JP6824585B2 - Vibration suppression device for structures - Google Patents

Description

The present invention relates to a structure vibration suppressing device that is connected to predetermined first and second parts in a system including a structure to suppress the vibration of the structure.

Conventionally, as a vibration suppression device for this type of structure, for example, one disclosed in Patent Document 1 is known. This vibration suppression device is applied to high-rise buildings, and is installed around a building with a rotary inertial mass damper having a rotating mass, a rigid member integrally provided at the top of the building, and a building. It is equipped with an axial force member. The axial force member extends in the vertical direction from the top to the bottom of the building and is relatively long. The rotary inertia mass damper is connected to the rigid member and the axial force member, and constitutes an additional vibration system together with the axial force member.

In the conventional vibration suppression device having the above-described configuration, the bending deformation (displacement) accompanying the vibration of the primary mode of the building is transmitted to the rotational inertia mass damper via the rigid member and the axial force member. As a result, the rotating mass of the rotating inertial mass damper rotates, so that a relatively large inertial force due to the rotating inertial mass of the rotating mass is generated as a reaction force of the rotating inertial mass damper, and the vibration of the building is suppressed.

Patent No. 5190652

As is clear from the configuration of the conventional vibration suppression device described above, the reaction force of the rotational inertia mass damper generated by the vibration of the structure repeatedly acts on the axial force member in the compression direction and the tension direction. The reaction force acting in the compression direction may cause the axial force member to buckle, and in that case, the vibration of the structure cannot be appropriately suppressed. Such a defect becomes particularly remarkable when the axial force member is relatively long as described above.

The present invention has been made to solve the above problems, and by reducing the reaction force due to the rotational inertial mass of the rotating mass when the rotational inertial mass damper contracts due to the vibration of the structure. An object of the present invention is to provide a structure vibration suppressing device capable of preventing the connecting member from buckling and, by extension, appropriately suppressing the vibration of the structure.

In order to achieve the above object, the invention according to claim 1 includes a rotary inertial mass damper and a connecting member, and is connected to predetermined first and second parts in a system including a structure to form a structure. A vibration suppression device for a structure for suppressing vibration, a rotary inertial mass damper is provided in a cylinder filled with a working fluid and connected to a first portion and slidably in the cylinder in the axial direction. , The piston that divides the inside of the cylinder into the first fluid chamber and the second fluid chamber is connected to the piston, extends outward from the cylinder in the axial direction via the second fluid chamber, and is connected to the second portion. A piston rod is provided, and the connecting member is provided in series between the first portion and the cylinder and at least one between the second portion and the piston rod, extends in the axial direction of the cylinder, and has a rotational inertia mass. The damper also bypasses the piston and communicates with the first and second fluid chambers, as well as a first passage filled with working fluid, a rotatable rotary mass, and the flow of working fluid in the first passage. A flow conversion mechanism that converts the piston into the rotational motion of the rotating mass, a second passage that is provided in parallel with the first passage, communicates with the first and second fluid chambers, and is filled with a working fluid, and a first A valve for the first communication passage, which is provided in the communication passage and allows the flow of the working fluid from the second fluid chamber to the first communication passage and limits the flow of the working fluid from the first fluid chamber to the first communication passage. , And, when the piston slides toward the first fluid chamber, the working fluid is always allowed to flow from the first fluid chamber to the second passage, and the piston is the second fluid. It is equipped with at least one of the valves for the second passage that always limits the flow of the working fluid from the second fluid chamber to the second passage when sliding to the chamber side, and is a rotary inertial mass damper due to the vibration of the structure. The reaction force of the rotary inertial mass damper due to the rotary inertial mass of the rotary mass is smaller than the reaction force when the rotary inertial mass damper is extended over the entire stroke of the piston in the cylinder. And.

According to this configuration, between the first part in the system including the structure and the cylinder of the rotary inertia mass damper connected to the first part, and the second part in the system including the structure, and the second part. A connecting member extending in the axial direction of the cylinder is provided in series with at least one of the piston rods of the rotary inertial mass damper connected to the two portions. The relative displacement between the first part and the second part due to the vibration of the structure is transmitted to the cylinder and the piston rod via the connecting member, whereby the piston connected to the piston rod slides in the cylinder. ..

Further, when the vibration suppression device is provided with the valve for the first communication passage and is not provided with the valve for the second communication passage (hereinafter, the vibration suppression device in this case is referred to as the "first vibration suppression device"). When the piston slides in the cylinder due to the vibration of the structure and moves to the second fluid chamber side, the working fluid in the second fluid chamber is pressed by the piston toward the first and second passages. As a result, the flow of the working fluid toward the first fluid chamber side is generated in the first and second communication passages. The flow of the working fluid in the first continuous passage is converted into the rotational motion of the rotating mass by the flow conversion mechanism, and the rotating mass is rotated by this, so that a reaction force due to the rotational inertial mass of the rotating mass is generated.

On the other hand, when the piston moves to the first fluid chamber side, the working fluid in the first fluid chamber is pressed toward the first and second passages by the piston, but the working fluid from the first fluid chamber to the first passage. The flow of the working fluid is limited by the valve for the first communication passage, and the flow of the working fluid to the second fluid chamber side occurs in the second communication passage. By limiting the flow of the working fluid by the valve for the first communication passage in this way, the amount of rotation of the rotating mass becomes smaller as compared with the case where the piston moves to the second fluid chamber side, and the rotation thereof. The reaction force due to the inertial mass becomes small.

Further, when the valve for the second continuous passage is provided and the valve for the first continuous passage is not provided (hereinafter, the vibration suppression device in this case is referred to as the "second vibration suppression device"), the piston moves inside the cylinder. When it slides and moves to the first fluid chamber side, the piston presses the working fluid in the first fluid chamber toward the first and second passages, so that the second fluid chamber side is inside the first and second passages. Flow of working fluid to. Further, the flow of the working fluid in the first continuous passage is converted into the rotational motion of the rotating mass by the flow conversion mechanism, so that a reaction force is generated by the rotational inertial mass of the rotating mass.

On the other hand, when the piston moves to the second fluid chamber side, the working fluid in the second fluid chamber is pressed toward the first and second passages by the piston, but the working fluid from the second fluid chamber to the second passage. The flow of the working fluid is limited by the valve for the second communication passage, and the flow of the working fluid toward the first fluid chamber side occurs in the first communication passage. By limiting the flow of the working fluid by the valve for the second passage in this way, the working fluid flowing in the first passage is compared with the case where the piston moves to the first fluid chamber side. The flow rate increases, which increases the reaction force due to the rotational inertial mass of the rotating mass.

Further, when both the first and second passage valves are provided (hereinafter, the vibration suppression device in this case is referred to as a "third vibration suppression device"), when the piston moves to the first fluid chamber side, the first The flow of the working fluid from the 1 fluid chamber to the 1st communication passage is restricted by the valve for the 1st communication passage, and the flow of the working fluid to the 2nd fluid chamber side is generated in the 2nd communication passage. On the other hand, when the piston moves to the second fluid chamber side, the flow of the working fluid from the second fluid chamber to the second passage is restricted by the valve for the second passage, and the first fluid chamber side is inside the first passage. Flow of working fluid to. As a result, in the third vibration suppression device, when the piston moves to the first fluid chamber side, the rotational inertia mass of the rotating mass becomes smaller than when it moves to the second fluid chamber side.

Here, in any of the first to third vibration suppression devices described above, a reaction force due to the viscous resistance of the working fluid is generated as the working fluid flows in the first and second communication passages. In the first vibration suppression device, it is premised that the reaction force due to the viscous resistance is set to a value sufficiently smaller than the reaction force due to the rotational inertial mass of the rotating mass.

As described above, when the piston moves to the first fluid chamber side, that is, when the rotational inertia mass damper contracts due to the vibration of the structure, all of the first to third vibration suppression devices extend. The reaction force of the rotary inertial mass damper due to the rotary inertial mass of the rotary mass becomes smaller and reduced as compared with the above. Further, since the connecting member is provided as described above, when the rotary inertial mass damper contracts, the reaction force of the rotary inertial mass damper generated by the vibration of the structure acts as a compressive force on the connecting member. .. From the above, it is possible to prevent the connecting member from buckling during the vibration of the structure, and it is possible to appropriately suppress the vibration of the structure.

The invention according to claim 2 is characterized in that, in the vibration suppression device for the structure according to claim 1, at least one of the first and second communication passage valves is composed of a check valve.

According to this configuration, at least one of the first and second passage valves is composed of a check valve. Therefore, when the valve for the first passage is provided, the valve for the first passage allows the flow of the working fluid from the second fluid chamber to the first passage, and the flow from the first fluid chamber to the first passage is allowed. The flow of the working fluid into the single passage is blocked. Further, when the valve for the second passage is provided, the valve for the second passage allows the flow of the working fluid from the first fluid chamber to the second passage, and the flow from the second fluid chamber to the second passage is allowed. The flow of working fluid into the communication passage is blocked. As described above, when the rotary inertial mass damper contracts due to the vibration of the structure, the reaction force due to the rotary inertial mass of the rotary mass can be hardly generated. Therefore, the effect of the invention according to claim 1 described above can be obtained. Can be obtained effectively.

It is a figure which shows typically the vibration suppression apparatus according to 1st Embodiment of this invention together with the structure to which this is applied. It is a figure which shows enlarged part of the vibration suppression device and a structure of FIG. It is sectional drawing which shows the rotational inertia mass damper of the vibration suppression apparatus of FIG. It is sectional drawing which shows the check valve of the rotary inertial mass damper of FIG. 3, the case where the valve body is located at (a) the closed position, and (b) the case where it is located at the open position. .. It is sectional drawing which shows the rotational inertia mass damper of the vibration suppression apparatus by 2nd Embodiment of this invention. FIG. 5 is a cross-sectional view showing a check valve or the like of the rotary inertial mass damper of FIG. 5 when the valve body is located at (a) a closed position and (b) a case where the valve body is located at an open position. .. It is sectional drawing which shows the modification of the rotary inertia mass damper of FIG. It is sectional drawing which shows the other modification of the rotary inertia mass damper of FIG.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 schematically shows a vibration suppression device according to a first embodiment of the present invention together with a structure B to which the device B is applied. The structure B is, for example, a residential or commercial high-rise building, and is erected on the foundation F. Here, the foundation F is not limited to the foundation of the structure, and may be an underground structure or the like.

As shown in FIG. 1, the vibration suppression device is composed of a plurality of vibration suppression devices AD arranged symmetrically with each other in the horizontal direction about the structure B, and each vibration suppression device AD is a structure B. It includes a rotary inertial mass damper 1 arranged on the outer periphery and a connecting member 31 extending in the vertical direction along the structure B. As shown in FIGS. 2 and 3, the rotary inertial mass damper 1 includes a cylinder 2, a piston 3 slidably provided in the cylinder 2 in the axial direction, a piston rod 4 integrated with the piston 3, and a cylinder. It is provided with a first passage 5 and a second passage 6 connected to 2. In FIG. 2, for convenience, some components such as the first and second passages 5 and 6 are not shown.

The cylinder 2 integrally has a cylindrical peripheral wall 2a and a disk-shaped first end wall 2b and a second end wall 2c provided at both ends of the peripheral wall 2a in the axial direction, respectively. The space defined by the peripheral walls 2a, the first and second end walls 2b, and 2c is divided into the first fluid chamber 2d and the second fluid chamber 2e by the piston 3. The first and second fluid chambers 2d and 2e are filled with a working fluid HF, and the working fluid HF is composed of an appropriate viscous fluid such as silicone oil.

Further, the first end wall 2b of the cylinder 2 is integrally provided with convex portions 2f protruding outward in the axial direction in a concentric manner. A space for partially accommodating the piston rod 4 is formed inside the convex portion 2f, and a universal joint is provided at the end of the convex portion 2f opposite to the first end wall 2b. The first fitting FL1 is provided. Further, rod guide holes 2g and 2h are formed at the centers of the first and second end walls 2b and 2c, respectively. The piston rod 4 extends in the cylinder 2 in the axial direction, and the central portion in the axial direction is integrally connected to the piston 3, and is liquidtightly inserted into the rod guide holes 2g and 2h via a seal. Further, one end of the piston rod 4 is accommodated in the space inside the convex portion 2f, and the portion of the piston rod 4 opposite to the convex portion 2f extends outward from the second end wall 2c, and the piston rod 4 A second attachment FL2 is provided at the other end of the piston via a universal joint.

Further, the outer peripheral surface of the piston 3 is in liquid-tight contact with the inner peripheral surface of the peripheral wall 2a of the cylinder 2 via a seal, and a plurality of axially penetrating outer end portions of the piston 3 in the radial direction. The first communication hole 3a and the second communication hole 3b (only one of each is shown) are formed. Each of the first and second communication holes 3a and 3b communicates with the first and second fluid chambers 2d and 2e, and the first relief valve 11 communicates with the first communication hole 3a and the first relief valve 11 communicates with the second communication hole 3b. Is provided with a second relief valve 12, respectively.

The first relief valve 11 is configured as a so-called normally closed valve, has a valve body and a spring that urges the valve body in the valve closing direction, and the pressure of the working fluid HF in the first fluid chamber 2d is predetermined. When it is smaller than the upper limit value, the first communication hole 3a is closed, and when the upper limit value is reached, the first communication hole 3a is opened. As a result, the first and second fluid chambers 2d and 2e communicate with each other through the first communication hole 3a, and the pressure of the working fluid HF in the first fluid chamber 2d is released to the second fluid chamber 2e side. Therefore, it is limited to the above upper limit or less, and its overgrowth is prevented.

Similarly, the second relief valve 12 has a valve body and a spring that urges the valve body in the valve closing direction, and when the pressure of the working fluid HF in the second fluid chamber 2e is smaller than the upper limit value, The second communication hole 3b is closed, and when the upper limit is reached, the second communication hole 3b is opened. As a result, the first and second fluid chambers 2d and 2e communicate with each other through the second communication hole 3b, and the pressure in the second fluid chamber 2e is released to the first fluid chamber 2d side, so that the upper limit value is reached. It is limited to the following and its overgrowth is prevented. The upper limit values of the first and second relief valves 11 and 12 may be set to different values.

Further, the piston 3 has a predetermined neutral position in the cylinder 2 shown in FIGS. 1 and 2 as an initial position, and is located at this neutral position when no external force has been input.

The first and second communication passages 5 and 6 bypass the piston 3 and communicate with the first and second fluid chambers 2d and 2e over the entire range in the cylinder 2 where the piston 3 can slide. , Connected to the cylinder 2 and provided in parallel with each other. The communication position of the first communication passage 5 with the first and second fluid chambers 2d and 2e overlaps that of the second communication passage 6 in the radial direction of the cylinder 2 (direction orthogonal to the axial direction). , It does not have to overlap.

Further, each of the first and second passages 5 and 6 has, for example, a circular cross section, and the cross-sectional area of both 5 and 6 (the area of the surface orthogonal to the direction in which the working fluid HF flows) is that of the cylinder 2. The value is set to be smaller than the cross-sectional area (area of the plane orthogonal to the axial direction), and the working fluids in the first and second communication passages 5 and 6 are the same as those in the first and second fluid chambers 2d and 2e. It is filled with HF. In FIG. 1, for convenience, the reference numerals of the working fluids HF in the first and second passages 5 and 6 are omitted.

Further, the rotary inertial mass damper 1 is provided in the gear motor M that converts the flow of the working fluid HF in the first continuous passage 5 into rotary motion, the rotary mass 21 connected to the gear motor M, and the second continuous passage 6. The check valve 7 provided is further provided. The gear motor M is, for example, an external gear type, and has a casing 22 and a first gear 23 and a second gear 24 housed in the casing 22. An inscribed gear type may be used as the gear motor M.

The casing 22 is integrally provided in the central portion of the first communication passage 5, and communicates with the inside of the first communication passage 5 via two entrances 22a and 22b facing each other. Further, the first and second gears 23 and 24 are respectively composed of spur gears, are integrally provided on the first and second rotary shafts 25 and 26, and mesh with each other. The first and second rotating shafts 25 and 26 extend horizontally in the direction orthogonal to the first connecting passage 5, and are rotatably supported by the casing 22, and the first rotating shaft 25 projects to the outside of the casing 22. ing. Further, the meshing portions of the first and second gears 23 and 24 face the inlets and outlets 22a and 22b of the casing 22. Further, the rotating mass 21 is coaxially provided integrally with the portion of the first rotating shaft 25 protruding from the casing 22. The rotating mass 21 is made of a material having a relatively large specific gravity, for example, iron, and is formed in a disk shape.

As shown in FIG. 4, the check valve 7 is, for example, a swing type, and is rotatably provided in a valve box 7a provided in the middle of the second passage 6 and in the valve box 7a. It has a valve body 7d. The valve box 7a is provided with a first communication port 7b and a second communication port 7c facing each other, and the inside of the valve box 7a is connected to the second communication port 6 via these communication ports 7b and 7c. Communicating. Further, the first and second communication ports 7b and 7c communicate with the first and second fluid chambers 2d and 2e, respectively, via the second communication passage 6.

The valve body 7d is rotatably supported by the valve box 7a via the shaft 7e, and is between the closed position shown in FIG. 4 (a) and the open position shown in FIG. 4 (b). It is rotatable. The shaft 7e is arranged in the vicinity of the first communication port 7b in the valve box 7a, and extends in a direction orthogonal to the second communication passage 6 (depth direction in FIG. 4). The valve body 7d completely closes the first communication port 7b when it is in the closed position and completely opens it when it is in the open position.

In the check valve 7 having the above configuration, when the piston 3 slides in the cylinder 2 toward the first fluid chamber 2d, the working fluid HF in the first fluid chamber 2d is pressed toward the second continuous passage 6 side. As a result, the valve body 7d is located in an open position due to the action of the pressure of the working fluid HF in the second communication passage 6, thereby the first fluid chamber 2d through the second communication passage 6. 2 Flow of the working fluid HF to the fluid chamber 2e side is always allowed. On the other hand, when the piston 3 slides in the cylinder 2 toward the second fluid chamber 2e, the valve body 7d is pressed as the working fluid HF in the second fluid chamber 2e is pressed toward the second continuous passage 6 side. , The pressure of the working fluid HF in the second connecting passage 6 acts as a back pressure to be located in the closed position, whereby the second fluid chamber 2e to the first fluid chamber 2d side via the second connecting passage 6 The flow of the working fluid HF to is always blocked.

In FIG. 3, the hollow arrow drawn near the second passage 6 indicates the direction in which the working fluid HF can flow in the second passage 6.

The connecting member 31 is a combination of a plurality of steel materials such as H-shaped steel in series, extends in the vertical direction along the structure B as described above, and the upper end thereof is the upper end of the structure B. It is connected to a portion, eg, the horizontal end of the top brace floor FB. The lower end of the connecting member 31 is connected to the second attachment FL2 of the rotational inertia mass damper 1, the rotational inertia mass damper 1 extends in the vertical direction, and the first attachment FL1 is connected to the foundation F. To.

As described above, the cylinder 2 of the rotary inertial mass damper 1 is connected to the foundation F, and the piston rod 4 is connected to the upper end portion of the structure B via the connecting member 31. Further, the connecting member 31 is provided in series between the piston rod 4 and the upper end portion of the structure B, and extends in the axial direction of the cylinder 2. The connection relationship between the cylinder 2 and the piston rod 4 may be reversed, that is, the cylinder 2 is connected to the upper end portion of the structure B via the connecting member 31, and the piston rod 4 is connected to the foundation F. You may.

Next, the operation of the rotary inertial mass damper 1 will be described. Since the structure B is a high-rise building as described above, the bending deformation tends to be more dominant than the shear deformation during the vibration. Therefore, the vibration of the structure B repeatedly reciprocates in the horizontal direction on the upper end side thereof. It is performed in such a manner that it moves and swings. The displacement of the structure B with respect to the foundation F due to the swing is transmitted as an external force to the cylinder 2 and the piston rod 4 via the connecting member 31 extending in the vertical direction, whereby the cylinder 2 and the piston rod 4 are aligned in the axial direction. It moves relatively and the piston 3 slides in the cylinder 2.

In this case, when the piston 3 slides to the first fluid chamber 2d side (left side in FIG. 3), a part of the working fluid HF in the first fluid chamber 2d is pushed out by the piston 3 into the first continuous passage 5. As a result, the working fluid HF flows to the second fluid chamber 2e side (right side) in the first communication passage 5. On the contrary, when the piston 3 slides to the second fluid chamber 2e side (right side), a part of the working fluid HF in the second fluid chamber 2e is pushed out by the piston 3 into the first continuous passage 5. As a result, the working fluid HF flows to the first fluid chamber 2d side (left side) in the first communication passage 5.

The flow of the working fluid HF is converted into rotary motion by the gear motor M, the first and second gears 23 and 24 are rotated, and the first rotating shaft 25 and the rotating mass 21 integrated with the first gear 23 are rotated. As a result, a reaction force is generated due to the rotational inertia mass of the rotating mass 21.

Further, when the piston 3 slides toward the first fluid chamber 2d, the valve body 7d of the check valve 7 is located at the open position as described above, so that the first fluid chamber 2d moves to the second continuous passage 6. Since the flow of the working fluid HF is allowed, a part of the working fluid HF in the first fluid chamber 2d is pushed out to the second passage 6 by the piston 3, whereby the second passage 6 is pushed into the second passage 6. 2 Flow of the working fluid HF to the fluid chamber 2e side occurs.

On the other hand, when the piston 3 slides toward the second fluid chamber 2e, the valve body 7d of the check valve 7 is located at the closed position as described above, so that the second fluid chamber 2e moves to the second communication passage 6. Since the flow of the working fluid HF is blocked, the working fluid HF in the second fluid chamber 2e is not pushed out to the second communication passage 6 by the piston 3, but is pushed out to the first communication passage 5 as described above. Therefore, in this case, the flow rate of the working fluid HF flowing in the first continuous passage 5 becomes larger than that when the piston 3 slides to the first fluid chamber 2d side, so that the rotating mass 21 The amount of rotation increases, and the reaction force due to the rotational inertia mass increases.

Further, in the rotary inertial mass damper 1, a reaction force due to the viscous resistance of the working fluid HF is generated as the working fluid HF flows in the first and second communication passages 5 and 6.

As described above, according to the first embodiment, the check valve 7 allows the flow of the working fluid from the first fluid chamber 2d to the second communication passage 6, and also allows the flow of the working fluid from the second fluid chamber 2e to the second. The flow of the working fluid HF into the communication passage 6 is blocked. Further, when the piston 3 slides toward the first fluid chamber 2d, that is, when the rotary inertial mass damper 1 contracts, the check valve 7 allows the flow of the working fluid HF as described above. The reaction force due to the rotational inertial mass of the rotary mass 21 is smaller and reduced as compared with the case where the rotary inertial mass damper 1 is extended.

Further, since the connecting member 31 is provided as described above, when the rotary inertial mass damper 1 contracts, the reaction force of the rotary inertial mass damper 1 generated by the vibration of the structure B is applied to the connecting member 31. Acts as a compressive force. From the above, it is possible to prevent the connecting member 31 from buckling during the vibration of the structure B, and by extension, the vibration of the structure B can be appropriately suppressed.

Further, by obtaining the above-mentioned effects, for example, the cross-sectional area of the connecting member 31 can be set to be relatively small, whereby the manufacturing cost of the vibration suppression device AD can be reduced and the vibration can be reduced. The design of the entire structure B including the restraining device AD can be improved.

Next, the rotational inertia mass damper 41 of the vibration suppression device according to the second embodiment of the present invention will be described with reference to FIGS. 5 and 6. In this rotary inertial mass damper 41, as compared with the rotary inertial mass damper 1 of the first embodiment, the check valve 7 is not provided in the second continuous passage 6, and the check valve 42 is in the first continuous passage 5. The main difference is that it is provided in. In FIGS. 5 and 6, the same components as those in the first embodiment are designated by the same reference numerals. Hereinafter, the points different from those of the first embodiment will be mainly described.

As shown in FIG. 6, the check valve 42 is, for example, a swing type like the check valve 7 of the first embodiment, and has a valve box 42a provided in the middle of the first continuous passage 5 and a valve box 42a. It has a valve body 42d rotatably provided in the valve box 42a. The valve box 42a is provided with a first communication port 42b and a second communication port 42c facing each other, and the inside of the valve box 42a is connected to the first communication passage 5 via these communication ports 42b and 42c. Communicating. Further, the first and second communication ports 42b and 42c communicate with the first and second fluid chambers 2d and 2e, respectively, via the first communication passage 5.

The valve body 42d is rotatably supported by the valve box 42a via the shaft 42e, and is between the closed position shown in FIG. 6A and the open position shown in FIG. 6B. It is rotatable. The shaft 42e is arranged in the vicinity of the second communication port 42c in the valve box 42a, and extends in a direction orthogonal to the first communication passage 5 (depth direction in FIG. 6). The valve body 42d completely closes the second communication port 42c when it is in the closed position and completely opens it when it is in the open position.

In the check valve 42 having the above configuration, when the piston 3 slides in the cylinder 2 toward the second fluid chamber 2e, the working fluid HF in the second fluid chamber 2e is pressed toward the first continuous passage 5. As a result, the valve body 42d is located in an open position due to the pressure of the working fluid HF in the first continuous passage 5, whereby the second fluid chamber 2e passes through the first continuous passage 5. The flow of the working fluid HF to the 1 fluid chamber 2d side is always allowed. On the other hand, when the piston 3 slides in the cylinder 2 toward the first fluid chamber 2d, the valve body 42d becomes pressed as the working fluid HF in the first fluid chamber 2d is pressed toward the first continuous passage 5. , The pressure of the working fluid HF in the first continuous passage 5 acts as a back pressure to be located in the closed position, whereby the first fluid chamber 2d to the second fluid chamber 2e side via the first continuous passage 5 The flow of the working fluid HF to is always blocked.

In FIG. 5, the hollow arrows drawn near the first passage 5 indicate the direction in which the working fluid HF can flow in the first passage 5.

Like the rotary inertia mass damper 1 of the first embodiment, the rotary inertia mass damper 41 has its cylinder 2 connected to the foundation F, and its piston rod 4 is connected to the structure B via the connecting member 31. It is connected to the upper end (see FIGS. 1 and 2). The displacement of the structure B with respect to the foundation F due to vibration is transmitted to the cylinder 2 and the piston rod 4 via the connecting member 31, whereby the piston 3 slides in the cylinder 2.

In this case, when the piston 3 slides to the second fluid chamber 2e side (to the right in FIG. 5), the valve body 42d of the check valve 42 is located at the open position as described above, so that the second fluid chamber 2e Since the flow of the working fluid HF from the to the first connecting passage 5 is allowed, a part of the working fluid HF in the second fluid chamber 2e is pushed out to the first connecting passage 5 by the piston 3, so that the first The flow of the working fluid HF to the first fluid chamber 2d side (left side) occurs in the communication passage 5. The flow of the working fluid HF in the first communication passage 5 is converted into the rotational motion of the rotary mass 21 by the gear motor M as in the case of the first embodiment, and as a result of the rotation of the rotary mass 21, its rotational inertia. A reaction force due to mass is generated. Further, a part of the working fluid HF in the second fluid chamber 2e is pushed out to the second passage 6 by the piston 3, and thereby the working fluid to the first fluid chamber 2d side in the second passage 6. HF fluidization occurs.

In this way, when the piston 3 slides toward the second fluid chamber 2e, that is, when the rotational inertia mass damper 41 extends, the working fluid HF flows in both the first and second communication passages 5 and 6. As a result, both a reaction force due to the rotational inertial mass of the rotating mass 21 and a reaction force due to the viscous resistance of the working fluid HF are generated. In the second embodiment, it is premised that the reaction force due to the viscous resistance is set to a value sufficiently smaller than the reaction force due to the rotational inertia mass of the rotating mass 21.

On the contrary, when the piston 3 slides to the first fluid chamber 2d side (left side), the valve body 42d is located at the closed position, so that the operation from the first fluid chamber 2d to the first communication passage 5 is performed. Since the flow of the fluid HF is blocked, the working fluid HF in the first fluid chamber 2d is not extruded into the first communication passage 5, but a part of it is extruded into the second communication passage 6, and the second communication passage 6 is pushed out. The flow of the working fluid HF to the second fluid chamber 2e side (right side) occurs in 6.

In this way, when the piston 3 slides to the first fluid chamber 2d side, that is, when the rotational inertia mass damper 41 contracts, the working fluid HF flows only in the second communication passage 6, thereby causing the rotating mass. The reaction force due to the rotational inertia mass of 21 is hardly generated, and the reaction force due to the viscous resistance of the working fluid HF is generated. From the above premise, the reaction force due to the viscous resistance is sufficiently smaller than the reduction of the reaction force due to the rotational inertia mass of the rotating mass 21.

As described above, according to the second embodiment, the check valve 42 allows the flow of the working fluid from the second fluid chamber 2e to the first continuous passage 5, and also allows the flow of the working fluid from the first fluid chamber 2d to the first. The flow of the working fluid HF into the communication passage 5 is blocked. Further, when the piston 3 slides toward the first fluid chamber 2d, that is, when the rotary inertial mass damper 41 contracts, the check valve 42 blocks the flow of the working fluid HF as described above. The reaction force due to the rotational inertia mass of the rotating mass 21 is hardly generated.

Further, since the connecting member 31 is provided as described in the first embodiment, when the rotary inertial mass damper 41 contracts, the reaction force of the rotary inertial mass damper 41 generated due to the vibration of the structure B is generated. , Acts on the connecting member 31 as a compressive force. From the above, as in the case of the first embodiment, it is possible to prevent the connecting member 31 from buckling during the vibration of the structure B, and by extension, the vibration of the structure B can be appropriately suppressed.

The present invention is not limited to the first and second embodiments described above (hereinafter, collectively referred to as "embodiments"), and can be implemented in various embodiments. For example, in the embodiment, swing type check valves 7 and 42 are used, but other suitable check valves such as ball type, poppet type, and wafer type may be used. Of course. Further, in the embodiment, as the second communication passage in the present invention, the second communication passage 6 that bypasses the piston 3 and is connected to the cylinder 2 is used, but it is formed in the piston 3 and penetrates in the axial direction. , Communication holes communicating with the first and second fluid chambers may be used. Thereby, the second continuous passage in the present invention can be easily constructed.

FIG. 7 shows a rotary inertial mass damper when the communication hole 3c as described above is used as the second communication passage according to the first embodiment. As shown in the figure, in this case, a check valve 8 is provided in the communication hole 3c, and the check valve 8 is used to move the first fluid chamber 2d to the second fluid chamber 2e via the communication hole 3c. The flow of the working fluid HF is allowed, and the flow of the working fluid HF from the second fluid chamber 2e to the first fluid chamber 2d through the communication hole 3c is blocked. It goes without saying that an appropriate check valve 8, such as a ball type, may be used as the check valve 8.

Further, in the first embodiment, as the valve for the second continuous passage in the present invention, a check valve 7 configured to prevent the flow of the working fluid HF from the second fluid chamber 2e to the second continuous passage 6 is provided. Although it is used, a valve for the second passage, which is configured to limit the flow of the working fluid from the second fluid chamber to the second passage, may be used. In this case, the valve for the second passage is configured as follows, for example. That is, when the piston slides toward the second fluid chamber, the pressure of the working fluid in the second passage acts as a back pressure on the valve body, whereby the opening degree of the valve body acts on the stopper. The valve for the second passage is configured so that the contact causes the piston to be held at a smaller value than when it slides toward the first fluid chamber.

Similarly, in the second embodiment, as the valve for the first communication passage in the present invention, the check valve 42 configured to block the flow of the working fluid HF from the first fluid chamber 2d to the first communication passage 5. However, a valve for the first communication passage configured to limit the flow of the working fluid from the first fluid chamber to the first communication passage may be used. In this case, the first communication passage valve is configured as follows, for example. That is, when the piston slides toward the first fluid chamber, the pressure of the working fluid in the first communication passage acts as a back pressure on the valve body, and thereby the opening degree of the valve body acts on the stopper. The valve for the first communication passage is configured so that the contact is held at a smaller value than when the piston slides toward the second fluid chamber side.

Further, in the first embodiment, the check valve 7 which is the valve for the second passage in the present invention is provided, and in the second embodiment, the check valve 42 which is the valve for the first passage in the present invention is provided. As described above, the vibration suppression device according to the present invention is configured, but it may be configured to include both the check valves 7 and 42.

Further, in the embodiment, the gear motor M is used as the flow conversion mechanism in the present invention, but other suitable mechanisms such as the screw mechanism described in FIG. 5 of Japanese Patent No. 5191579 and the screw mechanism of Japanese Patent No. 5161395 are used. A ball screw in which the piston shown in FIG. 2 of No. 2 is integrally provided on the nut, a vane motor, a plunger motor (piston motor), or the like may be used. When this ball screw is used as the flow conversion mechanism, the flow conversion mechanism and the first continuous passage are disclosed in JP2014-137108, JP2014-163447, and JP2014-211176. It may be configured as such.

Further, in the embodiment, a space for partially accommodating the piston rod 4 is formed in the convex portion 2f of the cylinder 2, and the space is filled with the working fluid HF to provide a sub-piston. , This sub-piston may be integrally provided at one end of the piston rod 4, thereby adding the function of a normal viscous damper.

FIG. 8 shows rotation when the working fluid HF is filled in the space inside the convex portion 2f and the sub-piston 9 connected to one end of the piston rod 4 is provided so as to be movable in the axial direction according to the first embodiment. It shows the inertial mass damper. In this case, the sub-piston 9 is provided with a communication hole (orifice) penetrating in the axial direction, a pressure regulating valve, and a relief valve. Further, in this case, the damping performance of the sub-piston 9 can be changed by adopting the configurations disclosed in JP-A-2017-53402, JP-A-2013-130203, JP-A-2009-19383, and the like. It may be configured as.

Further, in the embodiment, the connecting member 31 is provided in series between the upper end portion of the structure B and the rotational inertia mass damper 1, but instead of or together with this, the rotational inertia mass damper 1 and the foundation F It may be provided in series between. Further, in the embodiment, the first and second parts in the present invention are the brace floor FB at the upper end of the foundation F and the structure B, respectively, but other suitable parts may be used. Further, in the embodiment, the structure B is a high-rise building, but may be another suitable structure such as a bridge or a steel tower. Furthermore, it goes without saying that the variations relating to the embodiments described so far may be appropriately combined and applied. In addition, within the scope of the gist of the present invention, the detailed configuration (including shape, size, number, arrangement, etc.) can be appropriately changed.

B Structure F Foundation (1st part)
FB brace floor (second part)
AD Vibration suppression device 1 Rotational inertial mass damper 2 Cylinder 3 Piston 4 Piston rod 5 1st consecutive passage 6 2nd consecutive passage 7 Check valve M Gear motor (flow conversion mechanism)
21 Rotating mass 31 Connecting member HF working fluid 41 Rotating inertial mass damper 42 Check valve 3c Communication hole (second communication passage)
8 Check valve

Claims (2)

A structure vibration suppression device that includes a rotary inertial mass damper and a connecting member, is connected to predetermined first and second parts in a system including a structure, and suppresses vibration of the structure.
The rotary inertia mass damper is
A cylinder filled with working fluid and connected to the first part,
A piston that is slidably provided in the cylinder in the axial direction and divides the inside of the cylinder into a first fluid chamber and a second fluid chamber.
A piston rod that is connected to the piston, extends outward from the cylinder in the axial direction via the second fluid chamber, and is connected to the second portion.
With
The connecting member is provided in series between the first portion and the cylinder, and at least one between the second portion and the piston rod, and extends in the axial direction of the cylinder .
The rotary inertia mass damper further
A first passage that bypasses the piston and communicates with the first and second fluid chambers and is filled with a working fluid.
With a rotatable rotating mass,
A flow conversion mechanism that converts the flow of the working fluid in the first continuous passage into the rotational motion of the rotating mass, and
A second passage that is provided in parallel with the first passage and communicates with the first and second fluid chambers and is filled with a working fluid.
Provided in the first communication passage, the flow of the working fluid from the second fluid chamber to the first communication passage is allowed, and the flow of the working fluid from the first fluid chamber to the first communication passage is restricted. A valve for the first communication passage, and a working fluid provided in the second passage and when the piston slides toward the first fluid chamber, the working fluid from the first fluid chamber to the second passage. with always permit flow, the piston of the second communication passage valve to always limit the flow of hydraulic fluid to the second communication path from said second fluid chamber when the slide to the second fluid chamber side At least one and
Equipped with a,
When the rotational inertia mass damper contracts due to the vibration of the structure, the reaction force of the rotational inertia mass damper due to the rotational inertia mass of the rotating mass is the rotational inertia mass over the entire stroke of the piston in the cylinder. A vibration suppression device for a structure, characterized in that the reaction force is smaller than the reaction force when the damper is extended . The vibration suppression device for a structure according to claim 1, wherein at least one of the first and second passage valves is composed of a check valve.

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