JP5161395B1 - Vibration suppression device - Google Patents

Abstract

Disclosed is a vibration suppressing device capable of efficiently converting a displacement of a structure into a rotational motion of a rotating mass via a working fluid, thereby appropriately suppressing vibration of the structure.
A vibration suppressing device 1 includes a cylinder 2 filled with a working fluid HF, a rod 3 movable in an axial direction with respect to the cylinder 2, a fixed integrally with the rod 3, and as the rod 3 moves. A first piston 4 that slides in the cylinder 2, a bypass passage 11 that is connected to the cylinder 2 so as to bypass the first piston 4, and is rotatably provided in the bypass passage 11. A screw shaft 15 extending in the direction, and a nut 17 screwed onto the screw shaft 15 via a ball. The screw shaft 15 can slide along the screw shaft 15 in the bypass 11 passage and cannot rotate with respect to the bypass passage 11. A second piston 16 and a rotatable rotating mass 21 attached to the screw shaft 15.
[Selection] Figure 2

Description

  The present invention relates to a vibration suppressing device that is provided between two parts in a system including a structure and suppresses vibration of the structure.

  Conventionally, what was disclosed by patent document 1 as this kind of vibration suppression apparatus is known, for example. The vibration suppressing device is provided with a cylinder filled with a working fluid, a rod that is partially accommodated in the cylinder, movable in the axial direction, and integrally fixed to the rod so as to be slidable in the cylinder. It has a piston. Further, a bypass passage is connected to the cylinder so as to bypass the piston, and an impeller is provided in the middle of the bypass passage. A rotating mass is connected to the impeller.

  The conventional vibration suppression device having the above configuration is used as a vehicle suspension device. When an external force is input to the rod along with the vibration of the vehicle, the rod moves in the axial direction with respect to the cylinder, and the piston slides in the cylinder in the axial direction. As a result, the flow of the working fluid in the bypass passage causes the impeller and the rotating mass to rotate integrally, and the inertial force of the working fluid and the rotating mass acts on the vehicle as a resistance force, so that the vibration of the vehicle is reduced. It is suppressed.

JP 2007-205433 A

  As described above, in the conventional vibration suppression device, the displacement of a structure such as a vehicle is converted into a flow of working fluid, and the flow of the working fluid is further converted into rotational motion by the impeller and transmitted to the rotary mass. . For this reason, for example, when the flow rate of the working fluid is small, the amount of rotation of the impeller and the rotating mass tends to be insufficient, so that the inertial force of the rotating mass cannot be obtained sufficiently. There is a possibility that it cannot be suppressed.

  The present invention has been made to solve the above-described problems, and the displacement of the structure can be efficiently converted into the rotational motion of the rotating mass via the working fluid. An object of the present invention is to provide a vibration suppressing device that can appropriately suppress the vibration of the vibration.

  In order to achieve the above object, an invention according to claim 1 is a vibration suppressing device for suppressing vibration of a structure, provided between two parts in a system including the structure. A cylinder connected to one of the two parts and filled with a working fluid; a rod connected to the other of the two parts, partially accommodated in the cylinder, and movable in the axial direction with respect to the cylinder; A first piston fixed integrally with the rod and sliding in the cylinder as the rod moves, a bypass passage connected to the cylinder so as to bypass the first piston, and rotatably provided in the bypass passage A screw shaft that extends in the axial direction of the bypass passage, and a nut that is screwed to the screw shaft via a ball, is slidable in the bypass passage along the screw shaft, and is opposed to the bypass passage. A second piston non-rotatable Te, attached to the screw shaft, characterized in that it comprises a rotary mass rotatable.

  According to this configuration, when a structure vibrates due to an earthquake or the like and displacement occurs between two parts in the system including the structure, the displacement between the two parts (hereinafter referred to as “displacement of the structure”). ) Is transmitted to the cylinder and the rod. As a result, the rod moves in the axial direction with respect to the cylinder, and the first piston integrated with the rod slides in the cylinder accordingly, so that the working fluid in the cylinder and in the bypass passage connected to the cylinder is obtained. The flow occurs.

  A screw shaft extending in the axial direction is rotatably provided in the bypass passage. The nut of the second piston is screwed onto the screw shaft via a ball and is rotatable on the screw shaft. A rotating mass is attached. Thus, these screw shafts, nuts, and balls constitute a ball screw, and the nuts are rotatable with respect to the screw shafts. Further, the second piston can slide in the bypass passage along the screw shaft and cannot rotate with respect to the bypass passage.

  As described above, when flow occurs in the working fluid in the bypass passage, the second piston slides in the bypass passage by being pressed by the flowing working fluid. In this case, since the screw shaft can rotate and the nut of the second piston can rotate with respect to the screw shaft and cannot rotate with respect to the bypass passage, the second piston slides in the bypass passage. As it moves, the screw shaft rotates with the rotating mass relative to the bypass passage.

  As described above, the displacement of the structure due to the vibration is transmitted to the working fluid via the rod and the first piston, and further transmitted to the rotating mass via the second piston and the screw shaft, so that the rotating mass is Rotates. Therefore, the vibration of the structure can be suppressed by the viscous damping force (effect) of the working fluid and the rotational inertia force (effect) of the rotating mass.

  In this case, unlike the above-described conventional case, the flow of the working fluid is converted into rotational motion using a ball screw and a second piston, which are not an impeller, but a screw shaft, a nut and a ball. By appropriately setting the lead angle, the screw shaft and the rotation mass can be sufficiently rotated even when the flow rate of the working fluid is relatively small and the movement amount of the second piston is relatively small. As described above, the displacement of the structure can be efficiently converted into the rotational motion of the rotary mass via the working fluid, and thereby the vibration of the structure can be appropriately suppressed.

  The invention according to claim 2 is the vibration suppressing device according to claim 1, wherein the second piston is provided on one side in the axial direction with respect to the nut, and the first piston slides on one side of the cylinder. A first pressure receiving portion that is pressed by the working fluid that flows along with the nut and a nut that is provided on the other side in the axial direction with respect to the nut, and as the first piston slides on the other side of the cylinder. A second pressure receiving portion that is pressed by the flowing working fluid; a first elastic body that is provided between the nut and the first pressure receiving portion and that transmits the pressing force of the working fluid that acts on the first pressure receiving portion to the nut; And a second elastic body that is provided between the nut and the second pressure receiving portion and transmits a pressing force of the working fluid acting on the second pressure receiving portion to the nut.

  According to this configuration, when the working fluid flows as the first piston slides to one side of the cylinder, the first pressure receiving portion of the second piston is pressed by the flowing working fluid. On the contrary, when the working fluid flows as the first piston slides to the other side of the cylinder, the second pressure receiving portion of the second piston is pressed by the flowing working fluid. In addition, the pressing force of the working fluid acting on the first pressure receiving portion is transmitted to the nut via the first elastic body, and the pressing force of the working fluid acting on the second pressure receiving portion is transmitted via the second elastic body. Is transmitted to the nut.

  With the above configuration, when the first piston repeatedly slides with the rod on one side and the other side in the axial direction due to the reciprocation of the structure due to vibration, the displacement of the structure is as follows. Is transmitted to the rotating mass.

  That is, when the first piston slides to one side, the working fluid, the first pressure receiving portion, and the first elastic body, and when the first piston slides to the other side, the working fluid, the second pressure receiving portion, and As a result of being transmitted to the nut via the second elastic body and further transmitted to the rotating mass via the screw shaft, the rotating mass rotates. In this way, an additional vibration system composed of a working fluid, a first elastic body, and a rotating mass, and an additional vibration system composed of a working fluid, a second elastic body, and a rotating mass are configured for the reciprocation of the structure due to vibration. The

  Therefore, by setting the viscous damping coefficient of the working fluid, the spring constant of the first elastic body, the spring constant of the second elastic body, and the mass of the rotating mass, the natural frequency of the additional vibration system is set to the desired value of the structure. It is possible to tune (resonate) with the natural frequency of the structure, and more appropriately suppress the vibration of the structure.

  The invention according to claim 3 is the vibration suppressing device according to claim 2, wherein the spring constant of the first elastic body and the spring constant of the second elastic body are set to different values.

  In general, when a structure vibrates due to an earthquake or the like, it does not always vibrate at a single natural frequency, but usually vibrates at a plurality of different natural frequencies, that is, in a plurality of vibration modes. . On the other hand, normally, a single additional vibration system composed of a single mass damper and a supporting member has only one natural frequency. For this reason, in order to appropriately suppress the vibration of the structure due to the plurality of vibration modes, the natural frequency of the additional vibration system is tuned to the plurality of desired natural frequencies of the structure. A plurality of additional vibration systems corresponding to the number must be provided, which leads to an increase in the size and cost of the vibration suppression device.

  According to the present invention, the spring constants of the first and second elastic bodies constituting one and the other of the two additional vibration systems described in the description of the invention according to claim 2 are set to different values. . Accordingly, the natural frequency of one of these additional vibration systems is appropriately tuned to the desired one natural frequency of the structure, and the natural frequency of the other additional vibration system is adjusted to the other desired frequency of the structure. It can be appropriately tuned to one natural frequency. That is, the natural frequency of one and the other additional vibration system can be multiple-tuned to two desired natural frequencies of different structures, respectively. Accordingly, the vibration due to the plurality of vibration modes of the structure can be appropriately suppressed by a single vibration suppression device including the working fluid, the rotary mass, the first elastic body, the second elastic body, and the like, and further Miniaturization can be achieved.

  According to a fourth aspect of the present invention, in the vibration suppressing device according to the second or third aspect, the rotating mass is attached to the screw shaft, the first rotating mass is rotatable, and the first rotating mass is interposed via an elastic body. And a second rotating mass that is attached and rotatable relative to the first rotating mass.

  According to this configuration, the rotating mass is configured by the first and second rotating masses, the first rotating mass is attached to the screw shaft, and the second rotating mass is connected to the first rotating mass via the elastic body. It is attached and is rotatable relative to the first rotating mass. For this reason, as is apparent from the description of the invention according to claim 1, the displacement of the structure due to vibration is transmitted to the screw shaft via the rod, the first piston, the working fluid, and the second piston, and further, the first As a result of being transmitted to the rotating mass, the first rotating mass rotates. Further, as the first rotating mass rotates, the second rotating mass rotates with respect to the first rotating mass. Therefore, in addition to the viscous damping effect of the working fluid and the rotational inertia effect of the first rotary mass, the vibration of the structure can be more appropriately suppressed by the rotary inertia effect of the second rotary mass.

  Further, since the second rotating mass is attached to the first rotating mass via an elastic body, the two additional vibration systems (hereinafter referred to as “first additional vibration system”) described in the description of the invention according to claim 2 are provided. In addition, the second additional vibration system including the second rotating mass and the elastic body can be further configured. In this case, the second additional vibration system is not provided in parallel to the entire first additional vibration system, and the second additional vibration system (for the operation of the first rotating mass of the first additional vibration system ( As the natural frequency of the additional vibration system configured by combining the first and second additional vibration systems, two combined natural frequencies are respectively obtained. It exists separately.

  Therefore, the masses of the first and second rotating masses, the spring constants of the first and second elastic bodies, and the spring constants of the elastic bodies (hereinafter referred to as “specifications of the first and second additional vibration systems”) are set. Allows the above two combined natural frequencies to be appropriately multiple tuned to the two different desired natural frequencies of the structure, respectively, and thus according to the two different desired vibration modes of the structure. Vibration can be appropriately suppressed. Alternatively, by setting the specifications of the first and second additional vibration systems, the two combined natural frequencies can be appropriately multiple-tuned to the same desired natural frequency of the structure, and thus the structure The vibration by one desired vibration mode can be suppressed more appropriately.

  In addition, as described in the description of the invention according to claim 3, when the spring constants of the first and second springs are different from each other, the additional structure constituted by a combination of the first and second additional vibration systems. As the natural frequency of the vibration system, 2 × 2 = 4 combined natural frequencies exist separately. Therefore, by setting the specifications of the first and second additional vibration systems, the above four combined natural frequencies can be appropriately multiple-tuned to the four different desired natural frequencies of the structure. As a result, the vibrations of the four desired vibration modes of the structure can be appropriately suppressed. Alternatively, by setting the specifications of the first and second additional vibration systems, the four combined natural frequencies can be appropriately tuned to the same desired natural frequency of the structure, and thus the structure The vibration by one desired vibration mode can be suppressed more appropriately.

  The invention according to claim 5 is the vibration suppressing device according to any one of claims 1 to 4, characterized in that the cross-sectional area of the bypass passage is smaller than the cross-sectional area of the cylinder.

  According to this configuration, the cross-sectional area of the bypass passage, that is, the area of the surface orthogonal to the direction in which the working fluid flows in the bypass passage is larger than the cross-sectional area of the cylinder, that is, the area of the surface orthogonal to the direction in which the working fluid flows in the cylinder. It ’s getting smaller. As a result, the displacement of the first piston in the cylinder when the first piston slides and the working fluid flows as described in the description of the invention according to claim 1 with the displacement of the structure. On the other hand, the movement amount of the second piston in the bypass passage can be increased, and the rotation amount of the rotary mass can be increased. Therefore, the rotational inertia force of the rotary mass can be obtained more appropriately, and consequently the vibration of the structure can be more appropriately suppressed.

  For the same reason, the pressing force of the working fluid acting on the second piston can be made smaller than the pushing force of the working fluid acting on the first piston, so the first and second aspects of the invention according to claim 2 As the elastic body, a compact one having a small spring constant can be adopted.

  According to a sixth aspect of the present invention, in the vibration suppressing device according to any one of the first to fifth aspects, the screw shaft extends outside the bypass passage, and the rotary mass is disposed outside the bypass passage. It is characterized by that.

  According to this configuration, since the rotary mass is arranged outside the bypass passage, the mass of the rotary mass, that is, the rotary inertia force thereof can be easily adjusted.

  According to a seventh aspect of the present invention, in the vibration suppressing device according to any one of the first to sixth aspects, the first pressure chamber and the second pressure chamber communicated with the bypass passage on both sides of the first piston in the cylinder. Are respectively defined, and the valve is opened when one of the pressure of the working fluid in the first pressure chamber and the pressure of the working fluid in the second pressure chamber reaches a predetermined value, whereby the first and second pressure chambers are formed. And a relief valve communicating with each other.

  According to this configuration, the first and second pressure chambers communicating with the bypass passage are respectively defined on both sides of the first piston in the cylinder. As described above, since the first piston slides in the cylinder in accordance with the vibration of the structure, the viscous damping force of the working fluid and the rotational inertia force of the rotating mass are generated. The pressure of the working fluid in the room has a close correlation with the viscous damping force of the working fluid and the rotational inertia force of the rotating mass, and the larger both are, the larger the viscous damping force and the rotational inertia force are.

  According to the present invention, when the pressure of the working fluid in the first or second pressure chamber reaches a predetermined value, that is, the reaction force of the vibration suppressing device including the viscous damping force of the working fluid and the rotational inertia force of the rotating mass. When (axial force) becomes relatively large, both pressure chambers are communicated by the relief valve. As a result, even if the first piston slides in the cylinder, the working fluid is hardly compressed and the working fluid does not flow in the cylinder, so that the viscous damping force of the working fluid and the rotational inertia force of the rotating mass reach a peak. Therefore, the excessive increase can be prevented.

It is a model figure of the vibration suppression apparatus by 1st Embodiment. It is sectional drawing which shows the vibration suppression apparatus by 1st Embodiment. It is sectional drawing which follows the III-III line of FIG. It is sectional drawing which expands and shows the nut and screw shaft of a vibration suppression apparatus. It is a figure which shows the example at the time of applying the vibration suppression apparatus by 1st Embodiment to a structure. It is a model figure of the vibration suppression apparatus by 2nd Embodiment. It is sectional drawing which shows the vibration suppression apparatus by 2nd Embodiment. It is a figure which shows the example at the time of applying the vibration suppression apparatus by 2nd Embodiment to a structure. It is sectional drawing which shows the vibration suppression apparatus by 3rd Embodiment. It is a model figure of the vibration suppression apparatus by 4th Embodiment. It is sectional drawing which shows the vibration suppression apparatus by 4th Embodiment.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 shows a model of a vibration suppression device 1 according to a first embodiment of the present invention. As shown in the figure, the vibration suppressing device 1 includes a first viscous element, a first inertia connecting element, and an axial force limiting mechanism.

  The first viscous element and the first inertia connecting element each exhibit a viscous damping effect and a rotational inertia effect in order to suppress the vibration of the structure, and the axial force limiting mechanism is a shaft of the vibration suppressing device 1. This is to limit the force (reaction force).

  FIG. 2 illustrates the vibration suppressing device 1 described above. The vibration suppression device 1 includes a cylindrical cylinder 2, a rod 3 accommodated in the cylinder 2, and a first piston 4.

  The cylinder 2 includes a pair of side walls 2a and 2a that are opposed to each other in the axial direction, and a peripheral wall 2b that is integrally provided between the two side walls 2a and 2a. The oil chamber defined by the side walls 2a, 2a and the peripheral wall 2b is divided by the first piston 4 into a first oil chamber 2c and a second oil chamber 2d. Filled with oil HF. These first and second oil chambers 2 c and 2 d are respectively arranged on one side and the other side in the axial direction with respect to the first piston 4. This hydraulic oil HF corresponds to the first viscous element described above.

  Further, a rod guide hole 2e penetrating in the axial direction is formed at the radial center of each side wall 2a, and a seal 5 is provided in the rod guide hole 2e. Further, a convex portion 2f protruding in the axial direction is integrally provided on the side wall 2a on one side in the axial direction (left side in FIG. 2), and a housing portion 2g is defined inside the convex portion 2f. Has been. Further, the first fitting FL1 is provided on the convex portion 2f via a universal joint.

  The rod 3 is inserted into the rod guide holes 2 e and 2 e, extends in the axial direction, and is movable in the axial direction with respect to the cylinder 2. One end of the rod 3 is accommodated in the accommodating portion 2g, and most of the rod 3 other than the one end is accommodated in the cylinder 2. Usually, the rod 3 is located at the neutral position shown in FIG. 2, and in this state, the volumes of the first and second oil chambers 2c, 2d are equal to each other. Moreover, the 2nd fixture FL2 is provided in the other end part of the rod 3 via the universal joint.

  The first piston 4 is formed in a columnar shape and is integrally fixed to the rod 3. A seal 6 is provided on the peripheral surface of the first piston 4. A plurality of holes penetrating in the axial direction are formed in the radially outer end of the first piston 4 (only two are shown), and the first relief valve 7 and the second hole are formed in these holes. A relief valve 8 is provided. The first relief valve 7 is composed of a valve body 7a and a spring 7b that biases the valve body 7a toward the valve closing side, and opens when the pressure of the hydraulic oil HF in the first oil chamber 2c reaches a predetermined value. Thus, the first and second oil chambers 2c and 2d are communicated with each other.

  Similar to the first relief valve 7, the second relief valve 8 includes a valve body 8a and a spring 8b that urges the valve body 8a toward the valve closing side. The pressure of the hydraulic oil HF in the second oil chamber 2d is When the predetermined value is reached, the valve is opened, whereby the first and second oil chambers 2c, 2d are communicated with each other. These first and second relief valves 7 and 8 correspond to the above-described axial force limiting mechanism (see FIG. 1).

  The vibration suppressing device 1 includes a bypass pipe 11, a screw shaft 15, a second piston 16, and first rotating masses 21 and 21. The first rotating masses 21 and 21 correspond to the first inertial connecting element (see FIG. 1) described above. The bypass pipe 11 is connected to the cylinder 2 so as to bypass the first piston 4, and communicates with the first and second oil chambers 2c and 2d.

  The bypass pipe 11 integrally includes a first pipe line 12 and a second pipe line 13 provided symmetrically with respect to the cylinder 2 and a third pipe line 14 extending in parallel with the cylinder 2. The cross sections (surfaces orthogonal to the axial direction) of these first to third pipelines 12 to 14 are circular. The cross-sectional area of the bypass pipe 11 (area of the surface orthogonal to the axial direction) is set to a value smaller than the cross-sectional area of the cylinder 2 (area of the surface orthogonal to the axial direction).

  One end of the first conduit 12 is connected to the radially outer end of one side wall 2 a of the cylinder 2. The first pipe line 12 extends from the side wall 2a to one side in the axial direction, bends at a right angle, and extends outward in the radial direction. The other end of the first pipe 12 is connected to one end of the third pipe 14 in the axial direction. One end of the second conduit 13 is connected to the radially outer end of the other side wall 2 a of the cylinder 2. The second pipe line 13 extends from the side wall 2a to the other side in the axial direction, bends at a right angle, and extends outward in the radial direction. Further, the other end of the second pipeline 13 is connected to the other end of the third pipeline 14 in the axial direction.

  Further, a pair of rails 14 b and 14 b are integrally provided on the inner surface of the peripheral wall 14 a of the third conduit 14. For convenience, hatching indicating the cross section of the rails 14b and 14b is omitted in FIG. 2 and other drawings described later. As shown in FIG. 3, both 14b and 14b are arrange | positioned so that it may protrude a little in the radial direction of the 3rd pipe line 14, and mutually opposes in radial direction. Each rail 14 b extends in the axial direction over the entire portion between the connection portion of the third pipeline 14 with the first pipeline 12 and the connection portion of the second pipeline 13.

  In addition, support holes 14d and 14d penetrating in the axial direction are formed in the wall portions 14c and 14c at the one end portion and the other end portion of the third pipe line 14 in the axial direction. A bearing 22 is attached to the inner surface of each wall portion 14c, and a seal 23 is provided in each support hole 14d. The support hole 14 d, the thrust bearing 22, and the seal 23 are arranged coaxially in the third pipeline 14.

  The screw shaft 15 is inserted into the support holes 14b and 14b, is rotatably supported by the thrust bearings 22 and 22, and is partially accommodated in the third pipe line 14. It extends in the axial direction. Flange 15a, 15a is integrally provided on one side portion and the other side portion of screw shaft 15 in the axial direction, and these flanges 15a, 15a are thrust bearing 22 from the inside in the axial direction. , 22 are in contact with each other. With the above configuration, the screw shaft 15 can rotate with respect to the third pipeline 14 and cannot move in the axial direction.

  The second piston 16 includes a cylindrical nut 17, a first pressure receiving portion 18, and a second pressure receiving portion 19, and is accommodated in the third pipe 14. As shown in FIG. 4, the nut 17 is screwed to the screw shaft 15 via a ball 17 a and is rotatable with respect to the screw shaft 15. Thus, the screw shaft 15, the nut 17, and the ball 17a constitute a ball screw. The lead angles of the screw shaft 15 and the nut 17 are set to relatively small values.

  The first and second pressure receiving portions 18 and 19 are formed in a donut plate shape, have an outer diameter larger than that of the nut 17, and are integrally and coaxially fixed to both end portions in the axial direction of the nut 17. . As shown in FIGS. 3 and 4, the first pressure receiving portion 18 has a pair of recesses 18 a and 18 a formed on the outer peripheral portion thereof, and a seal 24 is attached to the outer peripheral surface thereof. Further, a guide hole 18b penetrating in the axial direction is formed at the radial center of the first pressure receiving portion 18, and a seal 25 is attached to the guide hole 18b.

  As with the first pressure receiving portion 18, the second pressure receiving portion 19 has a pair of recesses 19 a and 19 a formed on the outer peripheral portion thereof, and a seal 24 is attached to the outer peripheral surface thereof. Further, a guide hole 19b is formed at the radial center of the second pressure receiving portion 19, and a seal 25 is attached to the guide hole 19b.

  The first and second pressure receiving portions 18 and 19 are fitted to the inner peripheral surface of the third pipeline 14 via the seal 24, and the concave portions 18 a and 18 a and 19 a and 19 a are connected to the third pipeline 14. The rails 14 b and 14 b are engaged via a seal 24. Further, the screw shaft 15 is rotatably fitted to the guide holes 18 b and 19 b of the first and second pressure receiving portions 18 and 19 through a seal 25.

  With the above configuration, the second piston 16 can rotate with respect to the screw shaft 15, can slide in the third pipe line 14 along the screw shaft 15, and can move with respect to the third pipe line 14. It is impossible to rotate.

  Moreover, as shown in FIG. 2, the one end part and other end part of the screw shaft 15 become the protrusion parts 15b and 15b which protrude outside the wall parts 14c and 14c of the 3rd pipe line 14, and each protrusion The first rotating mass 21 is coaxially fixed to the portion 15b. The first rotating mass 21 is formed in a donut plate shape using a material having a relatively large specific gravity (for example, iron).

  FIG. 5 shows an example in which the vibration suppressing device 1 is installed in a structure (for example, a high-rise building) B1. As shown in the figure, the first fixture FL1 is connected to the lower beam BD1 via the elastic first support member SU1, and the second fixture FL2 is elastic to the second support member. The vibration suppression device 1 is connected in parallel to these beams BU1 and BD1 by being connected to the upper beam BU1 via SU2.

  When the structure B1 reciprocates due to vibration caused by an earthquake or the like, displacement between the upper and lower beams BU1 and BD1 (hereinafter referred to as “displacement of the structure B1”) is transmitted to the cylinder 2 and the rod 3, and accordingly, the rod 3 Reciprocates in the axial direction with respect to the cylinder 2. In this case, when the rod 3 moves from the neutral position to one side (left side in FIG. 2) in the axial direction with respect to the cylinder 2, the first piston 4 integral with the rod 3 slides in the cylinder 2 to one side. Accordingly, the hydraulic oil HF in the first oil chamber 2c is compressed, and the second oil chamber 2d expands.

  As a result, a part of the hydraulic oil HF in the first oil chamber 2c flows into the third pipe 14 via the first pipe 12 of the bypass pipe 11 and the first pressure receiving portion 18 of the second piston 16. Is pressed, the second piston 16 slides along the screw shaft 15 in the third pipe line 14 to the other side in the axial direction. Along with this, the screw shaft 15 screwed into the nut 17 of the second piston 16 via the ball 17a rotates with respect to the third conduit 14, and the first rotating masses 21, 21 integrated with the screw shaft 15 also rotate. To do.

  Contrary to the above, when the rod 3 moves from the neutral position to the other side in the axial direction with respect to the cylinder 2 (right side in FIG. 2), the first piston 4 slides in the cylinder 2 to the other side, Accordingly, the hydraulic oil HF in the second oil chamber 2d is compressed and the first oil chamber 2c is expanded. As a result, a part of the hydraulic oil HF in the second oil chamber 2d flows into the third pipe 14 via the second pipe 13 of the bypass pipe 11 and the second pressure receiving portion 19 of the second piston 16. , The second piston 16 slides along the screw shaft 15 in the third pipeline 14 to one side in the axial direction. Along with this, the screw shaft 15 rotates with respect to the third pipe 14, and the first rotation masses 21, 21 integrated with the screw shaft 15 also rotate.

  The lengths of the bypass passage 11 and the screw shaft 15 are set to values larger than the maximum movement amount of the second piston 16 accompanying the movement of the first piston 4.

  As described above, according to the first embodiment, the displacement of the structure B <b> 1 due to vibration is transmitted to the hydraulic oil HF via the rod 3 and the first piston 4, and further, the first or second pressure receiving portions 18, 19. The first rotary masses 21 and 21 are rotated by being transmitted to the first rotary masses 21 and 21 through the nut 17, the ball 17 a and the screw shaft 15. Therefore, the vibration of the structure B1 can be suppressed by the viscous damping effect of the hydraulic oil HF and the rotational inertia effect of the first rotating masses 21 and 21.

  In this case, unlike the above-described conventional case, the flow of the hydraulic oil HF is converted into a rotational motion by using a ball screw including the screw shaft 15, the nut 17 and the ball 17a and the second piston 16 instead of the impeller. In addition, the lead angles of the screw shaft 15 and the nut 17 are set to relatively small values. Therefore, even when the amount of movement of the second piston 16 is relatively small because the flow rate of the hydraulic oil HF is relatively small, the screw shaft 15 and the first rotary masses 21 and 21 can be sufficiently rotated. As described above, the displacement of the structure B1 can be efficiently converted into the rotational motion of the first rotating masses 21 and 21 via the hydraulic oil HF, and thereby the vibration of the structure B1 can be appropriately suppressed. .

  Moreover, since the vibration suppression device 1 is connected to the structure B1 via the first and second support members SU1 and SU2 having elasticity, the first and second support members SU1 and SU2 and the first rotation are connected to the structure B1. An additional vibration system can be configured by the mass 21 and the hydraulic oil HF. In the first embodiment, the cross-sectional area of the bypass pipe 11, the lead angle of the screw shaft 15 and the nut 17, the viscosity damping coefficient of the hydraulic oil HF, the mass of the first rotating mass 21, and the first and second support members SU1, SU2. Is set so that the natural frequency of the additional vibration system is tuned (resonated) with the primary natural frequency of the structure B1, for example.

  Therefore, the natural frequency of the additional vibration system can be appropriately tuned to the primary natural frequency of the structure B1, and hence vibration due to the primary mode of the structure B1 can be appropriately suppressed. The natural frequency of the structure B1 to be tuned is not limited to the primary natural frequency, and may be any other natural frequency.

  Further, in the adjustment of the natural frequency of the additional vibration system described above, specifically, by changing the cross-sectional area of the bypass pipe 11, the conversion efficiency into the rotational motion of the nut 17 with respect to the flow of the hydraulic oil HF, that is, the first. The rotational inertia effect of the rotary masses 21 and 21 and the viscous damping effect of the hydraulic oil HF can be adjusted. Furthermore, by changing the lead angle of the screw shaft 15 and the nut 17, the conversion efficiency of the nut 17 into the rotational motion with respect to the flow of the hydraulic oil HF, that is, the rotational inertia effect of the first rotary masses 21 and 21 can be adjusted. At the same time, the viscous damping effect of the hydraulic oil HF can be adjusted by changing the viscous damping coefficient of the hydraulic oil HF. Further, the rotational inertia effect of the first rotating masses 21 and 21 can be adjusted by changing the masses of the first rotating masses 21 and 21.

  Further, since the cross-sectional area of the bypass pipe 11 is set to a value smaller than the cross-sectional area of the cylinder 2, the second piston 16 in the bypass pipe 11 has an amount of movement of the first piston 4 in the cylinder 2. The amount of movement can be increased, and the amount of rotation of the first rotating masses 21 and 21 can be increased. Therefore, the rotational inertia force of the first rotating masses 21 and 21 can be obtained more appropriately, and as a result, the vibration of the structure B1 can be more appropriately suppressed.

  Moreover, since the 1st rotation masses 21 and 21 are arrange | positioned outside the bypass pipe 11, the adjustment of the mass of the 1st rotation masses 21 and 21 can be performed easily.

  Further, when the pressure of the hydraulic oil HF in the first or second oil chamber 2c, 2d reaches a predetermined value, that is, from the viscous damping force of the hydraulic oil HF and the rotational inertia force of the first rotary masses 21, 21. When the reaction force (axial force) of the vibration suppressing device 1 is relatively large, the two oil chambers 2c, 2d are communicated with each other by the first and second relief valves 7, 8. As a result, even if the first piston 4 slides in the cylinder 2, the compression of the hydraulic oil HF and the flow of the hydraulic oil HF are hardly performed in the cylinder 2, and the viscous damping force of the hydraulic oil HF and the first The rotational inertia force of the rotary masses 21 and 21 reaches a peak, and therefore, it is possible to prevent the excessive increase.

  In the first embodiment, the first rotary masses 21 and 21 are fixed to the screw shaft 15. However, the first rotary masses 21 and 21 are rotatably provided on the screw shaft 15 and are attached to the screw shaft 15 via an elastic body or a viscoelastic body. You may connect. In this case, since the additional vibration system is configured by these elastic bodies or viscoelastic bodies and the first rotating masses 21 and 21, the first and second support members SU1 and SU2 described above become unnecessary, and accordingly, The whole vibration suppression device 1 can be reduced in size. In the first embodiment, one set of the bypass pipe 11, the screw shaft 15, the second piston 16, and the first rotating masses 21 and 21 is provided, but two or more sets may be provided in parallel.

  Next, a vibration suppressing device 1A according to a second embodiment of the present invention will be described with reference to FIGS. FIG. 6 shows a model of the vibration suppression device 1A. As is clear from the comparison between FIG. 6 and FIG. 1 described above, the vibration suppression device 1A is the first in comparison with the first embodiment. The only difference is that the elastic element is connected in series with the first inertial connection element. Further, the first additional vibration system is constituted by the first elastic element, the first inertia connecting element, and the first viscous element.

  FIG. 7 shows the vibration suppressing device 1A as an embodiment. As shown in the figure, in the vibration suppressing device 1A, the first piston 34 and the second spring 35 corresponding to the first elastic element are provided in the second piston 31 as compared with the first embodiment. The point is mainly different. In FIG. 7, the same components 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.

  The 2nd piston 31 has the nut 17, the 1st pressure receiving part 18, and the 2nd pressure receiving part 19 similarly to the 2nd piston 16 of 1st Embodiment. The first and second pressure receiving portions 18 and 19 are not integrally fixed to the nut 17, and the first flange 32 and the second flange 33 are coaxially fixed to both ends of the nut 17 in the axial direction. Has been.

  These first and second flanges 32 and 33 are basically configured in the same manner as the first and second pressure receiving portions 18 and 19, respectively, and are recessed portions that engage with the rail 14 b of the third pipeline 14. , And a guide hole (both not shown) into which the screw shaft 15 is inserted is provided. Unlike the first and second pressure receiving portions 18 and 19, the first and second flanges 32 and 33 are not provided with the seals 24 and 25.

  The first pressure receiving portion 18 is provided on one side in the axial direction with respect to the nut 17, and is attached to the first flange 32 via the first spring 34. The second pressure receiving portion 19 is provided on the other side in the axial direction with respect to the nut 17, and is attached to the second flange 33 via the second spring 35. Both the first and second springs 34 and 35 are compression coil springs, and the spring constants of both the springs 34 and 35 are set to the same value. Details thereof will be described later.

  With the above configuration, the second piston 31 having the first and second pressure receiving portions 18 and 19, the first and second springs 34 and 35, the first and second flanges 32 and 33, and the nut 17 is attached to the screw shaft 15. The third pipe 14 can be slid along the screw shaft 15 and cannot be rotated with respect to the third pipe 14.

  FIG. 8 shows an example in which the vibration suppressing device 1A is installed in a structure (for example, a high-rise building) B2. As shown in the figure, the first fixture FL1 is directly connected to the connection portion between the left pillar PL of the structure B2 and the upper beam BU2, and the second fixture FL2 is directly connected to the structure B2. It is connected to a connection portion between the right column PR and the lower beam BD2, so that the vibration suppressing device 1A is obliquely attached to these columns PL, PR and beams BU2, BD2. .

  When the structure B2 reciprocates due to vibration caused by an earthquake or the like, displacement between the left and right columns PL, PR and the upper and lower beams BU, BD (hereinafter referred to as “displacement of the structure B2”) is transmitted to the cylinder 2 and the rod 3. Accordingly, the rod 3 reciprocates in the axial direction with respect to the cylinder 2. In this case, when the rod 3 moves from the neutral position to one side in the axial direction (left side in FIG. 7) with respect to the cylinder 2, the first piston 4 integrated with the rod 3 slides in the cylinder 2 to one side. Accordingly, the hydraulic oil HF in the first oil chamber 2c is compressed, and the second oil chamber 2d expands.

  As a result, a part of the hydraulic oil HF in the first oil chamber 2c flows into the third pipe 14 via the first pipe 12 of the bypass pipe 11, and the first pressure receiving portion 18 of the second piston 31. Press. The pressing force of the hydraulic oil HF is transmitted to the nut 17 via the first pressure receiving portion 18, the first spring 34, and the first flange 32, whereby the entire second piston 31 including the nut 17 is screwed to the screw shaft 15. Along the second pipe 14 in the axial direction. Along with this, the screw shaft 15 rotates with respect to the third pipe 14, and the first rotation masses 21, 21 integrated with the screw shaft 15 also rotate.

  Contrary to the above, when the rod 3 moves from the neutral position to the other side in the axial direction with respect to the cylinder 2 (right side in FIG. 7), the first piston 4 slides in the cylinder 2 to the other side, Accordingly, the hydraulic oil HF in the second oil chamber 2d is compressed and the first oil chamber 2c is expanded. As a result, part of the hydraulic oil HF in the second oil chamber 2d flows into the third pipe 14 via the second pipe 13 of the bypass pipe 11, and the second pressure receiving portion 19 of the second piston 31. Press. The pressing force of the hydraulic oil HF is transmitted to the nut 17 via the second pressure receiving portion 19, the second spring 35 and the second flange 33, so that the entire second piston 31 including the nut 17 is screwed to the screw shaft 15. Along the line, the inside of the third pipeline 14 is slid to one side in the axial direction. Along with this, the screw shaft 15 rotates with respect to the third pipe 14, and the first rotation masses 21, 21 integrated with the screw shaft 15 also rotate.

  As described above, according to the second embodiment, the displacement of the structure B2 due to the vibration causes the hydraulic oil HF, the first pressure receiving portion 18 and the first spring 34 to move when the first piston 4 slides to one side. Then, when the first piston 4 slides to the other side, it is transmitted to the nut 17 via the hydraulic oil HF, the second pressure receiving portion 19 and the second spring 35, and further to the first rotation via the screw shaft 15. As a result of being transmitted to the masses 21 and 21, the first rotary masses 21 and 21 rotate. In this way, the first additional vibration system including the hydraulic oil HF, the first or second springs 34 and 35, and the first rotating masses 21 and 21 is configured with respect to the reciprocating motion of the structure B2 due to vibration.

  In the second embodiment, the cross-sectional area of the bypass pipe 11, the lead angle of the screw shaft 15 and the nut 17, the viscosity damping coefficient of the hydraulic oil HF, the mass of the first rotating masses 21 and 21, and the first and second springs 34, The spring constant of 35 is set so that the natural frequency of the first additional vibration system is tuned (resonated) to the primary natural frequency of the structure B2, for example.

  Therefore, the natural frequency of the first additional vibration system can be appropriately tuned to the primary natural frequency of the structure B2, and hence vibration due to the primary mode of the structure B2 can be appropriately suppressed. The natural frequency of the structure B2 to be tuned is not limited to the primary natural frequency, and may be any other natural frequency.

  In the adjustment of the natural frequency of the first additional vibration system described above, specifically, by changing the cross-sectional area of the bypass pipe 11, the conversion efficiency of the nut 17 into the rotational motion with respect to the flow of the hydraulic oil HF, that is, The rotational inertia effect of the first rotary masses 21 and 21 and the viscous damping effect of the hydraulic oil HF can be adjusted. Furthermore, by changing the lead angle of the screw shaft 15 and the nut 17, the conversion efficiency of the nut 17 into the rotational motion with respect to the flow of the hydraulic oil HF, that is, the rotational inertia effect of the first rotary masses 21 and 21 can be adjusted. At the same time, the viscous damping effect of the hydraulic oil HF can be adjusted by changing the viscous damping coefficient of the hydraulic oil HF. Further, the rotational inertia effect of the first rotating masses 21 and 21 can be adjusted by changing the masses of the first rotating masses 21 and 21.

  Furthermore, since the cross-sectional area of the bypass pipe 11 is set to a value smaller than the cross-sectional area of the cylinder 2, the pressing force of the hydraulic oil HF acting on the second piston 16 is used as the hydraulic oil HF acting on the first piston 4. Therefore, the first and second springs 34 and 35 can be compact with a small spring constant.

  Further, unlike the first embodiment, the first additional vibration system can be configured by using the first and second springs 34 and 35 provided in the third pipeline 14, and thereby the first and second support members SU1. Since SU2 is unnecessary, the vibration suppression device 1A as a whole can be reduced in size accordingly. In addition, the effect by 1st Embodiment can be acquired similarly.

  Next, a vibration suppression device 1B according to a third embodiment of the present invention will be described with reference to FIG. The vibration suppressing device 1B is different from the second embodiment only in that the spring constants of the first and second springs 41 and 42 are set to different values. In FIG. 9, the same components as those of the second embodiment are denoted by the same reference numerals. Hereinafter, a description will be given focusing on differences from the second embodiment.

  As is apparent from the operation of the vibration suppression device 1A described in the second embodiment, in the vibration suppression device 1B according to the third embodiment, the displacement of the structure B2 due to vibration causes the first piston 4 to slide to one side. When the first piston 4 slides to the other side, the hydraulic oil HF, the second pressure receiving portion 19 and the second spring 42 are used. As a result of being transmitted to the nut 17 and further transmitted to the first rotating masses 21 and 21 via the screw shaft 15, the first rotating masses 21 and 21 rotate. Thus, with respect to the reciprocating motion of the structure B2 due to vibration, the first additional vibration system including the hydraulic oil HF, the first spring 41, and the first rotating masses 21, 21; the hydraulic oil HF, the second spring 42, and A second additional vibration system including the first rotating masses 21 and 21 is configured.

  In the third embodiment, the spring constant of the first spring 41, the cross-sectional area of the bypass pipe 11, the lead angle of the screw shaft 15 and the nut 17, the viscosity damping coefficient of the hydraulic oil HF, and the mass of the first rotating masses 21 and 21 are as follows. The natural frequency of the first additional vibration system is set so as to tune (resonate) with the primary natural frequency of the structure B2, for example. The spring constant of the second spring 42, the cross-sectional area of the bypass pipe 11, the lead angle of the screw shaft 15 and the nut 17, the viscosity damping coefficient of the hydraulic oil HF, and the mass of the first rotating masses 21 and 21 are as described above. The natural frequency of the 2-addition vibration system is set so as to tune (resonate) with the secondary natural frequency of the structure B2, for example.

  As a result, the natural frequencies of the first and second additional vibration systems can be multiple-tuned to the primary and secondary natural frequencies of the structure B2, respectively. Therefore, the vibration of the structure B2 in the primary and secondary vibration modes is caused by the vibration suppression device 1B including the hydraulic oil HF, the first rotary masses 21 and 21, the first spring 41, the second spring 42, and the like. It is possible to suppress appropriately, and as a result, further downsizing of the apparatus can be achieved. The natural frequency of the structure B2 to be tuned is not limited to the primary and secondary natural frequencies, and may be any other natural frequency. In addition, the effect by 1st and 2nd embodiment can be acquired similarly.

  In the second and third embodiments, the bypass pipe 11, the screw shaft 15, the second piston 16, the first rotating masses 21 and 21, the first and second springs 34 and 35 (41 and 42), one set, Although provided, two or more sets may be provided in parallel. In this case, the mass or the like of the first rotating mass may be set so that the natural frequencies of the plurality of additional vibration systems constituted thereby are synchronized with the same desired natural frequency of the structure B2. Alternatively, it may be set to tune to a plurality of different desired natural frequencies of the structure B2.

  Next, a vibration suppression device 1C according to a fourth embodiment of the present invention will be described with reference to FIGS. FIG. 10 shows a model of the vibration suppression device 1C. As is clear from a comparison between FIG. 10 and FIG. 6 described above, the vibration suppression device 1C is a second type compared to the second embodiment. The only difference is that the elastic element and the second inertial connection element are connected in parallel to the first inertial connection element. Further, the second additional vibration system is constituted by the second elastic element and the second inertia connecting element.

  FIG. 11 illustrates the vibration suppressing device 1C as embodied. As shown in the figure, compared with the second embodiment, the vibration suppressing device 1C includes a spring 51 corresponding to the second elastic element and second rotating masses 52 and 52 corresponding to the second inertia connecting element. The only difference is that In FIG. 11, the same components as those in the first and second embodiments are denoted by the same reference numerals. The following description will focus on differences from the first and second embodiments.

  The second rotating masses 52, 52 are formed in a donut plate shape using a material having a relatively large specific gravity (for example, iron), and are arranged on the projecting portions 15b, 15b of the screw shaft 15 via radial bearings 53, 53. Thus, it is rotatably supported coaxially. Each second rotating mass 52 is attached to the first rotating mass 21 via a spring 51 and is rotatable with respect to the first rotating mass 21. The spring 51 is a torsion coil spring.

  The vibration suppressing device 1C having the above configuration is attached to the structure B2 in the same manner as in the second embodiment, for example. When the structure B2 reciprocates due to vibration caused by an earthquake or the like, the displacement of the structure B2 is transmitted to the cylinder 2 and the rod 3 as in the second embodiment, and further transmitted to the second piston 31 via the hydraulic oil HF. As a result, the screw shaft 15 rotates together with the first rotation masses 21 and 21. Further, as the first rotating masses 21 and 21 rotate, the second rotating masses 52 and 52 rotate.

  As described above, according to the fourth embodiment, in addition to the viscous damping effect of the hydraulic oil HF and the rotational inertia effect of the first rotary masses 21 and 21, the rotational inertia effect of the second rotary masses 52 and 52 allows the structure B2 to Vibration can be suppressed more appropriately.

  Since the second rotating masses 52 and 52 are attached to the first rotating masses 21 and 21 via the springs 51, in addition to the first additional vibration system described in the second embodiment, the springs 51 and 2 A second additional vibration system including the rotary masses 52 and 52 can be further configured. In this case, as is clear from FIG. 10, two combined natural frequencies exist separately as the natural frequencies of the additional vibration system configured by combining the first and second additional vibration systems.

  In the fourth embodiment, the cross-sectional area of the bypass pipe 11, the lead angle of the screw shaft 15 and the nut 17, the viscosity damping coefficient of the hydraulic oil HF, the mass of the first rotating masses 21 and 21, and the first and second springs 34 and 35. , The mass of the second rotating masses 52 and 52, and the spring constant of the spring 51 are respectively tuned (resonant) to the first and second natural frequencies of the structure B2, for example. ) Is set to.

  Therefore, the two combined natural frequencies of the first and second additional vibration systems can be appropriately multiple-tuned to the primary and secondary natural frequencies of the structure B2, respectively. Vibration due to the secondary mode can be appropriately suppressed. The natural frequency of the structure B2 to be tuned is not limited to the primary and secondary natural frequencies, but may be any other two different natural frequencies. Alternatively, the two combined natural frequencies may be tuned to the same single natural frequency of the structure B2.

  Further, in the adjustment of the natural frequencies of the first and second additional vibration systems described above, specifically, by changing the cross-sectional area of the bypass pipe 11, the nut 17 rotates to the movement of the hydraulic oil HF. The conversion efficiency, that is, the rotational inertia effect of the first and second rotary masses 21, 21, 52, and 52 and the viscous damping effect of the hydraulic oil HF can be adjusted.

  Further, by changing the lead angle of the screw shaft 15 and the nut 17, the conversion efficiency of the nut 17 into the rotational motion with respect to the flow of the hydraulic oil HF, that is, the rotational inertia of the first and second rotary masses 21, 21, 52, 52. The effect can be adjusted, and the viscosity damping effect of the hydraulic oil HF can be adjusted by changing the viscosity damping coefficient of the hydraulic oil HF. Further, by changing the masses of the first and second rotating masses 21, 21, 52, 52, the rotational inertia effects of the first and second rotating masses 21, 21, 52, 52 can be adjusted, respectively.

  Moreover, since the 2nd rotation mass 52 and 52 is arrange | positioned outside the bypass pipe 11 similarly to the 1st rotation mass 21 and 21, the setting of the mass of the 2nd rotation mass 52 and 52 can be performed easily. it can. In addition, the effect by 1st and 2nd embodiment can be acquired similarly.

  In the fourth embodiment, the spring 51 is a torsion coil spring, but may be another elastic body such as rubber. Moreover, in 4th Embodiment, although the 2nd rotation mass 52 is attached to the 1st rotation mass 21 via the spring 51, you may attach via the viscous body which has viscosity further. Alternatively, instead of the spring 51, it may be attached via a viscoelastic body having both elasticity and viscosity, for example, viscoelastic rubber.

  Furthermore, in the fourth embodiment, as described in the second embodiment, the first and second springs 34 and 35 in which the spring constants are set to the same value are used, but instead of both 34 and 35, The first and second springs 41 and 42 in which the spring constants described in the third embodiment are set to different values may be used. In this case, as the natural frequency of the additional vibration system configured by the combination of the first and second additional vibration systems, four combined natural frequencies exist separately.

  Further, the cross-sectional area of the bypass pipe 11, the lead angle of the screw shaft 15 and the nut 17, the viscosity damping coefficient of the hydraulic oil HF, the mass of the first rotating masses 21 and 21, the spring constant of the first and second springs 41 and 42, The masses of the second rotating masses 52 and 52 and the spring constant of the spring 51 are, for example, such that the above-described four combined natural frequencies are respectively tuned (resonated) with the primary to fourth-order natural frequencies of the structure B2. To be set. The natural frequency of the structure B2 to be tuned is not limited to the primary to quaternary natural frequencies, and may be any other natural frequency.

  Further, in the fourth embodiment, the bypass pipe 11, the screw shaft 15, the second piston 16, the first rotating masses 21 and 21, the second rotating masses 52 and 52, the first and second springs 34 and 35, one set, Although provided, two or more sets may be provided in parallel. In this case, the mass or the like of the first rotating mass may be set so that the natural frequencies of the plurality of additional vibration systems constituted thereby are synchronized with the same desired natural frequency of the structure B2. Alternatively, it may be set to tune to a plurality of different desired natural frequencies of the structure B2.

  In the second to fourth embodiments, the first and second springs 34, 41, 35, 42 are compression coil springs, but may be other elastic bodies such as rubber.

  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 working oil HF is used as the working fluid of the present invention, but other suitable fluid having viscosity may be used. Further, in the embodiment, in order to make the second pistons 16 and 31 non-rotatable with respect to the bypass pipe 11 (third pipe line 14), the rail 14b is provided with the concave portions 18a of the first and second pressure receiving parts 18 and 19, 19a (the recesses of the flanges 32 and 33) are engaged, but without providing the rails 14b and the recesses 18a and 19a, the bypass pipe and the second piston are formed in a rectangular cross section, and the bypass pipe Two pistons may be slidably fitted.

  Furthermore, in the embodiment, the first and second rotating masses 21, 21, 52, and 52 are provided outside the third pipeline 14 of the bypass pipe 11, but may be provided inside thereof. In the embodiment, the first and second relief valves 7 and 8 are provided in the first piston 4, but the first piston 4 is bypassed in the cylinder 2 and the first and second oil chambers 2c and 2d are bypassed. Further, a bypass pipe communicating with each other may be further provided, and the first and second relief valves may be provided in the bypass pipe. Further, one or both of the first and second relief valves 7 and 8 may be omitted.

  In the embodiment, the vibration suppression devices 1 and 1A to 1C are installed between the structures B1 and B2 and used as so-called vibration control devices. However, the structures B1 and B2 and a support body that supports the structures B1 and B2 It may be installed between and used as a so-called seismic isolation device. Further, the embodiment is an example in which the present invention is applied to the structures B1 and B2 which are high-rise buildings. However, the vibration suppression device according to the present invention can be applied to other suitable structures such as bridges and steel towers. Applicable. In addition, it is possible to appropriately change the detailed configuration within the scope of the gist of the present invention.

DESCRIPTION OF SYMBOLS 1 Vibration suppression apparatus 2 Cylinder 2c 1st oil chamber (1st pressure chamber)
2d Second oil chamber (second pressure chamber)
3 Rod 4 1st piston 7 1st relief valve (Relief valve)
8 Second relief valve (Relief valve)
HF hydraulic oil (working fluid)
11 Bypass pipe (bypass passage)
15 Screw shaft 16 Second piston 17 Nut 17a Ball 18 First pressure receiving portion 19 Second pressure receiving portion 21 First rotating mass (rotating mass)
B1 Structure BD1 Lower beam (one of the two parts in the system including the structure)
BU1 Upper beam (the other of the two parts in the system including the structure)
1A Vibration Suppressing Device 31 Second Piston 34 First Spring (First Elastic Body)
35 Second spring (second elastic body)
B2 Structure PL Left column (one of the two parts in the system including the structure)
BU2 Upper beam (one of the two parts in the system including the structure)
PR Right column (the other of the two parts in the system including the structure)
BD2 Lower beam (the other of the two parts in the system including the structure)
1B Vibration Suppressing Device 41 First Spring (First Elastic Body)
42 Second spring (second elastic body)
1C Vibration suppression device 51 Spring (elastic body)
52 Second rotating mass (Rotating mass)

Claims (7)

A vibration suppression device provided between two parts in a system including a structure, for suppressing vibration of the structure,
A cylinder connected to one of the two parts and filled with a working fluid;
A rod connected to the other of the two parts, partially accommodated in the cylinder, and movable in the axial direction with respect to the cylinder;
A first piston fixed integrally with the rod and sliding in the cylinder as the rod moves;
A bypass passage connected to the cylinder to bypass the first piston;
A screw shaft rotatably provided in the bypass passage and extending in the axial direction of the bypass passage;
A second piston that has a nut screwed to the screw shaft via a ball, is slidable in the bypass passage along the screw shaft, and is not rotatable with respect to the bypass passage;
A rotatable rotating mass attached to the screw shaft;
A vibration suppressing device comprising: The second piston is
A first pressure receiving portion provided on one side of the axial direction with respect to the nut and pressed by a working fluid that flows as the first piston slides on one side of the cylinder;
A second pressure receiving portion that is provided on the other side in the axial direction with respect to the nut and is pressed by the working fluid that flows as the first piston slides on the other side of the cylinder;
A first elastic body provided between the nut and the first pressure receiving portion, for transmitting a pressing force of the working fluid acting on the first pressure receiving portion to the nut;
A second elastic body, which is provided between the nut and the second pressure receiving portion and transmits a pressing force of the working fluid acting on the second pressure receiving portion to the nut. Item 2. The vibration suppression device according to Item 1.   The vibration suppression device according to claim 2, wherein the spring constant of the first elastic body and the spring constant of the second elastic body are set to different values. The rotating mass is
A first rotating mass attached to the screw shaft and rotatable;
The vibration suppressing device according to claim 2, further comprising a second rotating mass attached to the first rotating mass via an elastic body and rotatable with respect to the first rotating mass. .   The vibration suppressing device according to any one of claims 1 to 4, wherein a cross-sectional area of the bypass passage is smaller than a cross-sectional area of the cylinder. The screw shaft extends outside the bypass passage,
The vibration suppressing device according to claim 1, wherein the rotating mass is arranged outside the bypass passage. In the cylinder, a first pressure chamber and a second pressure chamber communicating with the bypass passage are defined on both sides of the first piston,
A relief that communicates the first and second pressure chambers by opening the valve when one of the pressure of the working fluid in the first pressure chamber and the pressure of the working fluid in the second pressure chamber reaches a predetermined value. The vibration suppressing device according to any one of claims 1 to 6, further comprising a valve.

Images