JP2017187092A - Vibration suppression device for structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration suppression device for a structure capable of attaining a desired vibration control power when a vibration of the structure is relatively low and a larger vibration control power can be attained when the vibration of the structure is relatively high, and reducing the production cost.SOLUTION: A cylinder is connected to a first location, a piston slidably moving within the cylinder is connected to a second location, and an inside part of the cylinder is defined into a first fluid chamber and a second fluid chamber each filled with viscous fluid. When the piston is present in the inner space, the first communication passage is communicated with the first fluid chamber and the second fluid chamber, a fluid amount of viscous fluid flowing between the first communication passage and the first and second fluid chambers is adjusted by a flow rate adjustment mechanism and the flow rate adjustment mechanism is controlled by the control means. A second communication passage communicated with the first and second fluid chambers is closed by a first pressure adjustment valve when the pressure of the viscous fluid in the first fluid chamber is less than a first predetermined value, released when it reaches the first predetermined value, it is closed by a second pressure adjustment valve when a pressure of the viscous fluid in the second fluid chamber is less than a second predetermined value and it is released when it reaches a second predetermined value.SELECTED DRAWING: Figure 1

Description

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

  Conventionally, for example, a device disclosed in Patent Document 1 is known as a vibration suppressing device for this type of structure. This conventional vibration suppression device includes a semi-active fluid damper, a controller, and a sensor. The fluid damper is provided in a cylinder, in the cylinder so as to be slidable in the axial direction, and includes a piston that divides the inside of the cylinder into a pair of hydraulic chambers, an oil filled in the pair of hydraulic chambers, and a pair of hydraulic chambers Are connected to each other in parallel with a pair of inflow oil passages and outflow oil passages, and inflow oil passages and outflow oil passages. The above passive circuit is provided with a relief valve that opens when the oil pressure of the oil reaches a predetermined pressure, and an orifice, and the semi-active circuit is provided with an electric open / close control valve. In addition, the position of the piston in the cylinder is detected by the sensor, and the opening / closing operation of the opening / closing control valve is controlled by the 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 degree, thereby The pressed oil is caused to flow between a pair of hydraulic chambers via a semi-active circuit, thereby obtaining a damping force having a desired damping coefficient. Further, when the structure is vibrated greatly, the controller closes the open / close control valve, thereby causing the oil pressed by the piston to flow between the pair of hydraulic chambers via the passive circuit, A damping force having a larger damping coefficient is obtained. In this way, the fail-safe function for the semi-active circuit is made unnecessary by obtaining the damping force of the fluid damper using a passive circuit that does not require power supply when the structure vibrates.

JP 2004-125083 A

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

  The present invention has been made to solve the above-described problems, and obtains a desired damping force when the vibration of the structure is relatively small and a larger damping force when the vibration is relatively large. In addition, an object of the present invention is to provide a vibration suppressing device for a structure that can reduce manufacturing costs.

  In order to achieve the above object, the invention according to claim 1 is provided between the first part and the second part in the system including the structure, and the vibration of the structure for suppressing the vibration of the structure. A suppression device, which is connected to one of the first and second parts, and connected to the other of the first and second parts, and is slidably provided in the cylinder in the axial direction. A piston that is divided into a first fluid chamber and a second fluid chamber and is located at a predetermined neutral position in the cylinder when the structure is not vibrating; and a viscous fluid filled in the first and second fluid chambers; When the piston is located in a predetermined inner section including the neutral position, the piston is bypassed and communicated with the first and second fluid chambers, and the viscous fluid is between the first fluid chamber and the second fluid chamber. Provided in the first communication passage and the first communication passage, A flow rate adjusting mechanism for adjusting the flow rate of the viscous fluid flowing between the one communication path and the first and second fluid chambers, and a control means for controlling the adjustment of the flow rate of the viscous fluid by the flow rate adjusting mechanism; A second communication path that communicates with the first and second fluid chambers and causes the viscous fluid to flow between the first fluid chamber and the second fluid chamber; and a second communication path that is provided in the first fluid chamber. A first pressure regulating valve that closes the second communication path when the pressure of the viscous fluid is smaller than the first predetermined value and opens the second communication path when the pressure reaches the first predetermined value, and a second pressure control valve provided in the second communication path A second pressure regulating valve that closes the second communication path when the pressure of the viscous fluid in the second fluid chamber is smaller than a second predetermined value and opens the second communication path when the pressure reaches the second predetermined value; It is characterized by providing.

  According to this configuration, the cylinder is connected to one of the first and second parts in the system including the structure, and the piston is connected to the other of the first and second parts. The piston is provided in the cylinder so as to be slidable in the axial direction, and 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 located. The first and second fluid chambers are filled with a viscous fluid, and when the piston is located in a predetermined inner section including the neutral position, the first and second fluid chambers are disposed between the first fluid chamber and the second fluid chamber. A first communication passage for flowing the viscous fluid bypasses the piston and communicates with the first and second fluid chambers.

  Further, the first communication path is provided with a flow rate adjusting mechanism for adjusting the flow rate of the viscous fluid flowing between the first communication path and the first and second fluid chambers. The adjustment of the fluid flow rate is controlled by the control means. In addition, a second communication path for allowing the viscous fluid to flow between the first fluid chamber and the second fluid chamber communicates with the first and second fluid chambers, and the second communication path includes the first and second fluid paths. A second pressure regulating valve is provided. The first pressure regulating valve closes the second communication path when the pressure of the viscous fluid in the first fluid chamber is smaller than the first predetermined value, and opens the second communication path when the first predetermined value is reached. The Further, the second pressure control valve closes the second communication path when the pressure of the viscous fluid in the second fluid chamber is smaller than the second predetermined value, and when the pressure reaches the second predetermined value, the second communication path. Is released.

  As described above, the relative displacement between the first part and the second part generated with the vibration of the structure is transmitted to the cylinder and the piston, and thereby the piston slides in the cylinder. When the vibration of the structure is relatively small so that the piston slides in the inner section, as the viscous fluid flows between the first and second fluid chambers and the first communication path, A 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 flow amount of the viscous fluid flowing through the first communication path. Therefore, when the vibration of the structure is relatively small, the flow amount of the viscous fluid flowing between the first communication path and the first and second fluid chambers is controlled by the control means via the flow rate adjusting mechanism. A desired vibration damping force can be obtained.

  Further, when the vibration of the structure is relatively large, and the piston slides outside the inner section, the first communication path is not communicated with the first and second fluid chambers, and the viscous fluid is It does not flow between the second fluid chamber and the first communication path. 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 path is opened by the first pressure regulating valve, and the viscous fluid is the first and second fluids. It flows between the chamber and the second communication passage. In addition, when the pressure of the viscous fluid in the second fluid chamber pressed by the piston reaches the second predetermined value, the second communication path is opened by the second pressure regulating valve, and the viscous fluid is transferred to the first and second fluid chambers. And the second communication passage. As described above, a greater damping force can be obtained when the vibration of the structure is relatively large.

  Further, as described above, unlike the above-described conventional vibration suppression device, the semi-active circuit and the passive circuit are separated from each other without using a complicated hydraulic circuit connected in parallel to the inflow oil path and the outflow oil path. Since a simpler configuration including the first and second communication passages provided in 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 and / or the control means, the viscous fluid can be appropriately flowed between the first and second fluid chambers by the second communication path, and the abnormality is caused. Since the influence is limited only when the piston moves in the inner section, it is possible to prevent the vibration suppression device from being excessively and excessively reduced due to the abnormality, and damage to the structure due to the abnormality. Can be prevented.

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

  According to a second aspect of the present invention, in the vibration suppressing device for a structure according to the first aspect, the second communication path includes a plurality of communication holes penetrating in the axial direction of the piston.

  According to this configuration, since the plurality of communication holes penetrating in the axial direction of the piston are used as the second communication passage, it can be configured more simply than the case of using a communication passage of a type that bypasses the piston. Further, the manufacturing cost of the vibration suppressing device can be further reduced.

  The invention according to claim 3 is the structure vibration suppressing device according to claim 1 or 2, further comprising a relative speed detecting means for detecting a relative speed between the first part and the second part due to vibration of the structure. The control means includes a flow rate of the viscous fluid by the flow rate adjusting mechanism in accordance with the detected relative speed so that the damping force acting on the first and second portions via the cylinder and the piston becomes a predetermined value. The flow amount control for controlling the adjustment is performed.

  According to this configuration, the relative speed between the first part and the second part due to the vibration of the structure is detected by the relative speed detecting means, and is controlled on the first and second parts via the cylinder and the piston. Flow amount control (flow pressure control) for controlling adjustment of the flow amount of the viscous fluid by the flow rate adjustment mechanism is executed according to the detected relative speed 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 apparent from the above-described configuration. Therefore, when the piston slides in the inner section with 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 is the structure vibration suppressing device according to claim 3, further comprising a relative displacement detecting means for detecting a relative displacement between the first part and the second part due to vibration of the structure, The control means starts the flow amount control when the detected relative displacement becomes equal to or greater than the predetermined displacement, and then the flow amount when the state where the relative displacement is smaller than the predetermined displacement continues for the first predetermined time. The control is terminated, and the predetermined displacement is set to such a size 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 detection means, and the detected relative displacement during the vibration of the structure is equal to or greater than a predetermined displacement. When it becomes, flow amount control is started. In this case, the predetermined displacement is set to such a size 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, when the vibration of the structure is very small, and the relative displacement between the first part and the second part is smaller than the predetermined displacement, it is possible to prevent the flow amount control from being performed wastefully. . In addition, when the state in which the relative displacement is smaller than the predetermined displacement is continued for the first predetermined time after the flow amount control is started, the flow amount control is ended, so that the vibration of the structure is surely very small. The flow amount control can be ended after waiting. For the same reason, it is possible to prevent the execution and termination of the flow amount control from being repeated frequently.

  The invention according to claim 5 is the vibration suppressing device for a structure according to claim 4, further comprising piston position detecting means for detecting a piston position which is a position of the piston in the cylinder, wherein the control means is a flow amount control. After the start, 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 outside the inner 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 includes the first communication passage and the first and second fluid chambers. The amount of viscous fluid flowing between the two is adjusted. For this reason, the adjustment of the damping force by the flow amount control of the control means can be performed only when the piston slides in the inner section. According to the above-described configuration, when 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 started after the start, the detected piston position is in the inner section. And is stopped when the piston position is outside the inner section. Therefore, energy used for flow rate control can be saved.

  The invention according to claim 6 is the vibration suppression device for a structure according to claim 4, further comprising piston position detection means for detecting a piston position which is a position of the piston in the cylinder, wherein the control means is a flow amount control. When the detected piston position is in the inner section, the flow amount control is executed.After the piston position deviates from the inner section, the flow amount control is stopped and the flow amount control is stopped. When the state where the piston position is in the inner section continues for the second predetermined time, the flow amount control is resumed.

  As described in the description of the invention according to claim 5, the adjustment of the damping force by the flow amount control of the control means can be performed only when the piston slides 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 detection means. In addition, after the flow amount control is started, when the detected piston position is in the inner section, the flow amount control is executed, and after the piston position is out of the inner section, the flow amount control is stopped, While the flow amount control is stopped, the flow amount control is resumed when the state where the piston position is in the inner section continues for the second predetermined time.

  Thereby, 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, waiting for the vibration of the structure to be reliably reduced, Since the flow amount control can be resumed, the energy used for the flow amount control can be sufficiently saved. For the same reason, it is possible to prevent the flow amount control from being repeatedly executed and stopped.

  The invention according to claim 7 is the vibration suppression device for a structure according to claim 4, further comprising piston position detection means for detecting a piston position which is a position of the piston in the cylinder, wherein the control means is a flow amount control. When the detected piston position is within the inner section after the start of the flow, the flow amount control is executed, and after the piston position is located outside the inner section, the flow amount control is stopped and the flow amount control is stopped. In addition, when the state where the relative displacement is smaller than the predetermined displacement continues for the first predetermined time, the stop of the flow amount control is canceled and the flow amount control is ended.

  As described in the description of the invention according to claim 5, the adjustment of the damping force by the flow amount control of the control means can be performed only when the piston slides 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 detection means. Further, after the flow amount control is started, when the detected piston position is in the inner section, the flow amount control is executed, and after the piston position is located outside the inner section, 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 while the flow amount control is stopped, the stop of the flow amount control is released and the flow amount control is ended.

  Thereby, 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 this stopped state is described in the description of the invention according to claim 4. Since the flow amount control is continued until the end condition of the flow amount control is satisfied, that is, until the vibration of the structure is surely very small, energy used for the flow amount control can be sufficiently saved. For the same reason, it is possible to prevent the flow amount control from being repeatedly executed and stopped. In addition, since the stop of the flow amount control is released with the end of the flow amount control, the flow amount control is executed again when the relative displacement becomes greater than or equal to a predetermined displacement due to the vibration of the structure increasing again. can do.

It is sectional drawing which shows the vibration suppression apparatus by 1st Embodiment of this invention. It is sectional drawing which follows the II-II line of FIG. It is a block diagram which shows the control apparatus etc. of the vibration suppression apparatus of FIG. It is a figure which shows roughly the vibration suppression apparatus of FIG. 1 with a part of building which applied this. It is a flowchart which shows the process performed with the control apparatus of FIG. It is a flowchart which shows the process different from FIG. 5 performed with the control apparatus of FIG. FIG. 5 is a diagram illustrating an example of the relationship between the relative displacement between beams and the damping force in the building and the vibration suppressing device of FIG. 4 when the vibration of the building is relatively small. FIG. 5 is a diagram illustrating an example of the relationship between the relative displacement between beams and the damping force in the building and the vibration suppression device of FIG. It is a flowchart which shows the process performed with the control apparatus of the vibration suppression apparatus by 2nd Embodiment of this invention. 10 is a flowchart showing a continuation of FIG. 9. It is a flowchart which shows the process different from FIG.9 and FIG.10 performed with the control apparatus of the vibration suppression apparatus by 2nd Embodiment of this invention. It is a flowchart which shows a part of process performed with the control apparatus of the vibration suppression apparatus by 3rd Embodiment of this invention. It is a flowchart which shows a part of process performed with the control apparatus of the vibration suppression apparatus by 4th Embodiment of this invention. It is sectional drawing which shows the modification of a 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 suppressing device 1 according to a first embodiment of the present invention. The vibration suppression device 1 is configured as a so-called active fluid damper, and includes a cylinder 2, a piston 3 provided in the cylinder 2 so as to be slidable in an axial direction, a piston rod 4 integral with the piston 3, A communication path 5 connected to the cylinder 2 and a flow rate adjusting mechanism 6 provided in the communication path 5 are provided. The cylinder 2 has a cylindrical peripheral wall 2a, and disk-shaped first and second side walls 2b and 2c that are integrally and concentrically provided at one end and the other end in the axial direction of the peripheral wall 2a. Yes. A space defined by the peripheral wall 2a, the first and second side walls 2b, 2c is partitioned by the piston 3 into a first fluid chamber 2d and a second fluid chamber 2e. The first and second fluid chambers 2d and 2e are filled with a viscous fluid HF. The viscous fluid HF is made of, for example, silicon oil.

  Further, the first side wall 2b of the cylinder 2 is integrally provided with a convex portion 2f that protrudes outward in the axial direction, and the first mounting portion is connected to the convex portion 2f via a universal joint. A tool FL1 is provided. Furthermore, a rod guide hole 2g penetrating in the axial direction is formed at the radial center of the second side wall 2c. One end of the piston rod 4 is attached to the piston 3 and is partially accommodated in the cylinder 2 so as to be movable in the axial direction. The piston rod 4 is inserted into the rod guide hole 2g via a seal and has a second side wall. 2c extends outward. The other end of the piston rod 4 is provided with a second fixture FL2 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 through a seal, and a plurality of first holes penetrating in the axial direction are provided at the radially outer end of the piston 3. A communication hole 3a and a second communication hole 3b (only one is shown) are formed. A first pressure regulating valve 15 is provided in the first communication hole 3a, and a second pressure regulating valve 16 is provided in the second communication hole 3b.

  The first pressure regulating valve 15 includes a valve body and a spring that biases the valve body in a 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 When the communication hole 3a is closed and reaches a predetermined value, 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. Similar to the first pressure regulating valve 15, the second pressure regulating valve 16 includes a valve body and a spring that urges the valve body in the valve closing direction. The pressure of the viscous fluid HF in the second fluid chamber 2e is predetermined. When 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.

  The piston 3 is provided with a first relief valve and a second relief valve (both not shown). By these first and second relief valves, the pressure of the viscous fluid HF in the first and second fluid chambers 2d and 2e is restricted so as not to exceed a predetermined upper limit value larger than the predetermined value. .

  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. Connected to the cylinder 2. In the cylinder 2, predetermined outer sections INO and INO are provided on both outer sides in the axial direction of the inner section INI. In addition, 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 from that of the first and second communication holes 3a and 3b of the piston 3. Is also set to a large value. Furthermore, the communication path 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 using an electric motor 7 as a power source. The gear pump is of a circumscribed gear type, and includes a casing 8 and a first gear 9 and a second gear 10 accommodated in the casing 8. An internal gear type gear pump may be used. The casing 8 is integrally provided in the central portion of the communication path 5, and the inside thereof communicates with the communication path 5 via two entrances 8 a and 8 b facing each other.

  The first gear 9 is a spur gear, and is provided integrally with the first rotating shaft 11. The first rotating shaft 11 extends horizontally in a direction orthogonal to the communication path 5, is rotatably supported by the casing 8, and slightly protrudes outside the casing 8 (see FIG. 2). Similar to the first gear 9, the second gear 10 is configured by a spur gear, is provided integrally with the second rotating shaft 12, and meshes with the first gear 9. The second rotating shaft 12 extends in parallel with 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 8 a and 8 b of the casing 8.

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

  For example, as shown in FIG. 4, the vibration suppressing device 1 having the above configuration includes a joint portion between the upper beam BU and the left column PL of the high-rise building B, and a joint portion between the upper beam BU and the right column PR of the building B. Are connected via a connecting member EN to a joint portion of the lower beam BD of the building B and the right column PR. In this case, the first fixture FL1 is attached to the lower end of the brace material BR, the second fixture FL2 is attached to the connecting member EN, and the vibration suppressing 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. Moreover, when the building B is not vibrating, the piston 3 is in the neutral position shown in FIG. In FIG. 4, illustration of the communication path 5 and the flow rate adjusting mechanism 6 is omitted for convenience. Moreover, you may provide a left-right paired vibration suppression apparatus symmetrically centering | focusing on the brace material BR.

  Furthermore, in the vibration suppression device 1, when a relative displacement occurs in the left-right direction between the upper and lower beams BU, BD due to the vibration of the building B, the 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, The part flows through the communication path 5 to the second fluid chamber 2e side. On the contrary, when the piston 3 slides toward the second side wall 2c of the cylinder 2 (when the vibration suppressing device 1 extends), the viscous fluid HF in the second fluid chamber 2e is pressed by the piston 3. A part of the fluid flows through the communication passage 5 toward the first fluid chamber 2d.

  As apparent from the above operation, during the vibration of the building B, the 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 2 and the piston rod 4 to act to suppress the vibration of the building B. 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 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 measure acceleration caused by vibration of the upper beam BU (hereinafter referred to as “upper beam vibration acceleration”) ACBU and acceleration caused by vibration of the lower beam BD (hereinafter referred to as “lower beam vibration acceleration”) ACBD. 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 accordance with the detection signals of the first and second acceleration sensors 23 and 24.

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

  In step 1, the upper beam vibration velocity VBU is calculated as a positive value (+) when the upper beam BU is moving rightward in FIG. 4 due to vibration, and is negative (−) when moving leftward. ). The same applies to the lower beam vibration velocity VBD. In step 3 following step 2, the 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 above.

  Next, by integrating the upper beam vibration velocity VBU, an upper beam absolute displacement DBU that is an absolute displacement (displacement in the absolute coordinate system) of the upper beam BU due to vibration is calculated (step 4). Next, the lower beam absolute displacement DBD, which is the absolute displacement of the lower beam BD due to vibration, is calculated by integrating the lower beam vibration velocity VBD (step 5). In step 4, the upper beam absolute displacement DBU is calculated as a positive value (+) when the upper beam BU is displaced from the neutral position to the right in FIG. 4 due to vibration, and negative when it is displaced to the left. Calculated to a value (-). The same 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 a predetermined displacement DREF (Step 7). The predetermined displacement DREF is set to such a size that the piston 3 slides in a predetermined section inside the inner section INI when | REDB | <DREF during 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 in a size that can be recognized by a person in the building B is, for example, 1 mm.

  When the answer to 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 represents that the execution condition of the flow amount control is satisfied by “1”, and is initialized to “0” when the control device 21 is activated. If the answer to step 8 is NO (F_CONT = 0), the process ends.

  On the other hand, if the answer to step 7 is YES (| REDB | ≧ DREF), the timer value tM1 of the up-counting first timer is initialized to the value 0 (step 9), and the flow amount control execution flag F_CONT is “ It is determined whether it is “1” (step 10). When the answer to step 10 is NO (F_CONT = 0), the answer to step 7 is YES, and the flow amount control execution flag F_CONT is set to indicate that the flow amount control execution condition is satisfied. “1” is set (step 11), and this process is terminated. On the other hand, when the answer to step 10 is YES (F_CONT = 1), step 11 is skipped and the process is terminated. 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, if the answer to 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 equal to or longer than a first predetermined time TREF1 (for example, 10 sec). (Step 12). When this answer is NO (tM1 <TREF1), this process is finished as it is.

  On the other hand, when the answer to step 12 is YES (tM1 ≧ TREF1), that is, after the flow amount control is started as | REDB | ≧ DREF is satisfied, | REDB | <DREF When the state continues for the first predetermined time TREF1, 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 ends.

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

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

  In this step 23, the flow amount control is executed as follows. When the sign of the relative speed REVB between the beams 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 both BU and BD is changed. The flow amount of the viscous fluid HF flowing through the communication path 5 is such that the 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 omitted as appropriate.

  Since the damping force of the vibration suppressing device 1 is based on the viscous fluid HF, the smaller the input relative beam speed REVB is, the smaller it is. Therefore, in order to apply the damping force of the predetermined value FREF, the communication path The flow amount of the viscous fluid HF in 5 is adjusted to be smaller (so that the viscous fluid HF is less likely to flow). In this case, when the relative speed REVB between the beams is relatively large, the flow amount of the viscous fluid HF in the communication path 5 is adjusted by controlling the regeneration (power generation) of the electric motor 7. Further, when the input relative speed REVB between the beams is relatively small, by controlling the powering (power supply) of the electric motor 7, the piston 3 is moved in the direction opposite to the sliding direction of the piston 3 by the input of the relative speed REVB between the beams. The flow amount of the viscous fluid HF in the communication passage 5 is adjusted so as to slide.

  FIG. 7 shows the relationship between the inter-beam relative displacement REDB and the damping force FD of the vibration suppressing device 1 when the piston 3 slides in the inner section INI. In FIG. 7, a section (| + DPIN | = | −DPIN |) defined by a predetermined value + DPIN and a predetermined value −DPIN corresponds to the inner section INI, and + FMAX (−FMAX) is a value of the damping force FD. It is the maximum value. In the following description, “+” and “−” of the predetermined value + DPIN (−DPIN) and the maximum value + FMAX (−FMAX) are omitted as appropriate.

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

  FIG. 8 shows the relationship between the inter-beam relative displacement REDB and the damping force FD of the vibration suppressing device 1 when the piston 3 slides in the inner section INI and the outer section INO. When the piston 3 slides in the outer section INO (REDB> + DPIN, REDB <−DPIN), the communication path 5 does not communicate with the first and second fluid chambers 2d, 2e. The viscous fluid HF in the two fluid chambers 2d and 2e passes through the first and second communication holes 3a and 3b in accordance with the opening of the first and second pressure regulating valves 15 and 16, respectively. It flows into the chambers 2e and 2d. Thereby, when the piston 3 slides in the outer section INO, the vibration suppressing device 1 functions as a so-called passive damper. As a result, when the piston 3 slides in the inner section INI and the outer section INO and the inter-beam relative speed REVB is relatively small, the damping force FD changes as indicated by a thick solid line and an arrow.

  Further, when the piston 3 slides in the inner section INI and the outer section INO and the relative speed REVB between the beams is very large, the flow amount of the viscous fluid HF in the communication passage 5 is adjusted by the flow amount control. However, because of the configuration of the flow rate adjusting mechanism 6, the damping force FD cannot be controlled to the predetermined value + FREF (−FREF), and the pressure of the viscous fluid HF in the first and second fluid chambers 2d and 2e is The upper limit is reached by the restriction by the first and second relief valves. For this reason, in this case, the damping force FD becomes the maximum value + FMAX (−FMAX), and changes as indicated by a thick one-dot chain line and an 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. The piston 3 is provided in the cylinder 2 so as to be slidable in the axial direction, and the cylinder 2 is partitioned into a first fluid chamber 2d and a second fluid chamber 2e, and when the building B is not vibrating, the cylinder 2 It is located in a predetermined neutral position (see FIG. 1). The first and second fluid chambers 2d and 2e are filled with the viscous fluid HF, and when the piston 3 is located in a predetermined inner section INI including the neutral position, A communication path 5 for allowing the viscous fluid HF to flow between the second fluid chambers 2e bypasses the piston 3 and communicates with the first and second fluid chambers 2d and 2e.

  Further, the flow rate adjusting mechanism 6 described above is provided in the communication path 5, and the adjustment of the flow amount of the viscous fluid HF by the flow rate adjusting mechanism 6 is controlled by the control device 21. The piston 3 is formed with first and second communication holes 3a and 3b penetrating in the axial direction. 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 connected to both the communication holes 3a and 3b. Is provided.

  As described above, the inter-beam relative displacement REDB between the upper and lower beams BU and BD generated along with 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. When the vibration of the building B is relatively small so that the piston 3 slides in the inner section INI, the viscous fluid HF flows between the first and second fluid chambers 2d, 2e and the communication passage 5. Accordingly, a 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 flow amount of the viscous fluid HF flowing through the communication path 5. Therefore, when the vibration of the building B is relatively small, the flow amount of the viscous fluid HF flowing between the communication passage 5 and the first and second fluid chambers 2d and 2e is controlled via the flow rate adjusting mechanism 6. 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 slides outside the inner section INI, that is, 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, 2e and the communication path 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 the first fluid. The fluid 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 becomes the first and first fluids. The fluid flows between the two fluid chambers 2d and 2e and the second communication hole 3b. As described above, a relatively large damping force can be obtained when the vibration of the building B is large.

  Further, as described above, unlike the above-described conventional vibration suppression device, the semi-active circuit and the passive circuit are separated from each other without using a complicated hydraulic circuit connected in parallel to the inflow oil path and the outflow oil path. Since a simpler structure including the communication path 5 and the first and second communication holes 3a and 3b provided in the first and second communication holes is used, the manufacturing cost of the vibration suppressing device 1 can be reduced. Even when an abnormality occurs in the flow rate adjusting mechanism 6 and / or the control device 21, the viscous fluid HF is caused to flow between the first and second fluid chambers 2d and 2e through the first and second communication holes 3a and 3b. Since the fluid can be properly flowed and the influence of the abnormality is limited only when the piston 3 is moving in the inner section INI, the vibration damping force FD of the vibration suppressing device 1 due to the abnormality is excessive. In addition, it is possible to prevent under-sizing and damage to the building B due to the abnormality.

  In addition, since the first and second communication holes 3a and 3b are used as the second communication path in the present invention, the second communication path can be configured more simply than the case where the communication path of the type bypassing the piston 3 is used. The manufacturing cost of the vibration suppression device 1 can be further reduced.

  Further, the relative velocity REVB between the beams, 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-described flow rate control is performed according to the relative velocity REVB between the beams. Is executed (step 23 in FIG. 6). Thus, when the piston 3 slides in the inner section INI with the vibration of the building B, the damping force FD acting on the building B is set to the predetermined value FREF according to the beam relative speed REVB. Can be controlled.

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

  Further, after the flow amount control is started, 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 is ended (step) 13, step 21 of FIG. 6: NO, step 22), so that the flow amount control can be ended after waiting for the vibration of the building B to become very small reliably. For the same reason, it is possible to prevent the execution and termination of the flow amount control from being repeated frequently.

  Further, since the damping force FD of the vibration suppressing 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 damping force FD to the upper and lower beams BU and BD. It is sufficient that the rigidity of the member EN is set so as to satisfy the short-term allowable stress level with respect to the maximum value FMAX of the damping force FD, and the rigidity of the brace material BR and the connecting member EN is set as such. Thus, the cross-sectional areas of the brace material BR and the connecting member EN can be reduced.

  Next, a vibration suppressing device according to a second embodiment of the present invention will be described with reference to FIGS. This vibration suppressing device is different from the first embodiment only in the execution contents of the processing executed by the control device 21. 9 to 11, the same execution contents as those in the first embodiment are denoted by the same reference numerals. Hereinafter, a description will be given focusing on differences from the first embodiment.

  In FIG. 9, step 31 is executed following step 6. In this step 31, a 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 the above step 6. Next, Step 7 and subsequent steps in FIG. 10 are executed. The above map is a map obtained by experimentally determining the relationship between the inter-beam relative displacement REDB and the piston position POPI in consideration of the deformation rigidity of the brace material BR accompanying the vibration of the building B. As a result, the piston position POPI is calculated as a value 0 for the neutral position described above, and is a positive value (+) when it is closer to the first side wall 2b than the neutral position, and a negative value (when it is closer to the second side wall 2c). -), Respectively.

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

  When the answer to 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). This 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 to step 42 is NO (F_STOP = 0), the present process ends.

  Also, when the answer to step 12 in FIG. 10 is NO (tM1 <TREF1), that is, after starting the flow rate control, the state where | REDB | <DREF does not continue for the first predetermined time TREF1. Sometimes step 42 is executed. As is clear from the setting of the predetermined displacement DREF described above, when the answer to step 7 is NO and | REDB | <DREF, the piston 3 is located in the inner section INI.

  On the other hand, if the answer to 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 1). 43) The process is terminated.

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

  FIG. 11 shows a process for executing the flow amount control according to the second embodiment. When the answer to the step 21 in FIG. 11 is YES (F_CONT = 1), the step 43 in FIG. It is determined whether or not the stop flag F_STOP set at 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, if the answer to step 51 is NO (F_STOP = 0), the process is terminated after executing the step 23 and performing the flow amount control.

  As described above, according to the second embodiment, the piston position POPI that 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 within the inner section INI after the start (step 41: YES, step 7: NO, step 12: NO, step 42, step 44, FIG. 10). Step 51 in FIG. 11: NO, Step 23), and stop when the piston position POPI is outside the inner section INI (Step 41 in FIG. 10: NO, Step 43, Step 51 in FIG. 11: YES, Step 22) . Therefore, it is possible to save electric energy used for flow rate control.

  Next, a vibration suppression device according to a third embodiment of the present invention will be described with reference to FIG. This vibration suppression device is different from the second embodiment only in the execution contents of processing for setting various parameters executed by the control device 21. In FIG. 12, the same reference numerals are assigned to the same execution contents as those in the first and second embodiments. The following description will focus on differences from the first and second embodiments.

  When the answer to step 41 in FIG. 12 is NO (| POPI |> POREF), the timer value tM2 of the up-counting type second timer is initialized to 0 (step 61). Next, step 43 is executed, and after setting the stop flag F_STOP to “1”, this process is terminated.

  If the answer to step 42 in 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 equal to the second predetermined time TREF2. It is determined whether or not this is the case (step 62). The second predetermined time TREF2 is set to a value equal to or shorter than the first predetermined time TREF1, and is, for example, 5 seconds.

  When the answer to step 62 is NO (tM2 <TREF2), this process ends. On the other hand, when the answer to step 62 is YES, that is, when the state of | POPI | ≦ POREF (the state where the piston 3 is in the inner section INI) continues for the second predetermined time TREF2 while the flow amount control is stopped. Then, in order to cancel the stop of the flow amount control and restart the flow amount control, the step 44 is executed, and after setting the stop flag F_STOP to “0”, the present process is ended.

  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 in FIG. 11: NO, step 23), and stop when the piston position POPI is outside the inner section INI (step 41 in FIG. 12: NO, step 43, FIG. 11) Step 51: YES, Step 22).

  Further, when the flow amount control is stopped (step 42 in FIG. 12: YES), the flow amount is maintained when the piston position POPI remains in the inner section INI for the second predetermined time (step 62: YES). Control is resumed (step 44, step 51 in FIG. 11: NO, step 23). Thereby, 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. Thus, since the flow amount control can be resumed, the electric energy used for the flow amount control can be sufficiently saved. For the same reason, it is possible to prevent the flow amount control from being repeatedly executed and stopped. When the flow rate control is stopped (when the stop condition is satisfied; stop flag F_STOP = 1) and the piston 3 is moving in the inner section INI, the electric motor 7 generates power. The power source 22 may be charged.

  Next, a vibration suppressing device according to a fourth embodiment of the present invention will be described with reference to FIG. This vibration suppression device is different from the second embodiment only in the execution contents of processing for setting various parameters executed by the control device 21. In FIG. 13, the same reference numerals are given to the same execution contents as those in the first and second embodiments. The following description will focus on differences from the first and second embodiments.

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

  On the other hand, when the answer to step 71 is NO (F_STOP = 0), the step 41 is executed. If the answer to step 41 is YES (| POPI | ≦ POREF), the present process ends.

  If the answer to step 12 in FIG. 13 is NO (tM1 <TREF1), this process ends.

  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, when the piston position POPI is within the inner section INI, the flow amount control is executed (step 71 in FIG. 13: NO, step 41: YES, step 51 in FIG. 11: NO, 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: FIG. 11: YES, step 22). Furthermore, when the flow amount control is stopped and the absolute value | REDB | of the relative displacement between the beams is smaller than the predetermined displacement DREF for the first predetermined time TREF1 (step 12 in FIG. 13: YES), the flow amount The stop of the control is released (step 44), and the flow amount control is ended (step 13, step 21 in FIG. 11: NO, step 22).

  Thereby, 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 this stopped state is changed to the flow amount according to the step 12 described above. Since the control is continued until the control end condition is satisfied, that is, until the vibration of the building B is surely very small, the electric energy used for the flow rate control can be sufficiently saved. For the same reason, it is possible to prevent the flow amount control from being repeatedly executed and stopped. In addition, since the stop of the flow amount control is released with the end of the flow amount control, the absolute value | REDB | of the relative displacement between the beams becomes equal to or greater 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 rate control is stopped and the piston 3 is moving in the inner section INI, the electric motor 7 generates power and the power source 22 may be charged. .

  The present invention is not limited to the described first to fourth embodiments (hereinafter collectively referred to as “embodiments”), and can be implemented in various modes. For example, in the embodiment, the viscous fluid HF made of silicon oil is used, but other appropriate viscous fluid may be used. In the embodiment, the communication path 5 connected to the cylinder 2 is used, but a communication path formed in the peripheral wall 2 a 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 path in the present invention, but the piston is bypassed and the communication path connected to the cylinder and the peripheral wall of the cylinder are used. You may use the formed communicating path.

  In the embodiment, the flow rate adjustment mechanism 6 having a gear pump is used as the flow rate adjustment mechanism in the present invention. However, another appropriate mechanism, for example, a flow rate adjustment mechanism having the piston mechanism 31 shown in FIG. 14 is used. May be. The piston mechanism 31 is the same as that disclosed in FIG. 5 and the like of Japanese Patent Application No. 2015-147612 by the applicant of the present invention, and a detailed description thereof will be omitted. When a flow rate adjustment mechanism having the piston mechanism 31 is used, as shown in FIG. 14 and as disclosed in FIG. 5 of Japanese Patent Application No. 2015-147612, the movement of the piston of the piston mechanism 31 is performed. In order to ensure a sufficient range, the communication path 32 is configured such that a portion extending in parallel with the cylinder 2 is relatively long. Alternatively, as a 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 or FIGS. 2 and 5, and an on-off valve for opening and closing the first communication passage Etc. may be used. When this on-off valve is used as the flow rate adjusting mechanism, the vibration suppressing device is configured as a so-called semi-active type fluid damper.

  Furthermore, in the embodiment, the pressures of the viscous fluids HF at which the first and second pressure regulating valves 15 and 16 are opened are set to the same predetermined value, but the first predetermined value and the second predetermined value are different from each other. Each may be set.

  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 speed REVB, but may be controlled according to the inter-beam relative displacement REDB, and in this case, the inter-beam relative displacement REDB becomes a value of 0. As described above, the flow rate adjusting mechanism 6 may be controlled using a feedback control algorithm. Furthermore, in the embodiment, the inter-beam relative speed REVB is calculated, but may be detected by a sensor. The same applies to the inter-beam relative displacement REDB and the piston position POPI.

  In the embodiment, the cylinder 2 is connected to the upper beam BU and the piston 3 is connected to the lower beam BD. 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 linked. Further, in the embodiment, the upper beam BU and the lower beam BD are adopted as the first and second parts in the present invention to suppress the interlayer displacement between the two layers, but other suitable parts are adopted. Also good. For example, upper and lower beams provided with one or more beams between each other may be employed to suppress interlayer displacement between three or more layers. Moreover, as a 1st and 2nd site | part, you may employ | adopt the beam of the lower layer part of a structure, and the beam of an upper layer part, respectively.

  In the embodiment, the vibration suppressing device 1 is provided so as to suppress vibration in the left-right direction of the building B, but may be provided so as to suppress vibration in the front-rear direction and vibration in the vertical direction. Furthermore, in the embodiment, the structure in the present invention is a high-rise building B, but may be another appropriate structure such as a steel tower or a bridge. It goes without saying that variations relating to the above embodiments may be applied in appropriate combination. 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)
DESCRIPTION OF SYMBOLS 1 Vibration suppression apparatus 2 Cylinder 2d 1st fluid chamber 2e 2nd fluid chamber INI Inner area 3 Piston 3a 1st communicating hole (2nd communicating path)
3b Second communication hole (second communication passage)
5 communication path (first communication path)
6 Flow adjustment mechanism HF Viscous fluid 15 First pressure regulating valve 16 Second pressure regulating valve 21 Control device (control means, relative speed detection means, relative displacement detection means, piston position detection means)
REVB Relative speed between beams (relative speed)
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 vibration suppressing device for a structure, which is provided between a first part and a second part in a system including a structure, for suppressing vibration of the structure,
A cylinder coupled to one of the first and second portions;
The cylinder is connected to the other of the first and second portions and is slidably provided in the cylinder in the axial direction. The cylinder is divided into a first fluid chamber and a second fluid chamber, and the structure vibrates. A piston located at a predetermined neutral position in the cylinder when not
A viscous fluid filled in the first and second fluid chambers;
When the piston is located in a predetermined inner section including the neutral position, the piston is bypassed and communicated with the first and second fluid chambers, and the first fluid chamber and the second fluid chamber A first communication path for flowing a viscous fluid between
A flow rate adjusting mechanism provided in the first communication path, for adjusting the flow rate of the viscous fluid flowing between the first communication path and the first and second fluid chambers;
Control means for controlling adjustment of the flow rate of the viscous fluid by the flow rate adjusting mechanism;
A second communication path that communicates with the first and second fluid chambers and causes a viscous fluid to flow between the first fluid chamber and the second fluid chamber;
The second communication path is provided in the second communication path, and the second communication path is closed when the pressure of the viscous fluid in the first fluid chamber is smaller than a first predetermined value, and when the pressure reaches the first predetermined value, the second communication path is closed. A first pressure regulating valve that opens the two communication passages;
The second communication path is provided in the second communication path, and the second communication path is closed when the pressure of the viscous fluid in the second fluid chamber is smaller than a second predetermined value, and the second communication path is closed when the second predetermined value is reached. And a second pressure regulating valve that opens the two communication passages.   2. The structure vibration suppressing device according to claim 1, wherein the second communication path includes a plurality of communication holes penetrating in the axial direction of the piston. A relative speed detecting means for detecting a relative speed between the first part and the second part due to vibration of the structure;
The control means has a viscosity by the flow rate adjusting mechanism according to the detected relative speed so that a damping force acting on the first and second parts via the cylinder and the piston becomes a predetermined value. The vibration suppression device for a structure according to claim 1 or 2, wherein flow amount control for controlling adjustment of a flow amount of fluid is executed. A relative displacement detecting means for detecting a relative displacement between the first part and the second part due to vibration of the structure;
The control means starts the flow amount control when the detected relative displacement becomes equal to or greater than a predetermined displacement, and thereafter, the state in which the relative displacement is smaller than the predetermined displacement continues for a first predetermined time. Sometimes, the flow amount control is finished,
The predetermined displacement is set to a size such 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 structure vibration suppression device according to claim 3, wherein the vibration suppression device is a structure. A piston position detecting means for detecting a piston position which is a position of the piston in the cylinder;
The control means executes the flow amount control when the detected piston position is within the inner section after the start of the flow amount control, and when the piston position is outside the inner section, 5. The structure vibration suppressing device 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;
The control means executes the flow amount control when the detected piston position is within the inner section after the start of the flow amount control, and after the piston position deviates from the inner section, The flow amount control is stopped, and the flow amount control is resumed when the state where the piston position is in the inner section continues for a second predetermined time during the stop of the flow amount control. The structure vibration suppression device according to claim 4. A piston position detecting means for detecting a piston position which is a position of the piston in the cylinder;
The control means executes the flow amount control when the detected piston position is within the inner section after the start of the flow amount control, and after the piston position is located outside the inner section. The flow amount control is stopped, and the stop of the flow amount control is released when the state in which the relative displacement is smaller than the predetermined displacement continues for the first predetermined time during the stop of the flow amount control. At the same time, the flow amount control is terminated, and the structure vibration suppressing device according to claim 4.

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