JP2012189104A - Inertial mass damper - Google Patents

Inertial mass damper Download PDF

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JP2012189104A
JP2012189104A JP2011051596A JP2011051596A JP2012189104A JP 2012189104 A JP2012189104 A JP 2012189104A JP 2011051596 A JP2011051596 A JP 2011051596A JP 2011051596 A JP2011051596 A JP 2011051596A JP 2012189104 A JP2012189104 A JP 2012189104A
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spring
cylinder
axial
rod
damper
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JP2011051596A
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JP5831734B2 (en
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Kazuhiko Isoda
和彦 磯田
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Shimizu Corp
清水建設株式会社
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Abstract

PROBLEM TO BE SOLVED: To provide an effective and appropriate inertial mass damper that can secure excellent performance for itself by integrally incorporating an additional spring.SOLUTION: A damper body 20 and a spring member 30 as an additional spring are serially connected to be integrally incorporated in an exterior cylinder 11. The damper body includes: a ball screw shaft 21 which is supported to be displaced and not to be rotated in an axial direction in the exterior cylinder; a ball nut 22 which is screwed to the ball screw shaft and held to be rotated and not to be displaced in the axial direction in the exterior cylinder; and a rotary weight 23 rotated by the rotation of the ball nut. The spring member 30 as the additional spring includes a set of disk spring groups where a plurality of disk springs 40 are stacked, and the entire disk spring groups are incorporated into the exterior cylinder to be elastically contracted/expanded in the relatively displaceable state in the axial direction of the exterior cylinder to deal with both compression and tension.

Description

  The present invention relates to an inertial mass damper that is suitable for application as a component in seismic isolation systems and vibration control systems for structures such as buildings.
The thing which applied the inertial mass damper to this kind of seismic isolation system and damping system is proposed (for example, refer to patent documents 1-3).
Inertial mass dampers can obtain an extremely large inertial mass with a small mass of rotating mass, and have a characteristic that a reaction force proportional to the relative acceleration acting on the damper can be obtained. By connecting an additional spring in series to the inertial mass damper, it is possible to reduce the response in the high frequency range, or to construct a system that can greatly improve the resonance characteristics like TMD. Expected.
  In such a system, a specific structure for connecting the additional spring in series with the inertial mass damper is a structure member (bending column, brace, plate, etc.) arranged in series with the inertial mass damper. Bending rigidity or shaft rigidity is used as an additional spring, or a special spring member such as a coil spring or a disc spring is connected in series to the inertia mass damper. In the former case, while having an appropriate spring rigidity Since it is not easy to set a structural member that can secure desired proof stress and stroke, the latter method is practical in practice.
  In such a case, various spring members can be used as the additional spring, but it is considered that a compact and large load bearing performance can be suitably used. Especially, a plurality of disk springs are combined in series or in parallel. If the disc spring group is used, the deformation performance and load resistance can be increased. Therefore, there is an advantage that a predetermined performance can be obtained at a lower cost and more compact than the case of using the most general coil spring.
However, since the disc spring alone can handle only the compressive force, in order to function as an additional spring that can handle not only the compressive force but also the tensile force, it corresponds to the disc spring group and the tensile force to cope with the compressive force. FIG. 6 shows an example thereof. A piston 2 that can be displaced in both directions is arranged in the cylinder 1, and a disc spring 3 as shown in FIG. As shown in (b), a configuration is adopted in which a large number (8 in the illustrated example) of each of the pistons 2 are housed as two sets of disc spring groups 3A stacked in series.
In such a spring member, the disc spring group on one side (the right side of the piston 2 in the illustrated example) against the compressive force generated between the rod 4 connected to the piston 2 and the clevis 5 provided at one end of the cylinder 1. The entire 3A is pressed by the piston 2 in one direction (rightward in the illustrated example) to be elastically compressed, and the other (the same, the left side) disk spring group 3A is moved to the piston 2 with respect to the tensile force. Therefore, it is possible to cope with this by pressing in the opposite direction (same as the left side) and elastically compressing.
JP 2008-101769 A JP 2009-180346 A JP 2009-293691 A
  In any case, in order to structurally connect a spring member as an additional spring to the inertial mass damper in series, as shown schematically in FIG. 7, the inertial mass damper 6 and one end of the spring member 7 are connected to each other. It is usual to connect via the clevis 8 and to connect the other end of the object firmly to a predetermined position of the target structure via the clevis 9.
  However, when the inertial mass damper 6 and the spring member 7 are connected to each other and installed in the target structure with the structure shown in FIG. As shown in (b), it is assumed that it will be bent by its own weight, or it will be deformed so that it will buckle during compression, making it impossible to maintain linearity. Further, there is a concern that the stroke cannot be maintained, the desired performance cannot be exhibited, and the reliability of the system is impaired.
  Although it is preferable to use the disc spring 3 as an additional spring as described above, the overall length of the spring member 7 having two disc spring groups 3A as shown in FIG. 6 is considerably increased. For this reason, there is a demand for a small spring member that can be suitably applied to this type of system.
  In view of the above circumstances, an object of the present invention is to provide an effective and appropriate inertial mass damper that can ensure excellent performance by incorporating an additional spring integrally.
  The invention according to claim 1 is an inertial mass damper that is interposed between two members that vibrate relative to each other in a direction to be separated from each other and controls relative vibration between the two members, and is connected to one of the two members The damper body and the additional spring are connected in series and integrated into the exterior cylinder, and the additional spring is connected to the other of the two members. The damper body is disposed in the exterior cylinder. A ball screw shaft supported in an axially displaceable and non-rotatable manner, a ball nut screwed to the ball screw shaft and held in the outer cylinder and held in an axially displaceable manner, and the rotation of the ball nut And the additional spring is connected to the ball screw shaft in a state in which the additional spring can expand and contract in the axial direction of the outer cylinder. And wherein the Rukoto.
  The invention according to claim 2 is the inertia mass damper according to claim 1, wherein the additional spring includes a disc spring group in which a plurality of disc springs are stacked in the axial direction of the outer cylinder, and the disc spring The entire group is composed of a spring member that is incorporated so as to be elastically expandable and contractible in a state in which it can be relatively displaced in the axial direction of the exterior cylinder.
  The invention according to claim 3 is the inertial mass damper according to claim 2, wherein the spring member as the additional spring includes an end cylinder element connected to the other of the two members, and the end cylinder A rod element whose tip is inserted so as to be relatively displaceable in the axial direction with respect to the element, and a spring element assembled to the tip of the rod element and housed in the end cylinder element, A ball screw shaft of the damper main body is connected to a base end portion of the rod element, and the spring element includes a set of the disc spring group in which a plurality of disc springs are stacked in series and / or in parallel. The rod elements are composed of a pair of push plates respectively disposed at both ends of the disc spring group, and the tip end portions of the rod elements are inserted into the entire spring elements so as to be relatively displaceable in the axial direction. Essential Are provided with stoppers at positions outside the respective pressing plates, and the whole spring element is assembled between the stoppers in a state in which it can be elastically displaced on both axial sides of the rod element, Each push plate is disposed inside a lid provided at each end of the end cylinder element, and each push plate is moved to the inner surface of each lid by axial relative displacement of the rod element with respect to the end cylinder element. The whole spring element is housed and held in the end cylinder element in a state in which the spring element can be displaced inward in the axial direction of the rod element.
According to the present invention, the damper body that functions as an inertia mass damper itself and the additional spring are accommodated in the exterior cylinder and connected in series inside the cylinder, so that both ends of the inertia mass damper are connected to the target structure. Therefore, it is sufficient to be pin-bonded to each other, so that it can be stably held only at both ends, and there is no deformation that is bent by its own weight or buckled during compression.
Compared to the conventional case where the inertial mass damper and the additional spring are connected, the overall required length can be shortened to achieve compactness, and the installation work for the target structure becomes easy and the production cost is reduced. It is also possible to reduce it.
  In particular, if a spring member made of a disc spring is used as the additional spring, a sufficiently small size and a low price can be realized. In that case, if a configuration corresponding to both compression and tension is achieved by a set of disc spring groups, the entire structure can be realized. The required length can be reduced sufficiently.
It is a figure which shows schematic structure of the inertial mass damper which is embodiment of this invention. It is explanatory drawing of the structural example of the spring member as an additional spring, and its behavior. It is a figure which shows the structural example of the disk spring group in a spring member. It is explanatory drawing of the behavior of the whole inertia mass damper same as the above. It is a figure which shows the modification of an inertial mass damper. It is a figure which shows an example of the additional spring by the conventional disc spring. It is a figure which shows the example of a connection of the conventional inertia mass damper and an additional spring.
An embodiment of the inertial mass damper 10 of the present invention will be described with reference to FIGS.
The inertia mass damper 10 of the present embodiment is integrally incorporated in the outer cylinder 11 with a damper body 20 that functions in the same manner as a conventional general inertia mass damper and a spring member 30 as an additional spring connected thereto. Focus on this.
  The exterior cylinder 11 is a hollow cylinder having a predetermined length of high-axis rigidity and high bending rigidity, and one end (the left end in the figure) is connected to a predetermined position of the target structure via a clevis 12. .
A damper main body 20 composed of a ball screw shaft 21, a ball nut 22, and a rotating weight 23 is incorporated in one end side (the left end side in the figure) in the exterior cylinder 11.
The ball screw shaft 21 has a disk-shaped anti-rotation plate 24 fixed substantially at the center, and the anti-rotation plate 24 is supported by the key 25 with respect to the outer cylinder 11 so as to be displaceable in the axial direction and non-rotatable. Therefore, the ball screw shaft 21 itself is supported in the outer cylinder 11 so as to be axially displaceable and non-rotatable.
The ball nut 22 is screwed onto the ball screw shaft 21 and is held by the bearing 26 in the outer cylinder 11 so as to be rotatable and non-displaceable in the axial direction. A cylindrical rotating weight 23 is held against the ball nut 22. It is assembled together.
Therefore, the damper main body 20 has a ball nut 22 when the ball screw shaft 21 is displaced in the axial direction with respect to the outer cylinder 11 (that is, with respect to the ball nut 22) via the spring member 30 as will be described later. In addition, the rotating weight 23 is rotated to obtain a large inertial mass, and the vibration damping effect and the seismic isolation effect which are excellent as in the conventional system are exhibited by using the rotating weight 23.
Of course, the damper main body 20 can freely set the inertial mass by adjusting the mass, size, shape, etc. of the lead of the ball screw and the rotary weight 23 as in the conventional general inertial mass damper. .
If the rotary weight 23 is attached to the ball nut 22 via an appropriate friction material (not shown) so as to be relatively rotatable, the rotary weight 23 is slipped with respect to the ball nut 21 when overloaded. The inertia mass damper 10 can be provided with an overload prevention function.
  The above-mentioned spring member 30 is incorporated in the other end side (right end side) in the exterior cylinder 11 so as to be capable of relative displacement in the axial direction, and the above-described ball screw shaft 21 is connected to this spring member 30, thereby A damper main body 20 that functions as an inertial mass damper and a spring member 30 that functions as an additional spring are structurally connected in series.
The configuration and behavior of the spring member 30 in this embodiment are shown in FIG.
The spring member 30 of the present embodiment includes an end cylinder element 31 (hereinafter simply referred to as an end cylinder 31) and a rod element 32 (hereinafter referred to as an axial displacement relative to the end cylinder 31). , Simply abbreviated as a rod 32), and a spring element 33 that is assembled to the tip of the rod 32 and accommodated in the end cylinder 31.
  The end cylinder 31 is inserted into the interior of the exterior cylinder 11 from the other end side, and can be displaced in the axial direction with respect to the exterior cylinder 11 via the key 34 (see FIG. 1) (that is, the end cylinder 31 protrudes and retracts from the exterior cylinder 11). The base end is connected to a predetermined position of the target structure via the clevis 35.
  The rod 32 is connected to the ball screw shaft 21 at the base end (the left end in the drawing), and accommodates and holds the spring element 33 assembled at the tip end (the right end portion in the drawing) in the end cylinder 31. Thus, the vibration of the target structure (vibration along the axial direction of the exterior cylinder 11) is transmitted to the ball screw shaft 21 via the end cylinder 31 and the spring element 33 to operate the damper main body 20.
The spring element 33 is mainly composed of a set of disc spring groups 40A in which a plurality of (eight in the illustrated example) disc springs 40 are stacked in series, and can itself handle both compression and tension. It is.
That is, in the spring element 33 in the present embodiment, the pressing plates 41 (41a, 41b) are respectively disposed on both ends of the disc spring group 40A, and the rod 32 is axially disposed with respect to the entire spring element 33. The rod 32 is inserted so as to be capable of relative displacement, and a force bolt as a stopper 42 (42a, 42b) is screwed to the rod 32 at a position outside each push plate 41, and between the stoppers 42, The entire spring element 33 is assembled in a state in which it can be elastically expanded and contracted on both sides in the axial direction of the rod 32 and the entire element can be elastically displaced.
In the state where the whole spring element 33 is accommodated in the end cylinder 31, as shown in FIG. 2A, the pressing plates 41 (41a on both sides) are pressed by the elastic biasing force of the whole disc spring group 40A. , 41b) is pressed against the inner surface of each annular lid 43 (43a, 43b) fixed to both ends of the end cylinder 31, and in this state, the spring element 33 is endless. Is stably held in the cylinder 31.
A cushioning material 44 such as hard rubber is attached to the outer surface of the push plate 41, so that noise is prevented from being generated when the push plate 41, the stopper 42 and the lid 43 come into contact with each other. ing.
Based on the above configuration, the spring member 30 is vibrated in the target structure from the state in which the spring member 30 is statically positioned at the end in the outer cylinder 11 in the state shown in FIG. ), When a compressive force is applied so that the end cylinder 31 is pushed into the outer cylinder 11, the rod 32 is relatively displaced in the direction pushed into the end cylinder 31, thereby The stopper plate 42b is pushed into the end cylinder 31 by the stopper 42b, and the whole disc spring group 40A is displaced rightward in the figure, and the pressing plate 41a is pressed against the lid 43a, whereby the spring element 33 is pressed. The whole is compressed elastically.
On the contrary, when a tensile force is applied so that the end cylinder 31 is pulled out from the outer cylinder 11 as shown in (c), the rod 32 is relatively displaced in the direction of pulling out from the end cylinder 31, thereby The pressing plate 41a is drawn into the end cylinder 31 by the other stopper 42a and the whole disc spring group 40A is displaced in the left direction in the figure, and the pressing plate 41b is pressed against the lid body 43b, whereby the spring element The entire 33 is elastically compressed.
  As described above, according to the spring member 30 of the present embodiment, the pair of disc spring groups 3A are compressed both in compression and in tension, so that both the compression force and the tensile force can be handled. Unlike the conventional spring member shown in FIG. 6, two sets of disc spring groups are not required, and therefore the number of disc springs 40 required can be halved even if the disc spring has the same rigidity as the conventional spring member. The required length as a whole can also be halved, and as a result, the configuration can be sufficiently simplified, reduced in size, and reduced in cost.
Of course, by adjusting the spring rigidity of the disc spring 40 as a single unit, the number of those, and the lamination pattern, it is possible to cope with a wide range of arbitrary deformation performance and proof stress. For example, various patterns such as shown in FIG. 3 may be designed so that the spring rigidity can be obtained.
In this case, if the disc springs 40 are arranged in parallel, the proof stress (load) can be increased. If the disc springs 40 are arranged in series, the deformation performance can be increased. The number of sheets necessary for a predetermined load may be arranged in parallel, and the number of sheets necessary for the predetermined deformation may be arranged in series.
  The inertial mass damper 10 of the present embodiment has a configuration in which the spring member 30 having the above-described configuration is incorporated into the exterior cylinder 11 as an additional spring, and the spring member 30 is connected to the damper main body 20 in the exterior cylinder 11. As shown in FIG. 4A, when receiving a compressive force, the damper member 20 is operated while the spring member 30 is displaced so as to be pushed into the outer cylinder 11 to move the ball nut 22 and the rotary weight 23 in one direction. 4B, when receiving the tensile force as shown in FIG. 4B, the damper main body 20 is operated while the spring member 30 is displaced so as to be pulled out of the outer cylinder 11, and the ball nut 22 and the rotary weight 23 are moved. In any case, the damper body 20 can be effectively operated to obtain desired characteristics.
And the inertia mass damper 10 of this embodiment should just pin-join the both ends of itself with the object structure via the clevis 12 and 35, and the inertia mass damper 6 and the conventional example shown in FIG. Since the spring member 7 is not connected with a three-pin structure, it can be stably held only at both ends, and it does not cause deformation such as bending due to its own weight or buckling during compression. No bending or torque is generated only by the axial load acting on the outer cylinder 11, and no torque load is generated on the main body structure to which the outer cylinder 11 is connected.
Of course, as compared with the case where the individual inertia mass dampers 6 and the spring members 7 are connected as in the conventional case, the overall required length can be shortened and the compactness can be realized, and the installation work for the target structure becomes easy. In combination with the use of the inexpensive disc spring 40, the manufacturing cost can be sufficiently reduced.
  The embodiment of the present invention has been described above. However, the above embodiment is a preferred example, and the present invention is not limited to the above embodiment. For example, within the scope of the present invention, Appropriate design variations and applications as listed are possible.
In the above-described embodiment, the whole spring element 33 including the disc spring group 40A is accommodated in the end cylinder 31, and the end cylinder 31 is built into the exterior cylinder 11 so as to be able to protrude and retract. What is necessary is just to comprise so that it may act on both compression and tension | tensile_strength by hold | maintaining the whole group 40A so that it can displace to the axial direction both sides, For this purpose, as shown in FIG. 43b is connected to each other with a bolt 50 (indicated by a chain line), the bolt 50 is fixed to the through hole provided in the lid 43b with a nut 51, and the bolt 50 is fixed to the lid 43a with a tap screw. Even if the bolt 50 is changed so as to function as an element that replaces the end cylinder (end cylinder element) 31 described above, it functions in the same manner.
In the modification shown in FIG. 5, in addition to the above changes, the rotation prevention plate 24 and the stopper 42b in the above embodiment are integrated, and the tip surface of the end cylinder 11 and the lid 43a are integrated. .
  As in the above-described embodiment, it is optimal to use the spring member 30 having a configuration corresponding to both compression and tension by a pair of disc spring groups 40A as in the above embodiment, but is not limited thereto. It is also possible to use a spring member composed of two sets of disc spring groups 3A for compression and tension shown in FIG. However, in that case, since the required dimension as an additional spring becomes long, it must be accommodated in the exterior cylinder 11.
  Furthermore, it is not limited to using the disc spring 40 as an additional spring, and includes a coil spring and a leaf spring as long as they can be accommodated in the outer cylinder 11 and exhibit equivalent spring rigidity in both compression and tension. Adopting an arbitrary spring element does not prevent it.
  Furthermore, the inertial mass damper of the present invention may incorporate an appropriate damping element such as an oil damper in the outer cylinder in addition to the additional spring being integrally incorporated in the outer cylinder. The clevises 12 and 35 may be ball joints.
10 Inertial Mass Damper 11 Exterior Cylinder 12 Clevis 20 Damper Body 21 Ball Screw Shaft 22 Ball Nut 23 Rotating Weight 24 Anti-Rotation Plate 25 Key 26 Bearing 30 Spring Member (Additional Spring)
31 End cylinder (end cylinder element)
32 Rod (Rod element)
33 Spring element 34 Key 35 Clevis 40 Belleville spring 40A Belleville spring group 41 (41a, 41b) Press plate 42 (42a, 42b) Stopper 43 (43a, 43b) Lid 44 Buffer material 50 Bolt (end cylinder element)
51 nuts

Claims (3)

  1. An inertia mass damper that is interposed between two members that vibrate relative to each other in a direction to be separated from each other and controls the relative vibration between the two members;
    In the exterior cylinder connected to one of the two members, the damper main body and the additional spring are connected in series and integrated together, and the additional spring is connected to the other of the two members,
    The damper main body is supported by a ball screw shaft that is axially displaceable and non-rotatable in the outer cylinder, and is held by the ball screw shaft so as to be rotatable and non-displaceable in the axial direction in the outer cylinder. A ball nut and a rotating weight rotated by rotation of the ball nut,
    The inertia mass damper, wherein the additional spring is connected to the ball screw shaft in a state in which the additional spring can expand and contract in the axial direction of the exterior cylinder.
  2. The inertial mass damper according to claim 1,
    The additional spring includes a disc spring group in which a plurality of disc springs are stacked in the axial direction of the exterior cylinder, and the entire disc spring group is elastically movable relative to the axial direction of the exterior cylinder. An inertial mass damper comprising a spring member incorporated so as to be extendable and contractible.
  3. An inertial mass damper according to claim 2,
    The spring member as the additional spring includes an end cylinder element connected to the other of the two members, and a rod element having a distal end inserted into the end cylinder element so as to be relatively displaceable in the axial direction. The rod element is constituted by a spring element assembled in the distal end portion of the rod element and accommodated in the end cylinder element, and the ball screw shaft of the damper body is connected to the proximal end portion of the rod element,
    The spring element is composed of a pair of disc spring groups in which a plurality of disc springs are stacked in series and / or in parallel, and a pair of pressing plates respectively disposed on both ends of the disc spring groups,
    The tip of the rod element is inserted so as to be relatively displaceable in the axial direction with respect to the entire spring element, and the rod element is provided with a stopper at a position outside each push plate. , The whole spring element is assembled between the stoppers in an elastically displaceable state on both axial sides of the rod element,
    Each push plate is disposed inside a lid provided at each end of the end cylinder element, and each push plate is moved by an axial relative displacement of the rod element with respect to the end cylinder element. An inertia mass damper, wherein the whole spring element is housed and held in the end cylinder element while being pressed against the inner surface and displaceable inward in the axial direction of the rod element.
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Cited By (13)

* Cited by examiner, † Cited by third party
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CN103625233A (en) * 2013-11-12 2014-03-12 江苏大学 Integrated Inerter suspension for vehicle
JP2014163447A (en) * 2013-02-25 2014-09-08 Shimizu Corp Vibration reduction device
JP2014234873A (en) * 2013-06-03 2014-12-15 清水建設株式会社 Vibration reduction device
JP2015083865A (en) * 2013-09-20 2015-04-30 株式会社免制震ディバイス Rotational inertia mass damper
JP2017015133A (en) * 2015-06-29 2017-01-19 日本精工株式会社 Rotational inertia mass damper
JP2017044328A (en) * 2015-08-28 2017-03-02 株式会社免制震ディバイス Mass damper
CN108458036A (en) * 2018-04-23 2018-08-28 东北大学 A kind of damper
CN108590300A (en) * 2018-03-30 2018-09-28 东南大学 Self-resetting metal energy consumption drag-line
JP2019032261A (en) * 2017-08-09 2019-02-28 カヤバ システム マシナリー株式会社 Vibration testing machine
CN110453800A (en) * 2019-07-22 2019-11-15 江苏科技大学 A kind of metal damper of Self-resetting bending energy-wasting
CN110836034A (en) * 2019-11-29 2020-02-25 华中科技大学 Assembled light metal damper capable of dissipating energy and reducing vibration in multiple stages
CN111486189A (en) * 2020-04-16 2020-08-04 北京空间飞行器总体设计部 Reusable small celestial body surface attachment buffer mechanism
WO2021019633A1 (en) * 2019-07-29 2021-02-04 株式会社ティ・カトウ Vibration control device and building material comprising same

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* Cited by examiner, † Cited by third party
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58102853U (en) * 1982-01-05 1983-07-13
JPS6084846U (en) * 1983-11-17 1985-06-11
JPH07259909A (en) * 1994-03-18 1995-10-13 Hitachi Ltd Mechanical vibration control apparatus
JP2004044748A (en) * 2002-07-15 2004-02-12 Mitsubishi Heavy Ind Ltd Vertical base-isolating device
JP2010255752A (en) * 2009-04-24 2010-11-11 Nsk Ltd Rotating inertia mass damper

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58102853U (en) * 1982-01-05 1983-07-13
JPS6084846U (en) * 1983-11-17 1985-06-11
JPH07259909A (en) * 1994-03-18 1995-10-13 Hitachi Ltd Mechanical vibration control apparatus
JP2004044748A (en) * 2002-07-15 2004-02-12 Mitsubishi Heavy Ind Ltd Vertical base-isolating device
JP2010255752A (en) * 2009-04-24 2010-11-11 Nsk Ltd Rotating inertia mass damper

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014163447A (en) * 2013-02-25 2014-09-08 Shimizu Corp Vibration reduction device
JP2014234873A (en) * 2013-06-03 2014-12-15 清水建設株式会社 Vibration reduction device
JP2015083865A (en) * 2013-09-20 2015-04-30 株式会社免制震ディバイス Rotational inertia mass damper
CN103625233A (en) * 2013-11-12 2014-03-12 江苏大学 Integrated Inerter suspension for vehicle
JP2017015133A (en) * 2015-06-29 2017-01-19 日本精工株式会社 Rotational inertia mass damper
JP2017044328A (en) * 2015-08-28 2017-03-02 株式会社免制震ディバイス Mass damper
JP2019032261A (en) * 2017-08-09 2019-02-28 カヤバ システム マシナリー株式会社 Vibration testing machine
CN108590300A (en) * 2018-03-30 2018-09-28 东南大学 Self-resetting metal energy consumption drag-line
WO2019184261A1 (en) * 2018-03-30 2019-10-03 东南大学 Self-resetting metal energy-dissipation cable
CN108590300B (en) * 2018-03-30 2019-11-12 东南大学 Self-resetting metal energy consumption drag-line
US10954685B1 (en) 2018-03-30 2021-03-23 Southeast University Self-centering cable with metal-based energy-dissipation
CN108458036A (en) * 2018-04-23 2018-08-28 东北大学 A kind of damper
CN110453800A (en) * 2019-07-22 2019-11-15 江苏科技大学 A kind of metal damper of Self-resetting bending energy-wasting
WO2021019633A1 (en) * 2019-07-29 2021-02-04 株式会社ティ・カトウ Vibration control device and building material comprising same
CN110836034A (en) * 2019-11-29 2020-02-25 华中科技大学 Assembled light metal damper capable of dissipating energy and reducing vibration in multiple stages
CN111486189A (en) * 2020-04-16 2020-08-04 北京空间飞行器总体设计部 Reusable small celestial body surface attachment buffer mechanism

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