JP2015137658A - vibration reduction device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration reduction device reduced in size so as to be preferably applied to a short span structure (a structure of short span engine frame) while combining a fluid pressure cylinder mechanism acting as a rational speed increasing mechanism against a rotary inertia mass mechanism and further realizing a superior vibration reducing performance.SOLUTION: This invention is constituted by a plurality of main damper units 32 present between the two members vibrated in relative manner to reduce a relative vibration and a sub-damper unit 36 separated from the main damper units 32. Several main damper units 32 comprise a main cylinder 30, a main piston 31 and a piston rod 39. The sub-damper unit 36 comprises a sub-cylinder 33, a fluid pressure cylinder mechanism 60 arranged in one inner space defined by a partition wall 61 of the sub-cylinder 33; and a rotary inertia mass mechanism 35 arranged in the other inner space. Then, several main damper units 32 are constituted while being connected in parallel with the sub-damper unit 36.

Description

  The present invention is a vibration reduction device that is interposed between two members that vibrate relative to each other and reduces the relative vibration, and particularly uses the inertial force generated by the rotating weight as a reaction force (belonging to a rotary inertial mass mechanism). Relates to the device.

As is well known, the rotational inertial mass mechanism is a device that generates a reaction force proportional to the relative acceleration at both ends of the inertial mass damper, and includes a damping piece shown in Patent Document 1 and a seismic isolation device shown in Patent Document 2 and Patent Document 3. Has been put to practical use. On the other hand, a rotary inertia mass mechanism that can obtain an inertial mass effect several thousand times as large as the actual mass of the rotary weight by using a ball screw mechanism is becoming widespread.
In a rotary inertia mass mechanism using such a ball screw mechanism, the inertia mass ψ is expressed by the following equation, where the rotary inertia moment I _θ of the rotary weight and the lead L _{d of the} ball screw are expressed as follows.

  For example, as shown in Patent Document 4 and Patent Document 5, a fluid-type rotary inertia mass mechanism (inertia pump damper) that utilizes the inertial mass of a fluid is also known. This fluid type rotary inertial mass mechanism recirculates a fluid (liquid) divided in a cylinder through a connecting pipe (bypass pipe) smaller in diameter than the cylinder diameter while applying pressure due to damper displacement. By increasing the reflux speed, an inertial mass effect larger than the fluid mass in the communication pipe can be obtained.

Here, since the reaction force generated in this type of rotary inertial mass mechanism is proportional to the relative acceleration, the relative displacement, speed and acceleration acting on both ends of the damper are multiplied by α on the output side using an amplification mechanism (acceleration mechanism). In this case, the damper reaction force installed on the output side is also multiplied by α.
Further, since the reaction force of the amplifying mechanism is α times larger on the input side than on the output side, the inertial mass Ψ (damper specifications) of the damper member is α ² times that of the above equation (1). This can be easily understood if the energy on the input side and the output side (displacement x force) are the same.

  For this reason, it is effective to combine an amplifying mechanism with a rotary inertial mass mechanism. Conventionally, devices using an amplifying mechanism using an insulator or a toggle mechanism have been proposed and put into practical use, but both In addition, a large space is required, and deformation loss due to looseness in the pin coupling portion is a problem, and it is difficult to realize a compact and large capacity damper. In addition, an apparatus using an amplifying mechanism using a planetary gear has been proposed, but the energy loss due to internal friction of the amplifying mechanism itself is large, and there has been a strong demand to develop a more rational speed-up method.

On the other hand, first, in a device using a fluid such as an oil damper (vibration reducing device, damping damper device), a reaction force proportional to the piston area and an inverse proportional displacement can be easily obtained, and energy loss is also small. Are known. That is, as is apparent from Pascal's principle, for example, when two pipe bodies (areas A ₁ : A ₂ = α: 1) having different cross-sectional areas shown in FIG. The amount (displacement) is 1: α, and the force is α: 1. That is, when the left large-area tube body in FIG. 11 is used as a reference, the right small-area tube body has a force that is 1 / α times and a displacement that is expanded α times.

  Then, an amplifying mechanism (speed increasing mechanism) that expands the damper displacement by using this principle is used, and as shown in FIG. 12, a communication pipe that communicates the internal spaces 3 and 4 defined by the piston 2 of the fluid pressure cylinder mechanism 1. As a result of examining the method of combining the rotary inertial mass mechanism 6 with 5, it was confirmed that the inertial mass effect equivalent to or higher than that of the conventional rotary inertial mass mechanism can be exhibited even if the external dimensions are significantly smaller. However, when configured in this way, a considerably large reaction force is generated in the communication pipe 5 and the rotary inertia mass mechanism 6, and therefore, by responding to the eccentric bending moment generated by the displacement of the fluid pressure cylinder mechanism 1 and the axis. There was a risk that the cost would increase.

  On the other hand, as shown in FIG. 13, the inventor of the present application houses the rotary inertia mass mechanism 8 inside the main cylinder 7 and forms a hydraulic mechanism (without the force in the axis O1 direction from the outside of the cylinder 7). A vibration reduction device A (hybrid rotary inertial mass mechanism) combining the fluid pressure cylinder mechanism 9 and the rotary inertial mass mechanism 8 has been devised, and a patent application has already been filed (Japanese Patent Application No. 2013-034738).

  More specifically, the vibration reducing device A is configured by providing a sub cylinder 10 having an outer diameter smaller than that of the main cylinder 7 in the main cylinder 7 so that the axis O1 is coaxially arranged. ing. At this time, the sub-cylinder 10 defines the inside 11 on the one end 7a side and the inside 12 on the other end 7b side of the main cylinder 7 in the axis O1 direction so that the inside 11 on one end side and the insides 11 and 13 communicate with each other. It is arranged. A sub piston 15 integrated with one end of the ball screw 14 is installed in the sub cylinder 10 so as to be movable (displaceable) in the direction of the axis O1. Thus, the interior 13 of the sub cylinder 10 is partitioned into one internal space 16 on the one end 7a side of the main cylinder 7 with the sub piston 15 therebetween, and the other internal space 17 in which the ball screw 14 is inserted. Yes.

  A main piston 18 is disposed in one internal space 11 on the one end 7 a side of the main cylinder 7, and the internal space 19 on the one end 7 a side and the ball screw 14 of the sub piston 15 are inserted between the main piston 18. The arranged internal space 17 communicates with the connecting pipe (bypass pipe) 20. Further, in the other inner space 12 on the other end 7b side of the main cylinder 7, an outer ring 21a is fixed to the main cylinder 7, and a bearing comprising an inner ring 21b supported rotatably around the axis O1 with respect to the outer ring 21a. 21 is provided, and a ball nut 22 is fixedly provided on an inner ring 21 b of the bearing 21. Then, the ball screw 14 and the ball nut 22 are screwed together so that the ball nut 22 can be rotated and restrained so as not to move (displaceable) in the direction of the axis O1.

Further, as shown in FIGS. 13 and 14, a substantially disk-shaped rotation restraining plate 23 is integrally attached to the other end side of the ball screw 14 with the central axes O1 being coaxially arranged. Since the restraint plate 23 is restrained so as not to rotate and is movable in the direction of the axis O1, the ball screw 14 is restrained so as not to be rotatable around the axis O1 and is movable in the direction of the axis O1. Further, the rotation restraint plate 23 is provided with restoring springs (restoring mechanisms) 24 and 25 that expand and contract in the axis O1 direction on both sides in the axis O1 direction. Furthermore, working oil (working fluid) is filled in the internal spaces 11 and 13 of the main cylinder 7 and the sub piston 15.
In this vibration reducing device A, the threaded portion of the ball screw 14 and the ball nut 22 is filled with grease, and there is no hydraulic oil.

In the vibration reducing device A configured as described above, the ball screw type rotary inertia mass mechanism 8 directly connected to the sub piston 15 with respect to the displacement X ₁ and the force F ₁ acting on the main piston is multiplied by α times. Displacement (X ₂ = αX ₁ ), α times acceleration (X ₂ (“••” on X ₂ ) = αX ₁ (“••” on X ₁ ))), 1 / α force (F ₂ = F ₁ / α) will act. As a result, the damper connected to the main piston 18 has the burden force F ₂ α times and the relative acceleration 1 / α relative to the inertia mass ψ ₂ of the rotary inertia mass mechanism 8 that is actually mounted, and the force inertial mass to be expressed by the ratio of the acceleration is alpha ² times.

  Therefore, in this vibration reducing apparatus A, since the force acting on the ball screw 14 is small, a large capacity damper can be realized using the inexpensive ball screw 14.

  As shown in Patent Document 6, a sub-cylinder is provided outside the main cylinder, both cylinders are connected by a bypass pipe, and a ball screw is screwed into a ball nut integrated with the sub-piston so that the outside of the sub-cylinder A mechanism is known that extends up to 1 and integrates a rotating weight. This is a ball screw and a rotating spindle that rotate when the ball nut is rotationally restrained and moves axially. The ball nut and ball nut filled with grease are directed to the same performance. The problem remains in that the oil is placed in the oil (hydraulic oil) in the cylinder and the sealing performance against the hydraulic pressure.

JP-A-11-201224 Japanese Patent No. 3250795 JP 2007-10110 A JP 2007-205433 A JP 2011-158015 A Japanese Patent No. 5161395

  However, in the above vibration reduction device (hybrid rotary inertia mass mechanism) by the inventors of the present application, in particular, one end of the main cylinder that houses the sub cylinder inside the main cylinder and communicates with the internal space on one end side of the sub cylinder. Since the main piston is arranged in the internal space on the side, the entire length of the damper becomes long and it is difficult to apply to the short span structure, and there is still room for further improvement in this respect.

  It has also been desired to further improve the vibration reduction performance.

  In view of the above circumstances, the present invention is suitable for a short-span structure (short-span frame structure) while being provided with a fluid pressure cylinder mechanism as a rational speed increasing mechanism in addition to a rotary inertia mass mechanism. It is an object of the present invention to provide a vibration reduction device that can be made compact so that it can be applied to and that exhibits excellent vibration reduction performance.

  In order to achieve the above object, the present invention provides the following means.

  The vibration reducing device of the present invention is a vibration reducing device for reducing relative vibration between two members that vibrate relatively, and is disposed between the two members to reduce relative vibration. A main damper portion and a sub-damper portion disposed separately from the plurality of main damper portions, wherein the plurality of main damper portions respectively include a main cylinder and a first compartment inside the main cylinder. And a main piston that is partitioned into a second compartment, and a piston rod that is connected to the main piston and extends outward in the axial direction of the main cylinder. And a fluid pressure cylinder mechanism as an amplification mechanism disposed in the internal space of the sub-cylinder, and a rotary inertia mass mechanism, and the fluid pressure cylinder machine Is disposed in the internal space so as to be slidable in the axial direction of the sub-cylinder and divides the internal space into a third compartment and a fourth compartment, and is connected to the sub-piston and extends. The rotary inertial mass mechanism includes a ball screw connected to the sub piston rod, a ball nut screwed to the ball screw, and an axis line driven by the ball nut. And a plurality of main damper portions each communicating the first compartment and the third compartment of the sub-damper portion with a first connecting pipe. The second compartment and the fourth compartment of the sub-damper part are communicated with each other by a second connecting pipe, and are connected in parallel to the sub-damper part, the first compartment and the first Two compartments, the third compartment and A serial fourth compartment, said a first connecting tube, characterized in that it is constituted by filling the working fluid to the second communication pipe.

  In the vibration reducing device of the present invention, at least one of the main piston of each of the main damper portions and the sub piston of the sub damper portion may include the first compartment, the second compartment, and / or the It is desirable that an orifice for communicating the third compartment and the fourth compartment is provided.

  Furthermore, in the vibration reducing device according to the present invention, a differential pressure between the first compartment and the second compartment is applied to at least one of the main piston of each main damper portion and the sub-piston of the sub damper portion. And / or when the differential pressure between the third compartment and the fourth compartment exceeds a preset relief pressure, the working fluid is passed between the first compartment and the second compartment. It is more desirable to provide a relief valve that circulates between the third compartment and the fourth compartment.

  In the vibration reduction device of the present invention, the main damper portion and the sub-damper portion are separated and configured separately, so that only the main damper portion is installed in the frame surface of a structure such as a building. Can be installed at an arbitrary position.

  At this time, the main damper part and the sub-damper part are separated so that the main damper part that needs to be installed in the frame is the simplest mechanism, i.e., a hydraulic mechanism composed of a main cylinder and a main piston. It will be comprised only by a fluid pressure cylinder mechanism, and length can be shortened.

  Furthermore, by connecting a plurality of main damper parts (n main damper parts) in parallel to the sub damper part, it is possible to configure a displacement enlarging mechanism that enlarges the displacement of one sub damper part n times. It becomes possible.

  As a result, it can be installed even within the frame surface of a short span structure, and the vibration damping performance (vibration reduction performance) can be improved reliably and effectively regardless of the structure of the frame. . That is, it is possible to realize a vibration reduction device that is excellent in versatility and excellent in vibration damping performance.

It is a figure which shows the vibration reduction apparatus which concerns on one Embodiment of this invention. It is the X1-X1 arrow view figure of FIG. It is a figure which shows the state which installed the vibration reduction apparatus which concerns on one Embodiment of this invention in the frame of a building. FIG. 4 is a view taken along line X1-X1 in FIG. 3. Fig. 5 shows the relationship between the load and horizontal displacement of a vibration reducing device (Fig. 5 (a)) having one main damper portion and a vibration reducing device (Fig. 5 (b)) having two (multiple) main damper portions. It is a figure. It is a figure which shows the modification of the vibration reduction apparatus which concerns on one Embodiment of this invention. It is a figure which shows the modification of the vibration reduction apparatus which concerns on one Embodiment of this invention. It is a figure which shows the modification of the vibration reduction apparatus which concerns on one Embodiment of this invention. It is a figure which shows the modification of the vibration reduction apparatus which concerns on one Embodiment of this invention. It is a figure which shows the modification of the vibration reduction apparatus which concerns on one Embodiment of this invention. It is a figure which shows the principle of Pascal. It is a figure which shows the conventional vibration reduction apparatus. It is a figure which shows the conventional vibration reduction apparatus. It is a X1-X1 line arrow line view of FIG.

  Hereinafter, a vibration reducing apparatus according to an embodiment of the present invention will be described with reference to FIGS.

  The vibration reducing apparatus according to the present embodiment is an apparatus for reducing the relative vibration of two members of a frame that is installed in a frame surface surrounded by pillars and beams of a building and that relatively vibrates due to an earthquake or the like. .

  As shown in FIGS. 1 and 2, the vibration reduction device B according to the present embodiment includes a plurality of main damper portions 32 having a main cylinder 30 and a main piston 31 (in this embodiment, two main damper portions 32a and 32b). ), A sub-cylinder 33, a sub-piston 34, and a sub-damper part 36 having a rotary inertia mass mechanism 35, and the plurality of main damper parts 32 (32a, 32b) and the sub-damper part 36 are separated. Configured.

  The plurality of main damper portions 32 (32a, 32b) are respectively disposed inside the main cylinder 30 and the main cylinder 30 so as to be slidable in the direction of the axis O2, and the inside of the main cylinder 30 is connected to the first compartment 37. And a main piston 31 partitioned into a second compartment 38. Further, a first piston rod 39 is provided through the main cylinder 30 on one end 30a side in the axis O2 direction so as to be coaxial with the main cylinder 30, and this first piston rod 39 (first piston rod 39) is arranged. Is connected to the main piston 31.

  Furthermore, the first compartment 37 and the second compartment 38 inside the main cylinder 30 are filled with working fluid such as water, oil, various viscous fluids, respectively. The main piston 31 has a relief valve (safety valve, overload prevention mechanism) that allows a working fluid to flow when the differential pressure between the first compartment 37 and the second compartment 38 exceeds a predetermined relief pressure. 40 is provided. Since the relief valve 40 is provided in this way, an excessive reaction force is exerted on each main damper portion 32 (32a, 32b) and sub-damper portion 36 even with an unexpected input (large vibration, external force). Can be prevented.

  Further, when the relief valve 40 is operated, the main piston 31 has a small orifice 41 for moving the working fluid between the compartments 37 and 38 and returning the main piston 31 to its original position. It is provided as a hole. By providing the orifice 41, the main piston 31 can be restored to the original position even with a small restoring force. The orifice 41 is formed so as to allow the working fluid to flow only at a small flow rate. As a result, the vibration reduction characteristics of the main damper portions 32 (32a, 32b) during an earthquake or the like, that is, the vibration suppression characteristics are as follows. It has little effect and can be ignored.

 In this embodiment, the orifice 41 is provided in the main piston 31 of each main damper portion 32 (32a, 32b). However, it is not always necessary to provide the orifice 41 in all the main pistons 31, and a plurality of main pistons 31 are provided. By providing the orifice 41 in at least one main piston 31 of the damper portion 32 (32a, 32b), it is possible to obtain the same operation effect by the orifice 41.

  Each main damper portion 32 (32a, 32b) is provided with an accumulator 42 so as to be connected (communicated) to the orifice 41.

  Each of the plurality of main damper portions 32 (32a, 32b) communicates with a first compartment 37 of the main cylinder 30 and a third compartment 45 of a sub cylinder 33 of a sub damper portion 36, which will be described later. The second compartment 38 of the main cylinder 30 and the fourth compartment 46 of the sub cylinder 33 of the sub-damper portion 36 which will be described later are communicated, and the first compartment 37 and the third compartment 45 of the main cylinder 30 and the sub cylinder 33 are communicated. In the meantime, a first communication pipe 47 and a second communication pipe 48 are connected between the second compartment 38 and the fourth compartment 46 to recirculate the working fluid.

  In the present embodiment, the first connecting pipe 47 and the second connecting pipe 48 are each formed as a branch pipe, and the third compartment 45 of one sub-damper part 36 and a plurality of main damper parts 32 (32a, 32b). Each of the first compartments 37 is communicated with a first connecting pipe 47 of one branch pipe, and each of the fourth compartment 46 of one sub-damper part 36 and each of the plurality of main damper parts 32 (32a, 32b). The second compartment 38 is configured to communicate with the second communication pipe 48 of one branch pipe.

  Of course, each of the first compartments 37 of the plurality of main damper portions 32 (32a, 32b) and the third compartment 45 of one sub-damper portion 36 are communicated with each other by a plurality of straight first communication pipes 47. The second compartments 38 of the plurality of main damper portions 32 (32a, 32b) and the fourth compartment 46 of one sub-damper portion 36 are configured to communicate with each other through a plurality of straight second communication tubes 48. May be. In this case, the main damper disposed in parallel by being connected to one sub-damper 36 by attaching / detaching the first connecting pipe 47 or the second connecting pipe 48 to / from one sub-damper 36. The number of units 32 (32a, 32b) can be set (adjusted) relatively easily.

  Further, each main damper portion 32 (32a, 32b) has an other end 30b of the main cylinder 30 and an end of the first piston rod 39 extending outward from the one end 30a of the main cylinder 30 in the axis O2 direction. Clevis (connection means such as a clevis joint and a ball joint) 49 and 50 are provided.

  In this embodiment, for example, as shown in FIG. 3 (cross-sectional view) and FIG. 4 (plan view), a pair of upper ends are connected to an upper beam (one member of two members) 51 to form a V-shape. The shear link brace 52 is installed in the building surface of the building, and one clevis 49 is connected to a joining jig 53 provided integrally with the lower end portion of the shear link brace 52 so that a plurality of main damper portions 32 (32a 32b) are arranged in the building surface of the building. Further, in the present embodiment, the other clevis 50 of each main damper portion 32 (32a, 32b) is connected to a frame such as one column 54 and the lower beam 55 forming the construction surface via a damper mounting jig 56. To do. In this way, the plurality of main damper portions 32 (32a, 32b) are interposed between the two members (51, 55) of the frame that relatively vibrate due to an earthquake or the like.

  In this embodiment, the plurality of main damper portions 32 (32a, 32b) are attached to the shear link brace 52 in one plane, but the main damper portions installed on adjacent planes in the plane. 32 may be connected, or the main damper portions 32 on the upper and lower floors may be connected.

  On the other hand, as shown in FIGS. 1 and 2, the sub damper portion 36 includes a rotary inertia mass mechanism 35 housed and provided in the sub cylinder 33, and a relative displacement and speed acting on the rotary inertia mass mechanism 35. The fluid pressure cylinder mechanism 60 of an amplification mechanism (speed increasing mechanism) for amplifying acceleration is combined.

  First, the sub cylinder 33 is provided with a partition wall 61 therein, and the partition wall 61 divides the interior into one internal space 62 on the one end 33a side in the axis O3 direction and the other internal space 63 on the other end 33b side. Has been. The sub damper portion 36 is configured by providing a fluid pressure cylinder mechanism 60 in one internal space 62 of the sub cylinder 33 and providing a rotary inertia mass mechanism 35 in the other internal space 63. Therefore, the rotary inertia mechanism 35 is not in contact with the working fluid and is disposed in the air.

  The fluid pressure cylinder mechanism 60 as an amplification mechanism in the present embodiment is disposed in one internal space 62 of the sub-cylinder 33 so as to be slidable in the direction of the axis O3. The one internal space 62 is connected to the third compartment 45. A sub-piston 34 that is partitioned into a fourth compartment 46 is provided. Further, a second piston rod 65 is disposed on the side of the one end 33a in the axis O3 direction of the sub cylinder 33 so as to be coaxial with the sub cylinder 33, and this second piston rod 65 (second piston rod 65). Is connected to the sub-piston 34.

  Further, the third compartment 45 and the fourth compartment 46 of the sub cylinder 33 are filled with working fluid such as water, oil, various viscous fluids, respectively. The sub-piston 34 has a small orifice 66 for moving the working fluid between the respective compartments 45, 46 of the third compartment 45 and the fourth compartment 46 and returning the sub-piston 34 to its original position. It is provided as a control hole.

  The orifice 66 is also formed so as to allow the working fluid to flow only at a small flow rate, so that it hardly affects the vibration reduction characteristics of the sub-damper portion 36 in the event of an earthquake, that is, the vibration damping characteristics. Can be ignored.

  The other end of the first connecting pipe 47 of the branch pipe having one end connected to the first compartment 37 of the main cylinder 30 of the plurality of main damper portions 32 (32a, 32b) is the third compartment 45 of the sub cylinder 33. The other end of the second connecting pipe 48 of the branch pipe connected to the second compartment 38 of the main cylinder 30 is connected to the fourth compartment 46 of the sub cylinder 33. Accordingly, a plurality of main damper portions 32 (32a, 32b) are connected in parallel to one sub-damper portion 36 through the first connecting tube 47 and the second connecting tube 48, and one sub-damper is provided. Between the first compartment 37 and the third compartment 45 of the main cylinder 30 and the sub-cylinder 33 of each of the part 36 and the plurality of main damper parts 32 (32a, 32b), the second compartment 38 and the fourth compartment 46. The working fluid recirculates between the two.

  The first connecting pipe 47 and the second connecting pipe 48 that connect the plurality of main damper portions 32 (32a, 32b) and the sub damper portion 36 are connected to each other because the high pressure acts. It is preferable to provide a quick coupler that has a small pressure loss and can be connected / disconnected with a single touch.

 In the present embodiment, the relief valve 40 is provided on the main piston 31 of each main damper portion 32 (32a, 32b). However, as described above, the first connecting pipe 47 and the second connecting pipe 48 are used. Since the first compartment 37 and the third compartment 45 and the second compartment 38 and the fourth compartment 46 of the main cylinder 30 and the sub-cylinder 33 communicate with each other, each of the main damper portions 32 (32a, 32b) A relief valve is provided not on the main piston 31 but on the sub-piston 34 of the sub-damper 36 so that the pressure in the third compartment 45 and the fourth compartment 46 exceeds a predetermined relief pressure and the relief valve operates. May be. Even in this case, the same effect as the effect of the relief valve 40 provided in the main piston 31 can be obtained.

  Next, the rotary inertia mass mechanism 35 provided so as to be entirely accommodated in the other internal space 63 of the sub-cylinder 33 is connected to the sub-piston 34 at one end and is disposed through the partition wall 61. It is connected to a fluid pressure cylinder mechanism 60 via a piston rod 67 and is configured to be driven by the sub piston 34.

  Specifically, the rotary inertia mass mechanism 35 has one end connected to the other end of the third piston rod 67, a ball screw 70 disposed coaxially with the sub-cylinder 33, and screwed to the ball screw 70. The arranged ball nut 71, the rotating weight 72 attached to the ball nut 71 and rotated by the rotation of the ball nut 71, and the other end of the ball screw 70 are driven by the ball screw 70 and in the direction of the axis O3. A rotation restraint plate 73 that is provided so as to be freely movable back and forth (movable) and restrained so as not to rotate around the axis O3, and a restoring mechanism arranged to bias the rotation restraint plate 73 in the front-rear direction in the direction of the axis O3. The restoring springs 74 and 75 are provided.

  The ball screw 70 is disposed with one end side thereof indirectly connected to the sub-piston 34 via the third piston rod 67. Alternatively, the ball screw 70 may be passed through the partition wall 61 without the third piston rod 67 and may be directly connected to the sub piston 34.

  A ball nut 71 screwed onto the ball screw 70 is supported by a bearing 76. The bearing 76 includes an annular outer ring 76a fixed to the inner surface of the sub-cylinder 33, and an annular inner ring 76b that is rotatably disposed around the axis O3 and supported in the inner hole of the outer ring 76a. Has been. A ball screw 70 is inserted through the center hole of the inner ring 76 b of the bearing 76 and a ball nut 71 is fixed to the inner ring 76 b of the bearing 76. Thereby, the ball nut 71 is disposed so as to be rotatable around the axis O3 and immovable in the direction of the axis O3. Further, a rotating weight 72 is integrally fixed to the ball nut 71. At this time, the rotary weight 72 is formed in, for example, a cylindrical shape, and the ball screw 70 is inserted into the inside, and the ball screw 70 and the sub cylinder 33 and the axis O3 of each other are coaxially arranged, and one end is attached to the ball nut 71. The other end is disposed on the bearing 77 so as to be rotatably supported around the axis O3.

  The rotation restricting plate 73 is for restricting the rotation of the ball screw 70 and is integrally attached to the other end of the ball screw 70. The rotation restricting plate 73 is formed in a substantially disc shape, and is provided with convex portions 73a that protrude radially outward from the outer peripheral edge on both sides in the radial direction across the center. Further, a guide tube 78 is mounted on the inner surface from the bearing 76 to the other end 33b on the other end 33b side of the sub cylinder 33, and radially outward on both sides of the center of the guide tube 78, respectively. A groove extending in the direction of the axis O3 is formed. The rotation restricting plate 73 is disposed by engaging the convex portion 73a with the groove of the guide tube 78, is guided by the groove of the guide tube 78, is movable in the direction of the axis O3, and is restricted by the groove to the axis line. It is provided around O3 so as not to rotate.

  The restoring springs (restoring mechanisms) 74 and 75 are for returning the ball screw 70 and thus the sub-piston 34 to the original position, and further between the rotation restricting plate 73 and the other end 33b of the sub cylinder 33, and further to the rotation restricting plate. 73 and a bearing 76, respectively. At this time, the restoring springs 74 and 75 are disposed so as to urge the rotation restraint plate 73 in the front-rear direction in the direction of the axis O3.

  In this embodiment, as shown in FIGS. 3 and 4, the shear link brace 52 and the vibration reducing device B constitute a shear link type vibration damping structure C of the building.

  Further, at this time, the vibration reducing apparatus B of the present embodiment connects the both ends to the joining jig 53 of the shear link brace 52 and the frame such as the column 54 and the beam 55, respectively, and a plurality of main damper portions 32 (32a, 32b). ) Are installed in the construction plane, that is, a plurality of main damper portions 32 (32a, 32b) are installed between two members that vibrate relatively by an earthquake or the like, and the main damper portions 32 (32a, 32b) The sub-damper portion 36 is installed by connecting the first connecting pipe 47 and the second connecting pipe 48. For this reason, the sub-damper portion 36 does not need to be installed in the construction surface, and its installation position can be arbitrarily set according to the length of the first communication pipe 47 and the second communication pipe 48, In the present embodiment, a flexible first communication pipe 47 or second communication pipe 48 such as a hydraulic hose is applied, and the sub-damper portion 36 is fixedly installed on the floor slab.

  In the vibration reduction device B of the present embodiment having the above-described configuration, two members such as the columns 54 and 57 that are subject to vibration reduction, the beams 51 and 55, the columns 54 and 57, and the beams 51 and 55 due to an earthquake or the like. Relative displacement (interlayer displacement) that approaches and separates between them occurs, and when the relative vibration occurs in these two members, the main pistons 31 of the plurality of main damper portions 32 (32a, 32b) are axial lines within the main cylinder 30. Move forward and backward in the O2 direction. At the same time, the working fluid passes through the first connecting pipe 47 and the second connecting pipe 48, and the first compartment 37 of the main cylinder 30 and the third compartment 45 of the sub cylinder 33 of each main damper portion 32 (32a, 32b). In the meantime, the second compartment 38 and the fourth compartment 46 are refluxed. At this time, since the sub-cylinder 33 has a smaller diameter than the main cylinder 30, the sub-piston 34 has a larger advance / retreat speed than the main piston 31 in accordance with the relative vibration of the two members, and a larger advance / retreat amount in the direction of the axis O3. Will move forward and backward. That is, the advance / retreat of the sub-piston 34 is accelerated and amplified with respect to the main piston 31 that moves forward / backward according to the relative vibration of the two members.

  In the present embodiment, the relief valve 40 is provided on the main piston 31. For this reason, in the unlikely event, the differential pressure between the first compartment 37 and the second compartment 38, and thus the third compartment 45 and the fourth compartment 46 communicating with these compartments 37, 38 through communication pipes 47, 48. When the pressure difference between the two exceeds a predetermined relief pressure set in advance, the relief valve 40 is opened and the pressure difference reaches a peak, thereby preventing an excessive reaction force from being generated.

  On the other hand, when the sub piston 34 increases (amplifies) and advances and retreats, the ball screw 70 advances and retreats in the direction of the axis O3 of the sub cylinder 33 together with the sub piston 34. At this time, since the convex portion 73a of the rotation restricting plate 73 is engaged with the groove of the guide tube 78, the ball screw 70 moves back and forth in the direction of the axis O3 without rotating, and further, the restoring springs 74 and 75 It moves from the original position back and forth in the direction of the axis O <b> 3 against the urging force and is displaced relative to the sub cylinder 33.

  When the ball screw 70 is displaced relative to the sub cylinder 33 in the direction of the axis O3 in this manner, the ball screw 70 is screwed to the ball screw 70, and can be rotated around the axis O3 and cannot move in the direction of the axis O3. The supported ball nut 71 rotates. As a result, the rotary weight 72 integrally connected to the ball nut 71 rotates following the ball nut 71, and the rotational inertial force becomes a reaction force to obtain a vibration reduction effect.

  When the vibration between the two members converges, the sub-piston 34 returns to the original position via the rotation restraint plate 73 and the ball screw 70 by the urging force of the restoring springs 74 and 75, so that no residual displacement occurs. . Furthermore, since the orifices 41 and 66 are provided in the main piston 31 and the sub piston 34, respectively, it is possible to return to the original position by a restoring force based on the elastic rigidity of the two members themselves. In addition, since the orifices 41 and 66 allow the working fluid to flow only at a small flow rate, the characteristics of the vibration reducing device B are hardly affected.

  Furthermore, in the vibration reduction device B of the present embodiment, two (n units) main damper portions 32 (32a, 32b) are connected in parallel to one sub damper portion 36. For this reason, when the relative vibration of the two members occurs, the amount of the working fluid flowing through the sub-damper portion 36 is doubled (n times) compared to the case where one main damper portion 32 is provided, and the linear range in which relief does not occur. As a result, the stress generated in each part of the sub-damper 36 is doubled. Since the internal pressure of the sub-damper portion 36 is doubled, the internal pressure of each main damper portion 32 (32a, 32b) is also doubled (n times), and the reaction force of each main damper portion 32 (32a, 32b) is also 2 Double (n times).

In this manner, by connecting two (n units) main damper parts 32 (32a, 32b) in parallel to one sub damper part 36, as shown in FIG. compared with the case where configured with a damper unit 32, increases the main damper unit 32 (32a, 32 b) displacement _{x 2} sub-damper unit 36 is doubled with respect to the displacement x of the (n times), linear before relief in the range, the reaction force _{F 2} of the sub-damper unit 36, becomes the main damper unit 32 (32a, 32 b) the reaction force F also twice (n times).

That is, the variables when one main damper portion 32 is connected to one sub damper portion 36 are the displacement x of the main damper portion 32, the displacement x ₂ of the sub damper portion 36, and the load F of the main damper portion 32. , when the load _{F 2} sub damper unit 36, the main damper unit 32 (32a, 32 b) of the two for one sub-damper unit 36 (n stand) variables when constituted by connecting in parallel, the main damper unit 32 (32a, 32b) displacement x 'and the displacement _{x 2} sub-damper unit 36', the main damper unit 32 (32a, 32b) load F ', the load _{F 2} sub damper unit 36', the following (2)
In the present embodiment, n in the formula (2) is n = 2. Further, the loads F ₂ ′ and F ′ are capped with relief loads (F _2R ′ and F _R ′).

Here, the inner diameter of the main cylinder 30 is D ₁ and the inner diameter of the sub cylinder 33 is D ₂ . Clear width area _{A 1} of the main cylinder ^{_{30, A 1 = πD 1 2/}} 4, inner size area _{A 2} of the sub-cylinder 33 becomes ^{_{A 2 = πD 2 2/4}} . Further, the speed increasing ratio α (speed ratio of the sub piston 34 to the main piston 31) is an area ratio of these, and α = A ₁ / A ₂ = (D ₁ / D ₂ ) ² .

When the displacement x ₂ sub-damper 36 using the displacement x of the main damper unit 32 is expressed by the following equation (3). On the other hand, the force F ₂ acting on the sub-piston 34 is proportional to the clear width area of the cylinder, can be represented by the formula (4).

  And the variable of each main damper part 32 (32a, 32b) can be represented by the following formula | equation (5) from the relationship of Formula (2). In the present embodiment, n in Expression (5) is n = 2.

In this way, the fluid pressure cylinder mechanism (amplifying mechanism) 60 of the sub-damper portion 36 is displaced nα times the main damper portion 32 (32a, 32b) (x ₂ ′ = nαx ′) and the force 1 / α (F ₂ '= F' / α) acts. Thereby, in this embodiment, compared with the case where the main damper part 32 is one, only a displacement becomes n times (2 times).

  The reaction force F ′ of the main damper portion 32 (32a, 32b) is α times the reaction force of the sub damper portion 36 obtained by multiplying the displacement x ′ of the main damper portion 32 (32a, 32b) by nα.

Therefore, in the vibration reduction device B of the present embodiment, the inertial mass Ψ, the damping coefficient c, and the spring constant k provided in the sub damper part 36 are the same as those provided in the main damper part 32 by nα ² times. The damping performance will be demonstrated.

Furthermore, since the plurality of main damper portions 32 (32a, 32b) are provided, the rack構全body becomes equivalent to the case where there is a ² fold (n [alpha).

  Moreover, in this embodiment, since the relief valve (safety valve) 40 is provided in the main piston 31 of the main damper part 32 (or the sub piston 34 of the sub damper part 36) as an overload prevention mechanism, an unexpected external force is generated. Even if the input is performed, an excessive reaction force is not generated in the main damper portion 32 and the sub damper portion 36.

  Further, an accumulator 42 is provided so as to be connected (communicated) to the orifice 41 to the main piston 31 of the main damper portion 32 (or the sub piston 34 of the sub damper portion 36). Further, since pressure is applied to the working fluid by the accumulator 42, even if the displacement of the main piston 31 and the sub piston 34 is small, that is, from a small earthquake (small vibration), the main piston 31 and the sub piston 34 The linear relationship of the displacements is maintained.

  Furthermore, in the present embodiment, a small orifice 41 is provided in the main piston 31 (or sub-piston 34), and the original force is restored by the restoring force based on the elastic rigidity of the structure connected to both ends of the main damper portion 32 (32a, 32b). Return to position. At this time, since the small orifice 41 circulates the working fluid at a small flow rate, the vibration damping characteristics of the main damper portion 32 (32a, 32b) at the time of an earthquake are hardly affected.

  For the sub-damper portion 36, no restoring force acts from the outside of the damper after the earthquake. In particular, after the relief valve 40 is actuated, even if the main piston 31 returns to the original position, there is a possibility that only the sub-piston 34 remains changed. For this reason, the function of returning the ball screw 70 to the original position is required.

  On the other hand, in this embodiment, a restoring spring 74 is provided as a restoring mechanism between the rotation restraint plate 73 integrated with the ball screw 70 and the other end 33b of the sub cylinder 33. A restoring spring 75 is also provided between the rotation restraint plate 73 and the bearing 76. The restoring springs 74 and 75 need not be limited in their installation positions as long as the ball screw 70, the rotation restraint plate 73, and thus the sub-piston 34 can be returned to their original positions after an earthquake. Further, since the rigidity is parallel to the rotary inertia mass mechanism 35, a very small spring rigidity is provided.

  Therefore, in the vibration reduction device B of the present embodiment having the above-described configuration (and the building damping structure C including the same), first, the main damper portion 32 and the sub damper portion 36 are separated, and the damper portions 32, Since it is configured as a separate type composed of 36, only the main damper portion 32 needs to be installed in the frame surface of the structure, and the sub-damper portion 36 can be installed at an arbitrary position.

  Further, by separating the main damper portion 32 and the sub-damper portion 36, the main damper portion 32 that needs to be installed in the frame surface is the simplest fluid pressure cylinder mechanism (the hydraulic pressure composed of the main cylinder 30 and the main piston 31). Only the mechanism) and the length can be shortened. As a result, it can be installed even within the frame surface of the short span structure, and the vibration damping performance can be improved reliably and effectively regardless of the structure of the frame. That is, it is possible to realize the vibration reducing device B having excellent versatility.

  Further, the main damper portion 32 is connected to the sub damper portion 36 by a first connecting pipe 47 and a second connecting pipe 48. For this reason, even if the total length of the sub-damper portion 36 is longer than the main damper portion 32, it is not necessary to dispose the sub-damper portion 36 in the frame surface. The installation location can be selected as appropriate, for example, along the 55. Thereby, since the main damper part 32 and the sub-damper part 36 are separated and configured, it is possible to reduce the possibility of obstructing the building plan by installing the vibration reducing device B, as compared with the conventional case. However, it is excellent in versatility, and it is possible to effectively improve the damping performance.

  Furthermore, in the vibration reduction device B of this embodiment (and a building damping structure C including the same), a plurality (n) of main damper portions 32 (32a, 32b) with respect to one sub damper portion 36. Therefore, it is possible to configure a displacement enlarging mechanism that enlarges the displacement of one sub-damper part n times.

  Further, if the ratio of the area of the main cylinder 30 of the plurality (n units) of the main damper parts 32 (32a, 32b) and the area of the sub cylinders 33 of the sub damper part 36 is α: 1, it is nα times the damper displacement. The speed increasing mechanism can be configured so that the displacement is applied to the sub-damper portion 36.

Conversely, since the lead of the ball screw 70 is multiplied by 1 / nα, the inertial mass is increased (nα) ² times by the speed increasing mechanism. For example, when α = 3, when two main damper portions 32 (32a, 32b) are installed, the inertial mass is 36 times over the entire construction surface. Therefore, since a large inertial mass can be generated even with a small rotating weight 72, a compact apparatus B can be configured with a large capacity.

  Therefore, according to the vibration reducing apparatus B (and the building damping structure C having the same) of the present embodiment, the mechanical mechanism is compared with the case where the displacement is increased by using a conventional insulator or toggle mechanism. Thus, it is possible to eliminate the friction loss due to the vibration, and to improve the vibration damping performance efficiently and effectively.

  Further, the axial force acting on the ball screw 70 of the sub damper portion 36 is 1 / α of the axial force of the main damper portion 32. For this reason, the reaction force can be processed by the ball screw 70 having a small diameter, and the inexpensive ball screw 70 and the ball nut 71 can be used. Furthermore, the same components as the oil damper can be used for the main damper portion 32 and the sub damper portion 36 (fluid pressure cylinder mechanism 60). From this point, it is also possible to reduce the cost of the entire apparatus.

  Furthermore, since the main piston 31 of the main damper part 32 or the sub piston 34 of the sub damper part 36 is provided with a relief valve (safety valve: relief mechanism) 40, it is possible to prevent an excessive burden force from being generated in the damper. As a result, for example, a friction damper utilizing slipping does not cause a decrease in performance due to wear, and a stable damping performance can be exhibited over a long period of time. That is, it is possible to realize a mechanism and a device excellent in fail-safe performance.

  In addition, since the recovery springs (recovery mechanisms) 74 and 75 and the orifices 41 and 66 for returning the piston to the original position are provided, any part in the damper can be automatically returned to the original position after the earthquake. it can. For this reason, even when multiple earthquakes such as aftershocks following a large earthquake occur, the piston in the damper drifts in a specific direction, or the stroke of the ball screw 70 decreases due to residual deformation. Without being trapped, it is possible to continuously and continuously exhibit the excellent vibration damping performance at the initial stage.

  As mentioned above, although one Embodiment of the vibration reduction apparatus which concerns on this invention was described, this invention is not limited to said one Embodiment, In the range which does not deviate from the meaning, it can change suitably.

For example, in this embodiment, the ball screw 70 of the rotary inertia mass mechanism 35 is installed so as not to rotate with respect to the sub-cylinder 33 and to be movable (displaceable) in the direction of the axis O3, and the ball nut 71 is rotated with respect to the sub-cylinder 33. The sub-damper portion 36 of the vibration reduction device B is configured by installing the rotary weight 72 integrally with the ball nut 71 so that the sub-damper 36 can be moved (displaced) in the direction of the axis O3.
On the other hand, if the rotary weight 72 can be rotated via the ball screw mechanism of the ball screw 70 and the ball nut 71 by the displacement of the sub piston 34 in the direction of the axis O3, the same effect as the present embodiment can be obtained. Can be obtained. For this reason, for example, contrary to the present embodiment, the ball screw 70 can be rotated by being connected to the spring 80 via a rotatable joint, and the ball nut 71 can be fixed to the sub cylinder 33 without using the bearing 77. The rotation weight 72 may be integrally connected to the ball screw 70 and rotated.

  Further, a rotation restraint plate 73 is connected to the ball screw 70, and restoring springs 74 and 75 are interposed between the rotation restraint plate 73 and the sub cylinder 33, and between the rotation restraint plate 73 and the bearing 76, respectively. However, if not particularly required, the restoring springs 74 and 75 may be omitted, and the restoring mechanism does not necessarily need to be constituted by the restoring springs 74 and 75. Further, as shown in FIG. 6, a restoring spring 81 is provided between one end 33a of the sub cylinder 33 and the tip of the second piston rod 65 projecting outward from the one end 33a of the sub cylinder 33 in the axis O3 direction. Of course, even in this case, it is possible to obtain the same effect as the present embodiment.

  Moreover, in this embodiment, although the relief valve 40 as a fail safe mechanism was provided in the main piston 31, you may abbreviate | omit when unnecessary. Further, it may be provided not on the main piston 31 but on the sub-piston 34. Further, a fail-safe function may be provided by adding a torque limiting mechanism to the ball screw mechanism instead of the relief valve 40. Although both ends of the main damper portion 32 are illustrated with clevises 49 and 50, they may be ball joints.

  Further, the fluid pressure cylinder mechanism 60 and the rotary inertia mass mechanism 35 do not have to be arranged in a cylinder (sub cylinder 33) having the same diameter. That is, the diameter of the rotary inertia mass mechanism 35 may be increased or decreased with respect to the fluid pressure cylinder mechanism 60 as necessary.

Further, the fluid pressure cylinder mechanism 60 and the rotary inertia mass mechanism 35 may not be disposed on the same axis.
For example, as shown in FIG. 7, a rack 81 is provided at the tip of the sub-piston rod (third piston rod 67) of the fluid pressure cylinder mechanism 60, and a screw gear or the like is provided at the tip of the ball screw 70 of the rotary inertia mass mechanism 35. A gear 82 is provided, the rack 81 and the gear 82 are meshed, and the fluid pressure cylinder mechanism 60 and the rotation inertia mass mechanism 35 are connected so that their axes intersect each other, and the rotation inertia mass with respect to the fluid pressure cylinder mechanism 60. The mechanism 35 may be configured to move synchronously. Even in this case, it is possible to obtain the same effect as that of the present embodiment.

8 and 9, a rack 81 is provided at the tip of the sub-piston rod 67 of the fluid pressure cylinder mechanism 60, and a gear 82 such as a screw gear is provided at the tip of the ball screw 70 of the rotary inertia mass mechanism 35. In addition, gears 83 and 84 such as circular gears (pinions) are provided between the rack 81 and the gear 82, and the gears 83 and 84 are engaged with the rack 81 and the gear 82, so that the fluid pressure cylinder mechanism 60 and the rotary inertia mass are engaged. You may make it connect the mechanism 35 so that a mutual axis line may cross | intersect.
In this case, by providing the small-diameter gear 84 between the rack 81 and the gear 82, the displacement of the fluid pressure cylinder mechanism 60 can be amplified and transmitted to the rotary inertia mass mechanism 35, which is more effective. In addition, it is possible to realize the vibration damping device B that can reduce vibration energy. 8, when the number of small-diameter gears 84 is increased as shown in FIG. 9, the displacement of the fluid pressure cylinder mechanism 60 can be further amplified and transmitted to the rotary inertia mass mechanism 35.

  Further, as shown in FIG. 10, a rack 81 is provided at the tip of the sub piston rod (third piston rod 67) of the fluid pressure cylinder mechanism 60, and a rack 85 is provided at the tip of the ball screw 70 of the rotary inertia mass mechanism 35. Further, a gear 86 such as a circular gear (pinion) is provided between the racks 81 and 85, the racks 81 and 85 and the gear 86 are meshed, and the fluid pressure cylinder mechanism 60 and the rotary inertia mass mechanism 35 are connected. Also good. In this case, the fluid pressure cylinder mechanism 60 and the rotary inertia mass mechanism 35 can be connected by arranging the axial directions thereof in the same direction. Even in the case of such a configuration, it is possible to obtain the same effects as those of the present embodiment.

  Further, for example, a ball screw 70 is connected to the gears 83, 84, and 86 of FIGS. You may make it comprise an apparatus.

DESCRIPTION OF SYMBOLS 1 Fluid pressure cylinder mechanism 2 Piston 3 Cylinder inner space 4 Cylinder inner space 5 Connecting pipe 6 Rotating inertia mass mechanism 7 Main cylinder 7a One end 7b Other end 8 Rotating inertia mass mechanism 9 Fluid pressure cylinder mechanism (hydraulic mechanism)
DESCRIPTION OF SYMBOLS 10 Sub cylinder 11 Inner side of one end of main cylinder 12 Inner side of other end of main cylinder 13 Inner side of sub cylinder 14 Ball screw 15 Sub piston 16 One internal space 17 Other internal space 18 Main piston 19 Internal space 20 Connecting pipe 21 bearing 21a outer ring 21b inner ring 22 ball nut 23 rotation restraint plate 24 restoring spring 25 restoring spring 30 main cylinder 30a one end 30b other end 31 main piston 32 main damper part 32a main damper part 32b main damper part 33 sub cylinder 34 sub piston 35 rotation Inertial mass mechanism 36 Sub-damper portion 37 First compartment 38 Second compartment 39 First piston rod 40 Relief valve 41 Orifice 42 Accumulator 45 Third compartment 46 Fourth compartment 47 First connecting pipe 48 Second connecting pipe 49 Clevis 5 0 Clevis 51 Upper beam 52 Shear link brace 53 Joining jig 54 Column 55 Lower beam 56 Damper mounting jig 57 Column 60 Fluid pressure cylinder mechanism 61 Partition wall 62 One internal space 63 Other internal space 65 Second piston rod 66 Orifice 67 Third piston rod 70 Ball screw 71 Ball nut 72 Rotating weight 73 Rotation restraint plate 73a Convex portion 74 Restoring spring 75 Restoring spring 76 Bearing 76a Outer ring 76b Inner ring 77 Bearing 78 Guide tube 80 Spring 81 Rack 82 Gear 83 Gear 84 Gear 85 Rack 86 Gear A Conventional vibration reduction device B Vibration reduction device C Building damping structure O1 Axis O2 Axis O3 of main damper part Axis of sub-damper part

Claims (3)

A vibration reducing device for reducing relative vibration between two members that vibrate relatively,
A plurality of main damper portions disposed between the two members to reduce relative vibration, and a sub-damper portion disposed separately from the plurality of main damper portions;
Each of the plurality of main damper portions includes a main cylinder, a main piston that divides the inside of the main cylinder into a first compartment and a second compartment, and is connected to the main piston so as to be outside in the axial direction of the main cylinder. It is configured with a piston rod that is extended,
The sub-damper portion includes a sub-cylinder, a fluid pressure cylinder mechanism as an amplification mechanism disposed in the internal space of the sub-cylinder, and a rotary inertia mass mechanism.
The fluid pressure cylinder mechanism is disposed in the internal space so as to be slidable in the axial direction of the sub-cylinder, and divides the internal space into a third compartment and a fourth compartment, and the sub-piston A sub-piston rod extending in a connected manner,
The rotary inertia mass mechanism includes a ball screw connected to the sub-piston rod, a ball nut screwed to the ball screw, and a rotation provided to be rotatable about an axis following the ball nut. A weight,
Each of the plurality of main damper portions communicates the first compartment and the third compartment of the sub-damper portion with a first connecting pipe, and the second compartment and the fourth compartment of the sub-damper portion. The chamber is communicated with the second connecting pipe, and is connected in parallel to the sub-damper portion;
The first compartment and the second compartment, the third compartment and the fourth compartment, the first connecting pipe, and the second connecting pipe are filled with a working fluid. A vibration reducing device characterized by that. The vibration reducing device according to claim 1,
At least one of the main piston of each main damper portion and the sub-piston of the sub damper portion is provided with the first compartment and the second compartment, and / or the third compartment and the fourth compartment. A vibration reducing device characterized in that an orifice for communication is provided. In the vibration reduction device according to claim 1 or 2,
At least one of the main piston of each main damper part and the sub-piston of the sub-damper part has a differential pressure between the first compartment and the second compartment, and / or the third compartment and the When the differential pressure between the fourth compartments exceeds a preset relief pressure, the working fluid is allowed to flow between the first compartment and the second compartment and / or the third compartment and the A vibration reducing apparatus, comprising a relief valve that circulates between the fourth compartments.

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