value, the first pressure regulating valve 15 is the first. The communication hole 3a is closed, and when a predetermined value is reached, the first communication hole 3a is opened. By opening the first communication hole 3a by the first pressure regulating valve 15, the first and second fluid chambers 2d and 2e communicate with each other through the first communication hole 3a. Like the first pressure regulating valve 15, the second pressure regulating valve 16 is composed of a valve body and a spring that urges the valve body in the valve closing direction, and the pressure of the viscous fluid HF in the second fluid chamber 2e is predetermined. When it is smaller than the value, the second communication hole 3b is closed, and when the predetermined value is reached, the second communication hole 3b is opened. By opening the second communication hole 3b by the second pressure regulating valve 16, the second and first fluid chambers 2e and 2d communicate with each other through the second communication hole 3b.

Further, the piston 3 is provided with a first relief valve and a second relief valve (neither of which is shown). These first and second relief valves limit the pressure of the viscous fluid HF in the first and second fluid chambers 2d and 2e so as not to exceed a predetermined upper limit value larger than the above predetermined value, respectively. ..

The communication passage 5 bypasses the piston 3 and communicates with the first and second fluid chambers 2d and 2e when the piston 3 is located in a predetermined inner section INI including a neutral position described later. It is connected to the cylinder 2. In the cylinder 2, predetermined outer sections INO and INO are provided on both outer sides of the inner section INI in the axial direction. Further, the cross-sectional area of the communication passage 5 (the area of the surface orthogonal to the axial direction) is set to a value smaller than that of the cylinder 2, and is smaller than that of the first and second communication holes 3a and 3b of the piston 3. Is also set to a large value. Further, the communication passage 5 is filled with the viscous fluid HF as in the first and second fluid chambers 2d and 2e.

The flow rate adjusting mechanism 6 has a gear pump powered by an electric motor 7. The gear pump is of the circumscribed gear type, and is composed of a casing 8, a first gear 9 and a second gear 10 housed in the casing 8, and the like. An inscribed gear type gear pump may be used as the gear pump. The casing 8 is integrally provided in the central portion of the communication passage 5, and the inside of the casing 8 communicates with the communication passage 5 via two entrances 8a and 8b facing each other.

Further, the first gear 9 is composed of a spur gear and is integrally provided with the first rotating shaft 11. The first rotating shaft 11 extends horizontally in a direction orthogonal to the communication passage 5, is rotatably supported by the casing 8, and slightly protrudes to the outside of the casing 8 (see FIG. 2). Like the first gear 9, the second gear 10 is composed of spur gears, is integrally provided on the second rotating shaft 12, and meshes with the first gear 9. The second rotating shaft 12 extends parallel to the first rotating shaft 11 and is rotatably supported by the casing 8. Further, the meshing portions of the first and second gears 9 and 10 face the entrances 8a and 8b of the casing 8.

The electric motor 7 is, for example, a DC motor capable of generating electric power, and its rotor (not shown) is concentrically connected to the first rotating shaft 11 and is connected to the first gear 9 and the first rotating shaft 11. It can rotate integrally. Further, as shown in FIG. 3, the electric motor 7 is connected to a power source 22 composed of, for example, a battery, via a control device 21. The control device 21 is composed of a combination of a rectifier, a CPU, RAM, ROM, an I / O interface, and the like.

As shown in FIG. 4, for example, the vibration suppression device 1 having the above configuration includes a joint portion of the upper beam BU and the left column PL of the high-rise building B and a joint portion of the upper beam BU and the right column PR of the building B. It is connected to the joint portion of the lower beam BD and the right column PR of the building B via the connecting member EN while being connected via the V-shaped brace material BR. In this case, the first attachment FL1 is attached to the lower end of the brace material BR, and the second attachment FL2 is attached to the connecting member EN, and the vibration suppression device 1 extends in the left-right direction. The brace material BR and the connecting member EN are made of, for example, H-shaped steel. Further, when the building B is not vibrating, the piston 3 is in the neutral position shown in FIG. In FIG. 4, for convenience, the communication passage 5 and the flow rate adjusting mechanism 6 are not shown. Further, a pair of left and right vibration suppression devices may be provided symmetrically with the brace material BR as the center.

Further, in the vibration suppression device 1, when a relative displacement occurs in the left-right direction between the upper and lower beams BU and BD due to the vibration of the building B, this relative displacement is transmitted to the cylinder 2 and the piston rod 4 as an external force. The piston rod 4 moves in the axial direction with respect to the cylinder 2, and the piston 3 integrated with the piston rod 4 slides in the cylinder 2 in the axial direction. In this case, when the piston 3 slides toward the first side wall 2b of the cylinder 2 (when the vibration suppression device 1 contracts), the viscous fluid HF in the first fluid chamber 2d is pressed by the piston 3, and one of them is The portion flows to the second fluid chamber 2e side through the communication passage 5. On the contrary, when the piston 3 slides toward the second side wall 2c side of the cylinder 2 (when the vibration suppression device 1 is extended), the viscous fluid HF in the second fluid chamber 2e is pressed by the piston 3. , A part of which flows to the first fluid chamber 2d side through the communication passage 5.

As is clear from the above operation, during the vibration of the building B, the vibration damping force according to the difference between the pressure of the viscous fluid HF in the first fluid chamber 2d and the pressure of the viscous fluid HF in the second fluid chamber 2e is the cylinder. It acts to suppress the vibration of the building B via the 2 and the piston rod 4. In the vibration suppression device 1, the vibration damping force is adjusted by controlling the electric motor 7 of the flow rate adjusting mechanism 6 by the control device 21 during the vibration of the building B due to an earthquake or the like.

Further, for example, semiconductor type first and second acceleration sensors 23 and 24 are connected to the control device 21. The first and second acceleration sensors 23 and 24 refer to the acceleration due to the vibration of the upper beam BU (hereinafter referred to as "upper beam vibration acceleration") ACBU and the acceleration due to the vibration of the lower beam BD (hereinafter referred to as "lower beam vibration acceleration") ACBD. Each is detected, and the detection signals are output to the control device 21. The control device 21 executes the processes shown in FIGS. 5 and 6 according to the programs stored in the ROM in response to the detection signals of the first and second acceleration sensors 23 and 24.

FIG. 5 shows a process for setting various parameters related to flow amount control, which will be described later. This process is repeatedly executed every predetermined time (for example, 10 msec). First, in step 1 of FIG. 5 (shown as “S1”; the same applies hereinafter), the absolute velocity (velocity in the absolute coordinate system) due to the vibration of the upper beam BU is obtained by integrating the detected upper beam vibration acceleration ACBU. The upper beam vibration velocity VBU is calculated. Next, by integrating the detected lower beam vibration acceleration ACBD, the lower beam vibration velocity VBD, which is the absolute speed due to the vibration of the lower beam BD, is calculated (step 2).

In this step 1, the upper beam vibration velocity VBU is calculated as a positive value (+) when the upper beam BU is moving to the right in FIG. 4 due to vibration, and a negative value (-) when the upper beam BU is moving to the left. ) Is calculated. This also applies to the lower beam vibration velocity VBD. In step 3 following step 2, the inter-beam relative velocity REVB is calculated by subtracting the lower beam vibration velocity VBD calculated in step 2 from the upper beam vibration velocity VBU calculated in step 1.

Next, by integrating the upper beam vibration velocity VBU, the upper beam absolute displacement DBU, which is the absolute displacement (displacement in the absolute coordinate system) of the upper beam BU due to vibration, is calculated (step 4). Next, by integrating the lower beam vibration velocity VBD, the lower beam absolute displacement DBD, which is the absolute displacement of the lower beam BD due to vibration, is calculated (step 5). In this step 4, the upper beam absolute displacement DBU is calculated as a positive value (+) when the upper beam BU is displaced to the right in FIG. 4 from the neutral position due to vibration, and is negative when the upper beam BU is displaced to the left. Calculated as a value (-). This also applies to the lower beam absolute displacement DBD. In step 6 following step 5, the inter-beam relative displacement REDB is calculated by subtracting the lower beam absolute displacement DBD calculated in step 5 from the upper beam absolute displacement DBU calculated in step 4 above.

Next, it is determined whether or not the absolute value | REDB | of the relative displacement between beams calculated in step 6 is equal to or greater than the predetermined displacement DREF (step 7). This predetermined displacement DREF is set to a size such that the piston 3 slides in the predetermined section inside the inner section INI when | REDB | <DREF during the vibration of the building B, specifically. , The absolute value of the relative displacement between the upper and lower beams BU and BD when the building B is vibrating with a size that can be recognized by a person in the building B is set, for example, 1 mm.

When the answer in step 7 is NO (| REDB | <DREF), it is determined whether or not the flow amount control execution flag F_CONT is "1" (step 8). The flow amount control execution flag F_CONT indicates that the execution condition for the flow amount control is satisfied by "1", and is initialized to "0" when the control device 21 is started. When the answer in step 8 is NO (F_CONT = 0), this process ends as it is.

On the other hand, when the answer in step 7 is YES (| REDB | ≧ DREF), the timer value tM1 of the up-count type first timer is initialized to a value 0 (step 9), and the flow amount control execution flag F_CONT is set to “ It is determined whether or not it is "1" (step 10). When the answer of step 10 is NO (F_CONT = 0), it is assumed that the execution condition of the flow amount control is satisfied because the answer of step 7 is YES, and the flow amount control execution flag F_CONT is set to indicate that. Set to "1" (step 11) and end this process. On the other hand, when the answer in step 10 is YES (F_CONT = 1), step 11 is skipped and this process ends. When the flow amount control execution flag F_CONT is set to "1", the flow amount control is started in the process of FIG. 6 described later.

On the other hand, when the answer in step 8 is YES (F_CONT = 1), it is determined whether or not the timer value tM1 of the first timer initialized in step 9 is TREF1 (for example, 10 sec) or more for the first predetermined time. (Step 12). When this answer is NO (tM1 <TREF1), this process is terminated as it is.

On the other hand, when the answer in step 12 is YES (tM1 ≧ TREF1), that is, after the flow amount control is started as | REDB | ≧ DREF is established, | REDB | <DREF When the state of TREF1 is continued for the first predetermined time, the flow amount control execution flag F_CONT is set to “0” in order to end the flow amount control (step 13), and this process is ended.

Further, FIG. 6 shows a process for executing the flow amount control. This process is repeatedly executed at predetermined time (for example, 10 msec) following the process shown in FIG. First, in step 21 of FIG. 6, it is determined whether or not the flow amount control execution flag F_CONT set in step 11 or 13 of FIG. 5 is "1". When the answer is NO (F_CONT = 0), the flow amount control is stopped (step 22), and this process is terminated. By executing this step 22, the power source 22 and the electric motor 7 are electrically cut off, and no current flows through the electric motor 7.

On the other hand, when the answer in step 21 is YES (F_CONT = 1), the flow amount control is executed according to the inter-beam relative velocity REVB calculated in step 3 of FIG. 5 (step 23), and this process is completed. ..

In this step 23, the flow amount control is executed as follows. When the sign of the inter-beam relative velocity REVB is + (-), that is, when the upper beam BU is displaced to the right (left) with respect to the lower beam BD, the relative displacement between the two BUs and BDs is determined. The amount of flow of the viscous fluid HF flowing through the communication passage 5 is such that the vibration damping force of the predetermined value + FREF (-FREF, see FIGS. 7 and 8 described later) in the suppressing direction acts on the upper and lower beams BU and BD. It is controlled via the electric motor 7. In the following description, "+" and "-" of the predetermined value + FREF (-FREF) are appropriately omitted.

Since the vibration damping force of the vibration suppression device 1 is based on the viscous fluid HF, the smaller the input inter-beam relative velocity REVB, the smaller the vibration damping force. Therefore, in order to exert the vibration damping force of the predetermined value FREF, the continuous passage is used. The flow amount of the viscous fluid HF in No. 5 is adjusted to be smaller (so that the viscous fluid HF is less likely to flow). In this case, when the relative velocity REVB between beams is relatively large, the flow amount of the viscous fluid HF in the communication passage 5 is adjusted by controlling the regeneration (power generation) of the electric motor 7. Further, when the input inter-beam relative speed REVB is relatively small, the piston 3 is moved in the direction opposite to the sliding direction of the piston 3 by the input of the inter-beam relative speed REVB by controlling the power running (power supply) of the electric motor 7. The flow amount of the viscous fluid HF in the communication passage 5 is adjusted so as to slide.

Further, FIG. 7 shows the relationship between the relative displacement between beams REDB and the vibration damping force FD of the vibration suppressing device 1 in the case where the piston 3 is sliding in the inner section INI. In FIG. 7, the section (| + DPIN | = | -DPIN |) defined by the predetermined value + DPIN and the predetermined value −DPIN corresponds to the inner section INI, and + FMAX (−FMAX) is the damping force FD. The maximum value. In the following description, "+" and "-" of the predetermined value + DPIN (-DPIN) and the maximum value + FMAX (-FMAX) are appropriately omitted.

As described above, when the absolute value | REDB | of the relative displacement between beams becomes equal to or greater than the predetermined displacement DREF due to the vibration of the building B (step 7: YES in FIG. 5), the flow amount control is started (step 11, FIG. Step 21 of 6: YES, step 23). As a result, as shown in FIG. 7, the vibration damping force FD is controlled to be a predetermined value + FREF (−FREF). In this case, the flow amount of the viscous fluid HF in the communication passage 5 is controlled so that the damping force FD acts in the direction of suppressing the relative displacement REDB between the beams with respect to the upper and lower beams BU and BD. The damping force FD changes as shown by the thick solid line and the arrow in FIG.

Further, FIG. 8 shows the relationship between the relative displacement between beams REDB and the vibration damping force FD of the vibration suppression device 1 in the case where the piston 3 slides in the inner section INI and the outer section INO. When the piston 3 is sliding on the outer section INO (REDB> + DPIN, REDB <-DPIN), the communication passage 5 does not communicate with the first and second fluid chambers 2d and 2e, so that the first and second fluid chambers 5 are not communicated with each other. The viscous fluid HF in the two fluid chambers 2d and 2e passes through the first and second communication holes 3a and 3b with the opening of the first and second pressure regulating valves 15 and 16, respectively, and the second and first fluids. It flows into the chambers 2e and 2d. As a result, when the piston 3 is sliding on the outer section INO, the vibration suppression device 1 functions as a so-called passive damper. As a result of the above, when the piston 3 is sliding between the inner section INI and the outer section INO and the relative velocity REVB between beams is relatively small, the damping force FD changes as shown by a thick solid line and an arrow.

Further, when the piston 3 is sliding between the inner section INI and the outer section INO and the relative velocity REVB between beams is very large, the flow rate of the viscous fluid HF in the communication passage 5 is adjusted by the flow rate control. However, due to the configuration of the flow rate adjusting mechanism 6, the vibration damping force FD cannot be controlled to a predetermined value + FREF (-FREF), and the pressure of the viscous fluid HF in the first and second fluid chambers 2d and 2e is the first. The upper limit is reached by the limitation by the 1st and 2nd relief valves. Therefore, in this case, the damping force FD becomes the maximum value + FMAX (−FMAX), and changes as shown by the thick alternate long and short dash line and the arrow.

As described above, according to the first embodiment, the cylinder 2 is connected to the upper beam BU of the building B, and the piston 3 is connected to the lower beam BD of the building B, respectively. The piston 3 is slidably provided in the cylinder 2 in the axial direction, and the inside of the cylinder 2 is divided into a first fluid chamber 2d and a second fluid chamber 2e, and the cylinder 2 is when the building B is not vibrating. It is located in a predetermined neutral position inside (see FIG. 1). Further, when the first and second fluid chambers 2d and 2e are filled with the viscous fluid HF and the piston 3 is located in a predetermined inner section INI including the neutral position, the first fluid chamber 2d and 2e The communication passage 5 for flowing the viscous fluid HF between the second fluid chambers 2e bypasses the piston 3 and communicates with the first and second fluid chambers 2d and 2e.

Further, the communication passage 5 is provided with the above-mentioned flow rate adjusting mechanism 6, and the control device 21 controls the adjustment of the flow rate of the viscous fluid HF by the flow rate adjusting mechanism 6. Further, the piston 3 is formed with first and second communication holes 3a and 3b penetrating in the axial direction thereof. The first and second communication holes 3a and 3b communicate with the first and second fluid chambers 2d and 2e, and the first and second pressure regulating valves 15 and 16 described above are provided in both communication holes 3a and 3b. It is provided.

From the above, the relative displacement REDB between the upper and lower beams BU and BD generated by the vibration of the building B is transmitted to the cylinder 2 and the piston 3, whereby the piston 3 slides in the cylinder 2. The vibration of the building B is relatively small, so that the viscous fluid HF flows between the first and second fluid chambers 2d and 2e and the communication passage 5 when the piston 3 slides in the inner section INI. Along with this, a vibration damping force corresponding to the difference between the pressure of the viscous fluid HF in the first fluid chamber 2d and the pressure of the viscous fluid HF in the second fluid chamber 2e acts on the upper and lower beams BU and BD. In this case, the difference between the pressure of the viscous fluid HF in the first fluid chamber 2d and the pressure of the viscous fluid HF in the second fluid chamber 2e changes according to the amount of flow of the viscous fluid HF flowing through the communication passage 5. Therefore, when the vibration of the building B is relatively small, the flow rate of the viscous fluid HF flowing between the communication passage 5 and the first and second fluid chambers 2d and 2e is controlled by the flow rate adjusting mechanism 6 through the control device 21. By controlling with, a desired damping force can be obtained.

Further, when the vibration of the building B is relatively large and the piston 3 is sliding outside the inner section INI, that is, in the outer section INO, the communication passage 5 communicates with the first and second fluid chambers 2d and 2e. The viscous fluid HF does not flow between the first and second fluid chambers 2d and 2e and the communication passage 5. In this case, when the pressure of the viscous fluid HF in the first fluid chamber 2d pressed by the piston 3 reaches a predetermined value, the first communication hole 3a is opened by the first pressure regulating valve 15, and the viscous fluid HF is first. And, it flows between the second fluid chambers 2d and 2e and the first communication hole 3a. Further, when the pressure of the viscous fluid in the second fluid chamber 2e pressed by the piston 3 reaches a predetermined value, the second communication hole 3b is opened by the second pressure regulating valve 16, and the viscous fluid HF is first and first. 2 Flows between the fluid chambers 2d and 2e and the second communication hole 3b. As described above, when the vibration of the building B is large, a relatively large damping force can be obtained.

Further, as described above, unlike the conventional vibration suppression device described above, the semi-active circuit and the passive circuit are separated from each other without using a complicated hydraulic circuit in which the inflow oil passage and the outflow oil passage are connected in parallel. Since a simpler configuration including the communication passages 5, 1st and 2nd communication holes 3a and 3b provided in the above is used, the manufacturing cost of the vibration suppression device 1 can be reduced. Further, even if an abnormality occurs in the flow rate adjusting mechanism 6 and / or the control device 21, the viscous fluid HF is transmitted between the first and second fluid chambers 2d and 2e by the first and second communication holes 3a and 3b. Since the fluid can be appropriately flowed and the effect of the abnormality is limited to when the piston 3 is moving in the inner section INI, the vibration damping force FD of the vibration suppression device 1 due to the abnormality is excessively increased. And under-reduction can be prevented, and damage to the building B due to the abnormality can be prevented.

Further, since the first and second communication holes 3a and 3b are used as the second communication passage in the present invention, it can be configured more easily than the case where the communication passage of the type that bypasses the piston 3 is used. The manufacturing cost of the vibration suppression device 1 can be further reduced.

Further, the inter-beam relative velocity REVB, which is the relative velocity between the upper and lower beams BU and BD due to the vibration of the building B, is calculated (step 3 in FIG. 5), and the above-mentioned flow amount control is performed according to the inter-beam relative velocity REVB. Is executed (step 23 in FIG. 6). As a result, when the piston 3 is sliding in the inner section INI due to the vibration of the building B, the damping force FD acting on the building B is set to a predetermined value FREF according to the relative velocity REVB between the beams. Can be controlled to.

Further, the inter-beam relative displacement REDB, which is the relative displacement between the upper and lower beams BU and BD due to the vibration of the building B, is calculated, and the absolute value | REDB | of the inter-beam relative displacement during the vibration of the building B is equal to or greater than the predetermined displacement DREF. (Step 7: YES in FIG. 5), flow amount control is started (step 11, step 21: YES in FIG. 6, step 23). Further, the predetermined displacement DREF is set to a size such that the piston 3 slides in the predetermined section inside the inner section INI when | REDB | <DREF during the vibration of the building B. As described above, it is possible to prevent the flow amount control from being unnecessarily performed when the vibration of the building B is very small and the relative displacement between beams REDB is smaller than the predetermined displacement DREF.

Further, after the start of the flow amount control, when the state in which the inter-beam relative displacement REDB is smaller than the predetermined displacement DREF continues for the first predetermined time TREF1 (step 12: YES in FIG. 5), the flow amount control ends (step). 13. Since step 21: NO, step 22) in FIG. 6, the flow amount control can be ended after waiting for the vibration of the building B to become very small. For the same reason, it is possible to prevent frequent repetition of execution and termination of flow amount control.

Further, since the vibration damping force FD of the vibration suppression device 1 can be controlled to a predetermined value + FREF (-FREF) by the flow amount control, the brace material BR and the connection for transmitting the vibration damping force FD to the upper and lower beams BU and BD. It is sufficient to set the rigidity of the member EN so as to satisfy the short-term allowable stress with respect to the maximum value FMAX of the damping force FD, and to set the rigidity of the brace material BR and the connecting member EN in that way. Therefore, the cross-sectional area of the brace material BR and the connecting member EN can be reduced.

Next, the vibration suppression device according to the second embodiment of the present invention will be described with reference to FIGS. 9 to 11. This vibration suppression device differs only in the execution content of the process executed by the control device 21 as compared with the first embodiment. In FIGS. 9 to 11, the same reference numerals are given to the same execution contents as those in the first embodiment. Hereinafter, the points different from those of the first embodiment will be mainly described.

In FIG. 9, step 31 is executed following step 6. In this step 31, the piston position POPI, which is the position of the piston 3 in the cylinder 2, is calculated by searching a predetermined map (not shown) based on the inter-beam relative displacement REDB calculated in step 6. Then, the steps 7 and subsequent steps in FIG. 10 are executed. The above map is a map obtained by experimentally obtaining the relationship between the relative displacement between beams REDB and the piston position POPI in consideration of the deformation rigidity of the brace material BR due to the vibration of the building B. As a result, the piston position POPI is calculated to have a value of 0 for the above-mentioned neutral position, a positive value (+) when it is on the first side wall 2b side of the neutral position, and a negative value (+) when it is on the second side wall 2c side. -) Are calculated respectively.

In FIG. 10, when the answer in step 10 is YES (F_CONT = 1), and following step 11, step 41 is executed. In this step 41, it is determined whether or not the absolute value | POPI | of the piston position calculated in the above step 31 is equal to or less than the predetermined value POREF. The predetermined value POREF is for determining that the piston 3 is in the inner section INI.

When the answer of this step 41 is YES (| POPI | ≤ POREF), that is, when the piston 3 is in the inner section INI, it is determined whether or not the stop flag F_STOP is "1" (step 42). The stop flag F_STOP indicates that the flow amount control is stopped by "1", and is initialized to "0" when the control device 21 is started. When the answer in step 42 is NO (F_STOP = 0), this process ends as it is.

Further, when the answer in step 12 of FIG. 10 is NO (tM1 <TREF1), that is, after the execution of the flow amount control is started, the state of | REDB | <DREF is not continued for the first predetermined time TREF1. Occasionally, step 42 is performed. As is clear from the setting of the predetermined displacement DREF described above, when the answer in step 7 is NO and | REDB | <DREF, the piston 3 is located in the inner section INI.

On the other hand, when the answer in step 41 is NO (| POPI |> POREF) and the piston 3 is outside the inner section INI, the stop flag F_STOP is set to "1" in order to stop the flow amount control (step). 43), this process is terminated.

On the other hand, when the answer in step 42 is YES, that is, when the piston 3 is located in the inner section INI while the flow amount control is stopped, the stop flag F_STOP is set in order to release the stop of the flow amount control. Set to "0" (step 44) and end this process.

Further, FIG. 11 shows a process for executing the flow amount control according to the second embodiment, and when the answer of the step 21 of FIG. 11 is YES (F_CONT = 1), the step 43 of FIG. 10 or It is determined whether or not the stop flag F_STOP set in 44 is "1" (step 51). When the answer is YES (F_STOP = 1), the step 22 is executed and the flow amount control is stopped. On the other hand, when the answer in step 51 is NO (F_STOP = 0), the step 23 is executed, the flow amount control is executed, and then this process is terminated.

As described above, according to the second embodiment, the piston position POPI, which is the position of the piston 3 in the cylinder 2, is calculated (step 31 in FIG. 9). Further, the flow amount control is executed when the piston position POPI is in the inner section INI after the start (step 41: YES, step 7: NO, step 12: NO, step 42, step 44, FIG. 10). Step 51: NO in FIG. 11: NO, step 23), stopped when the piston position POPI is outside the inner section INI (step 41: NO in FIG. 10, step 43, step 51: YES in FIG. 11, step 22). .. Therefore, the electric energy used for the flow amount control can be saved.

Next, the vibration suppression device according to the third embodiment of the present invention will be described with reference to FIG. Compared with the second embodiment, this vibration suppression device differs only in the execution content of the process for setting various parameters executed by the control device 21. In FIG. 12, the same execution contents as those in the first and second embodiments are designated by the same reference numerals. Hereinafter, the points different from those of the first and second embodiments will be mainly described.

When the answer in step 41 of FIG. 12 is NO (| POPI |> POREF), the timer value tM2 of the up-count type second timer is initialized to a value of 0 (step 61). Next, the step 43 is executed, the stop flag F_STOP is set to "1", and then this process ends.

Further, when the answer in step 42 of FIG. 12 is YES (F_STOP = 1) and the flow amount control is stopped, the timer value tM2 of the second timer initialized in step 61 is the second predetermined time TREF2. It is determined whether or not the above is the case (step 62). The second predetermined time TREF2 is set to a value equal to or less than the first predetermined time TREF1, and is, for example, 5 seconds.

When the answer in step 62 is NO (tM2 <TREF2), this process ends as it is. On the other hand, when the answer in step 62 is YES, that is, when the state of | POPI | ≤ POREF (the state in which the piston 3 is in the inner section INI) continues for the second predetermined time TREF2 while the flow amount control is stopped. In order to release the stop of the flow amount control and restart the flow amount control, the step 44 is executed, the stop flag F_STOP is set to "0", and then this process is terminated.

As described above, according to the third embodiment, the piston position POPI is calculated as in the second embodiment (see step 31 in FIG. 9). Further, after the start of the flow amount control, the flow amount control is executed when the piston position POPI is in the inner section INI as in the second embodiment (step 41: YES, step 7: NO, step in FIG. 12). 12: NO, step 42: NO, step 51: NO in FIG. 11, step 23), stopped when the piston position POPI is outside the inner section INI (step 41: NO in FIG. 12, step 43, FIG. 11). Step 51: YES, step 22).

Further, while the flow amount control is stopped (step 42: YES in FIG. 12), when the state in which the piston position POPI is in the inner section INI continues for the second predetermined time (step 62: YES), the flow amount Control is resumed (step 44, step 51: NO, step 23 in FIG. 11). As a result, after the piston position POPI deviates from the inner section INI, that is, after the vibration of the building B becomes relatively large, the flow amount control is stopped and the vibration of the building B is surely reduced. Since the flow amount control can be restarted, the electric energy used for the flow amount control can be sufficiently saved. For the same reason, it is possible to prevent frequent repetition of execution and stop of flow amount control. It should be noted that the electric motor 7 generates electricity while the flow amount control is stopped (when the stop condition is satisfied. Stop flag F_STOP = 1) and when the piston 3 is moving in the inner section INI. , The power supply 22 may be charged.

Next, the vibration suppression device according to the fourth embodiment of the present invention will be described with reference to FIG. Compared with the second embodiment, this vibration suppression device differs only in the execution content of the process for setting various parameters executed by the control device 21. In FIG. 13, the same execution contents as those in the first and second embodiments are designated by the same reference numerals. Hereinafter, the points different from those of the first and second embodiments will be mainly described.

In FIG. 13, when the answer in step 10 is YES (F_CONT = 1), and following step 11, step 71 is executed. In this step 71, it is determined whether or not the stop flag F_STOP is “1”. If the answer is YES (F_STOP = 1) and the flow amount control is stopped, this process is terminated as it is.

On the other hand, when the answer in step 71 is NO (F_STOP = 0), the step 41 is executed. When the answer in step 41 is YES (| POPI | ≤ POREF), this process ends as it is.

Further, when the answer in step 12 of FIG. 13 is NO (tM1 <TREF1), the present process is terminated as it is.

As described above, according to the fourth embodiment, the piston position POPI is calculated as in the second embodiment (see step 31 in FIG. 9). Further, after the start of the flow amount control, the flow amount control is executed when the piston position POPI is in the inner section INI (step 71: NO in FIG. 13, step 41: YES, step 51: NO in FIG. 11). Step 23), after the piston position POPI is located outside the inner section INI, the flow amount control is stopped (step 41: NO in FIG. 13, step 43, step 51: YES in FIG. 11, step 22). Further, when the absolute value | REDB | of the relative displacement between the beams is smaller than the predetermined displacement DREF for the first predetermined time TREF1 while the flow amount control is stopped, the flow amount is continued (step 12: YES in FIG. 13). When the stop of control is released (step 44), the flow amount control is terminated (step 13, step 21: NO in FIG. 11, step 22).

As a result, the flow amount control is stopped after the piston position POPI deviates from the inner section INI, that is, after the vibration of the building B becomes relatively large, and this stopped state is set to the flow amount according to step 12 described above. Since it is continued until the end condition of the control is satisfied, that is, until the vibration of the building B is surely very small, the electric energy used for the flow amount control can be sufficiently saved. For the same reason, it is possible to prevent frequent repetition of execution and stop of flow amount control. Further, since the stop of the flow amount control is released with the end of the flow amount control, when the absolute value | REDB | of the relative displacement between beams becomes larger than the predetermined displacement DREF due to the vibration of the building B increasing again. In addition, the flow amount control can be executed again. As in the third embodiment, when the flow amount control is stopped and the piston 3 is moving in the inner section INI, the electric motor 7 may generate electricity and the power supply 22 may be charged. ..

The present invention is not limited to the first to fourth embodiments described above (hereinafter, collectively referred to as "embodiments"), and can be implemented in various embodiments. For example, in the embodiment, the viscous fluid HF composed of silicone oil is used, but other suitable viscous fluid may be used. Further, in the embodiment, the communication passage 5 connected to the cylinder 2 is used, but the communication passage formed on the peripheral wall 2a of the cylinder 2 may be used. Further, in the embodiment, the first and second communication holes 3a and 3b are used as the second communication passage in the present invention, but the piston is bypassed and the communication passage connected to the cylinder and the peripheral wall of the cylinder are used. The formed communication passage may be used.

Further, in the embodiment, the flow rate adjusting mechanism 6 having a gear pump is used as the flow rate adjusting mechanism in the present invention, but another suitable mechanism, for example, a flow rate adjusting mechanism having a piston mechanism 31 shown in FIG. 14 is used. You may. Since this piston mechanism 31 is the same as that disclosed in FIG. 5 of Japanese Patent Application No. 2015-147612 by the present applicant, detailed description thereof will be omitted. When a flow rate adjusting mechanism having a piston mechanism 31 is used, the movement of the piston of the piston mechanism 31 is as shown in FIG. 14 and as disclosed in FIG. 5 of Japanese Patent Application No. 2015-147612. In order to secure a sufficient range, the communication passage 32 is configured so that the portion extending in parallel with the cylinder 2 is relatively long. Alternatively, as the flow rate adjusting mechanism, a vane pump, a flow rate adjusting mechanism having a screw mechanism described in paragraph [0049] of Japanese Patent No. 5191579, FIGS. 2 and 5, and an on-off valve for opening and closing the first continuous passage. Etc. may be used. When this on-off valve is used as the flow rate adjusting mechanism, the vibration suppression device is configured as a so-called semi-active fluid damper.

Further, in the embodiment, the pressures of the viscous fluids HF opened by the first and second pressure regulating valves 15 and 16 are set to the same predetermined values, but are set to different first and second predetermined values. Each may be set.

Further, in the embodiment, the flow rate adjusting mechanism 6 is controlled as described above, but the control method is not limited to these, and other appropriate methods may be used. For example, in the embodiment, the flow rate adjusting mechanism 6 is controlled according to the inter-beam relative velocity REVB, but it may be controlled according to the inter-beam relative displacement REDB. In that case, the inter-beam relative displacement REDB becomes a value 0. As described above, the flow rate adjusting mechanism 6 may be controlled by using the feedback control algorithm. Further, in the embodiment, the relative velocity REVB between beams is calculated, but it may be detected by a sensor. This also applies to the inter-beam relative displacement RED B and the piston position POPI.

Further, in the embodiment, the cylinder 2 is connected to the upper beam BU and the piston 3 is connected to the lower beam BD, but conversely, the cylinder 2 is connected to the lower beam BD and the piston 3 is connected to the upper beam BU. , Each may be connected. Further, in the embodiment, the upper beam BU and the lower beam BD are adopted as the first and second portions in the present invention, respectively, to suppress the inter-story displacement between the two layers, but other appropriate portions are adopted. May be good. For example, upper and lower beams having one or more beams provided between each other may be adopted to suppress inter-story displacement between three or more layers. Further, it goes without saying that the lower layer beam and the upper layer beam of the structure may be adopted as the first and second portions, respectively.

Further, in the embodiment, the vibration suppression device 1 is provided so as to suppress the vibration in the left-right direction of the building B, but it may be provided so as to suppress the vibration in the front-rear direction and the vibration in the up-down direction. Further, in the embodiment, the structure in the present invention is a high-rise building B, but other suitable structures such as steel towers and bridges may be used. It goes without saying that the variations relating to the above embodiments may be appropriately combined and applied. In addition, it is possible to appropriately change the detailed configuration within the scope of the gist of the present invention.

B building (structure)
BU upper beam (one of the first and second parts)
BD lower beam (the other of the first and second parts)
1 Vibration suppression device 2 Cylinder 2d 1st fluid chamber 2e 2nd fluid chamber INI inner section 3 Piston 3a 1st communication hole (2nd communication passage)
3b 2nd communication hole (2nd communication passage)
5 consecutive passages (1st consecutive passage)
6 Flow rate adjusting mechanism HF viscous fluid 15 1st pressure regulating valve 16 2nd pressure regulating valve 21 Control device (control means, relative velocity detecting means, relative displacement detecting means, piston position detecting means)
REVB Relative velocity between beams (relative velocity)
REDB Relative displacement between beams (relative displacement)
+ FREF predetermined value-FREF predetermined value DREF predetermined displacement TREF1 first predetermined time POPI piston position TREF2 second predetermined time

Claims (7)

A structure vibration suppression device provided between a first portion and a second portion in a system including a structure for suppressing vibration of the structure.
A cylinder connected to one of the first and second parts,
It is connected to the other of the first and second parts and is slidably provided in the cylinder in the axial direction, and the inside of the cylinder is divided into a first fluid chamber and a second fluid chamber, and the structure vibrates. A piston located in a predetermined neutral position in the cylinder when not provided.
The internal space of the cylinder is divided into a predetermined inner section including the neutral position of the piston and a predetermined outer section adjacent to both outer sides of the inner section.
The viscous fluid filled in the first and second fluid chambers and
When the piston is located in the inner section, the viscous fluid communicates with the first and second fluid chambers by bypassing the piston and between the first fluid chamber and the second fluid chamber. A first communication passage configured so as not to bypass the piston when the piston is located in the outer section.
The first passage and the first passage are provided in the first passage by using an electric motor as a power source and converting the mechanical energy of the electric motor into the kinetic energy of the viscous fluid in the first passage. And a flow rate adjusting mechanism having a pump for actively adjusting the flow rate of the viscous fluid flowing between the second fluid chamber and the second fluid chamber.
A control means for controlling the adjustment of the flow rate of the viscous fluid by the flow rate adjusting mechanism, and
A second communication passage that communicates with the first and second fluid chambers and allows the viscous fluid to flow between the first fluid chamber and the second fluid chamber.
The second passage is provided in the second passage, the second passage is closed when the pressure of the viscous fluid in the first fluid chamber is smaller than the first predetermined value, and the first predetermined value is reached. The first pressure regulating valve that opens the double passage and
The second passage is provided when the pressure of the viscous fluid in the second fluid chamber is smaller than the second predetermined value, the second passage is closed, and when the pressure reaches the second predetermined value, the second passage is closed. Further equipped with a second pressure regulating valve that opens the double passage ,
When said piston is located at the outer section, the vibration suppression device of a structure which is characterized that you function as a passive damper by the first pressure regulating valve and the second control valve is opened. The vibration suppression device for a structure according to claim 1, wherein the second communication passage is composed of a plurality of communication holes penetrating in the axial direction of the piston. Further provided with a relative velocity detecting means for detecting the relative velocity between the first portion and the second portion due to the vibration of the structure.
The control means adjusts the flow rate having the pump according to the detected relative velocity so that the vibration damping force acting on the first and second portions via the cylinder and the piston becomes a predetermined value. The vibration suppression device for a structure according to claim 1 or 2, wherein the flow rate control for controlling the adjustment of the flow rate of the viscous fluid by a mechanism is executed. Further provided with a relative displacement detecting means for detecting a relative displacement between the first portion and the second portion due to vibration of the structure.
The control means started the flow amount control when the detected relative displacement became equal to or more than the predetermined displacement, and then the state in which the relative displacement was smaller than the predetermined displacement continued for the first predetermined time. At times, the flow amount control is terminated and
The predetermined displacement is set to such a size that the piston slides in a predetermined section inside the inner section when the relative displacement is smaller than the predetermined displacement during vibration of the structure. The vibration suppression device for a structure according to claim 3, wherein the device is characterized by the above. A piston position detecting means for detecting a piston position, which is a position of the piston in the cylinder, is further provided.
After the start of the flow amount control, the control means executes the flow amount control when the detected piston position is in the inner section, and when the piston position is in the outer section , the control means The vibration suppression device for a structure according to claim 4, wherein the flow amount control is stopped. A piston position detecting means for detecting a piston position, which is a position of the piston in the cylinder, is further provided.
After the start of the flow amount control, the control means executes the flow amount control when the detected piston position is in the inner section, and the piston position deviates from the inner section to the outer section. After that, the flow amount control is stopped, and the flow amount control is restarted when the state in which the piston position is in the inner section continues for the second predetermined time while the flow amount control is stopped. The vibration suppression device for a structure according to claim 4, characterized in that. A piston position detecting means for detecting a piston position, which is a position of the piston in the cylinder, is further provided.
After the start of the flow amount control, the control means executes the flow amount control when the detected piston position is in the inner section, and after the piston position is located in the outer section , When the flow amount control is stopped and the state in which the relative displacement is smaller than the predetermined displacement continues for the first predetermined time while the flow amount control is stopped, the stop of the flow amount control is released. The vibration suppression device for a structure according to claim 4, wherein the flow amount control is terminated.

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