JP2011012720A - Suspending vibration control structure - Google Patents

Suspending vibration control structure Download PDF

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JP2011012720A
JP2011012720A JP2009155725A JP2009155725A JP2011012720A JP 2011012720 A JP2011012720 A JP 2011012720A JP 2009155725 A JP2009155725 A JP 2009155725A JP 2009155725 A JP2009155725 A JP 2009155725A JP 2011012720 A JP2011012720 A JP 2011012720A
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rocking
suspension
mass
center
damping
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JP5207077B2 (en
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Kazuhiko Isoda
和彦 磯田
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Shimizu Construction Co Ltd
Shimizu Corp
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Shimizu Construction Co Ltd
Shimizu Corp
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Abstract

PROBLEM TO BE SOLVED: To speedily damp a vibration of a suspending structure suspended and supported by a suspending material without bending rigidity such as a wire and swinging as a swinging pendulum.SOLUTION: A rocking oscillator 6 having its barycentric position as an oscillation center 8 is set on a hanging side 7 via a rotary support 9 in a freely oscillating manner. A damping mechanism 10 for damping the oscillation by generation of a resistance force by the oscillation of the rocking oscillator 6, is added. The position directly below the barycentric position 8 of the rocking oscillator 6 is set as a suspending point 11, and a mass body 2 is suspended from there by the suspending material 1. The natural frequency of the mass body 2 determined by the length Lof the suspending material 1 is synchronized with that in the oscillation of the rocking oscillator 6 determined by the distance Lfrom the oscillation center 8 to the suspending point 11.

Description

本発明は振り子として振動する吊り構造物を対象とする吊り制振構造に関する。   The present invention relates to a suspension damping structure for a suspension structure that vibrates as a pendulum.

建築・土木の技術分野において各種の吊り構造物の振動を低減すること、たとえばクレーンによる揚重作業時に吊り荷の揺れを低減すること、あるいは天井から吊り下げられて設置されている各種の装置や機具類の地震時の揺れを低減することは、作業安全性や地震時における建物の安全性・健全性を確保し、居住者の安心感を維持するうえで重要であるが、そのような吊り構造物の揺れを抑制し速やかに減衰させ得る有効な制振構造は確立されていない。   Reduce vibrations of various suspended structures in the technical field of construction and civil engineering, for example, reduce swinging of suspended loads during crane lifting, or various devices installed suspended from the ceiling Reducing the shaking of equipment during an earthquake is important to ensure work safety, the safety and soundness of buildings during an earthquake, and maintain a sense of security for residents. An effective vibration control structure that can suppress the vibration of the structure and quickly attenuate it has not been established.

上記のような吊り構造物は、図４に示すようにワイヤー等の曲げ剛性がない吊り材１によって質量体２が吊り下げられた振り子としてモデル化できるが、現時点においてそのような振り子に対する制振手法としては、（ａ）に示すようにＴＭＤ（動吸振機構）３を設置するか、（ｂ）に示すように吊り元６の近傍にオイルダンパー４等の粘性減衰装置を設置するか、（ｃ）に示すように吊り元の近傍をブレース材５等の変形拘束部材により支持することが考えられる。   The suspension structure as described above can be modeled as a pendulum in which the mass body 2 is suspended by a suspension member 1 having no bending rigidity such as a wire as shown in FIG. As a technique, as shown in (a), a TMD (dynamic vibration absorbing mechanism) 3 is installed, or as shown in (b), a viscous damping device such as an oil damper 4 is installed in the vicinity of the suspension base 6 ( As shown in c), it is conceivable that the vicinity of the suspension source is supported by a deformation restraining member such as the brace material 5.

また、特許文献１〜３には天井面から吊り支持された照明器具を対象として吊り材の中段部にバランサーや可動質量からなる制振装置を設置するものが提案され、特許文献４には横揺れ障害を生じやすい構造物に適用する重力作用型動吸振器についての提案がある。   Further, Patent Documents 1 to 3 propose a lighting apparatus that is suspended and supported from the ceiling surface, in which a damping device including a balancer and a movable mass is installed in the middle part of the suspension material. There is a proposal for a gravity-acting dynamic vibration absorber applied to structures that are prone to shaking disturbances.

特開平９−３３０６０６号公報JP-A-9-330606 特開平１１−８２６１３号公報JP-A-11-82613 特開平１１−１８２６２０号公報JP-A-11-182620 特開平９−５３６８１号公報Japanese Patent Laid-Open No. 9-53681

図４（ａ）に示すようなＴＭＤ３による場合、ＴＭＤ３による付加質量が吊り材１に作用するから、巨大な付加質量をもつＴＭＤ３を質量体２に搭載することは現実的ではないし、付加質量を現実的な範囲に留めた場合にはさしたる応答低減効果を期待できない。
図４（ｂ）に示すようなオイルダンパー４による場合、オイルダンパー４により大きな減衰を付与しようとしても吊り材１の水平剛性が小さいためオイルダンパー４の変形があまり生じず、大きな応答低減効果は得られない。
図４（ｃ）に示すように吊り元の近傍でブレース５により吊り材１の変形を拘束しても、振り子の長さがやや短くなる（固有周期が短くなる）だけで振動自体は殆ど変わらず、大きな制振効果は得られない。 In the case of TMD3 as shown in FIG. 4 (a), since the additional mass due to TMD3 acts on the suspension member 1, it is not realistic to mount the TMD3 having a huge additional mass on the mass body 2, and the additional mass is not increased. When it is kept within a realistic range, it is not possible to expect a further response reduction effect.
In the case of the oil damper 4 as shown in FIG. 4B, even if it is intended to give a large damping to the oil damper 4, the horizontal rigidity of the suspension material 1 is small, so that the oil damper 4 does not deform so much, and a large response reduction effect is obtained. I can't get it.
As shown in FIG. 4C, even if the deformation of the suspension material 1 is restrained by the brace 5 in the vicinity of the suspension source, the vibration itself is almost changed only by slightly shortening the pendulum length (shortening the natural period). Therefore, a great vibration control effect cannot be obtained.

また、特許文献１〜３に示される制振装置は実質的にＴＭＤであるから、図４（ａ）の場合と同様に充分な効果を得るためには大きな付加質量を必要とし、照明器具程度の小質量のものには適用可能ではあるものの大規模かつ大質量の吊り構造物を対象とする制振手法としては現実的ではない。
さらに特許文献４に示される動吸振器はリンク等の曲げ剛性の大きい吊り部材によって吊り支持されている構造物を対象とするものであって、ワイヤー等の曲げ剛性のない吊り材による吊り構造物には適用できるものではない。 Moreover, since the damping device shown by patent documents 1-3 is substantially TMD, in order to acquire sufficient effect similarly to the case of FIG. Although it can be applied to those with a small mass, it is not realistic as a vibration control method for a large-scale and large-mass suspension structure.
Furthermore, the dynamic vibration absorber disclosed in Patent Document 4 is intended for a structure that is suspended and supported by a suspension member having a high bending rigidity such as a link, and is a suspension structure that uses a suspension material that does not have a bending rigidity such as a wire. Is not applicable.

上記事情に鑑み、本発明はワイヤー等の曲げ剛性のない吊り材により吊り支持されて振り子として振動する吊り構造物の振動を速やかに減衰させ得る有効適切な吊り制振構造を提供することを目的とする。   In view of the above circumstances, an object of the present invention is to provide an effective and appropriate suspension damping structure that can quickly attenuate the vibration of a suspension structure that is suspended and supported by a suspension member having no bending rigidity such as a wire and vibrates as a pendulum. And

本発明は曲げ剛性を有しない吊り材によって質量体が吊り下げられて振り子として振動する吊り構造物を対象とする吊り制振構造であって、重心位置を揺動中心とするロッキング揺動体を吊り元に回転支承を介して揺動自在に設置するとともに、該ロッキング揺動体の揺動により抵抗力を生じてその揺動を減衰せしめる減衰機構を付加し、前記ロッキング揺動体の重心位置の直下を吊り点としてその吊り点から前記質量体を前記吊り材により吊り下げるとともに、前記吊り材の長さにより定まる前記質量体の固有振動数と、前記揺動中心から前記吊り点までの距離により定まる前記ロッキング揺動体の揺動における固有振動数とを同調させたことを特徴とする。   The present invention is a suspension vibration control structure for a suspension structure in which a mass body is suspended by a suspension member having no bending rigidity and vibrates as a pendulum, and a rocking oscillator having a center of gravity at the center of oscillation is suspended. Originally, it is installed so as to be able to swing through a rotating support, and a damping mechanism is added to generate a resistance force by swinging the rocking rocking body so as to attenuate the rocking. The mass body is suspended from the suspension point by the suspension material as a suspension point, and is determined by the natural frequency of the mass body determined by the length of the suspension material and the distance from the swing center to the suspension point. It is characterized in that the natural frequency in the rocking rocking body rocking is synchronized.

本発明においては、前記ロッキング揺動体の揺動による回転慣性モーメントIθを、前記質量体の質量Mと、前記吊り点からの前記質量体の振り子としての長さL1と、前記揺動中心から前記吊り点までの距離L2とに基づき、
Iθ＝M(L1＋2L2)L2、L1≫L2
の関係を満たすように設定すると良い。 In the present invention, the rotational inertia moment I θ due to the rocking rocking body rocking, the mass M of the mass body, the length L 1 as the pendulum of the mass body from the suspension point, and the rocking center Based on the distance L 2 from the suspension point to
I θ = M (L 1 + 2L 2 ) L 2 , L 1 >> L 2
It is good to set to satisfy the relationship.

本発明によれば、質量体には何ら手を加えずその吊り元の近傍にロッキング揺動体を設置するだけで、質量体の振り子としての振動を急峻に収斂させることができ、微小振幅から大振幅まで有効であり、制振のために設置する機構の所要高さ寸法が吊り長さに対して充分に小さくて済む。
また、固定端（吊り元）にロッキング揺動体の自重を預けることから吊り材への荷重の増加はほとんどないし、ロッキング揺動体より下方は従来の吊り構造と全く同じなので使い勝手や美観を損なうこともない。 According to the present invention, the vibration as the pendulum of the mass body can be sharply converged by simply installing the rocking rocking body in the vicinity of the suspension source without modifying the mass body. It is effective up to the amplitude, and the required height dimension of the mechanism installed for damping is sufficiently small with respect to the suspension length.
Also, since the rocking rocker's own weight is entrusted to the fixed end (hanging source), there is almost no increase in the load on the suspension material. Absent.

本発明の吊り制振構造の実施形態を示す図である。It is a figure which shows embodiment of the suspension damping structure of this invention. 同、モデル図である。FIG. 同、効果を示す図である。It is a figure which shows an effect similarly. 従来の吊り構造物に対する制振手法を示す図である。It is a figure which shows the damping method with respect to the conventional suspension structure.

図１に本発明の実施形態を示す。これは、図４に示したものと同様にワイヤー等の曲げ剛性を有しない吊り材１によって吊り下げられた質量体２が振り子として振動する吊り構造物を対象とする制振構造であって、吊り元（固定端）７に対してロッキング揺動体６を揺動自在に設置してそのロッキング揺動体６を介して質量体２を吊り下げるようにしたものである。   FIG. 1 shows an embodiment of the present invention. This is a vibration control structure for a suspended structure in which the mass body 2 suspended by a suspension material 1 having no bending rigidity such as a wire or the like vibrates as a pendulum in the same manner as shown in FIG. A rocking rocking body 6 is swingably installed with respect to a suspension base (fixed end) 7 and the mass body 2 is suspended via the rocking rocking body 6.

ロッキング揺動体６は円盤状の形態のもの、あるいは後述するように複数の錘を一体に連結したもの（図２（ｂ）参照）が好適に採用可能であり、（ｂ）に示すように重心位置を揺動中心８として回転支承９により揺動自在（揺動中心８に対して周縁部が上下方向に回転自在）に設置されているものである。   The rocking rocking body 6 can be suitably used in the form of a disk or a structure in which a plurality of weights are integrally connected (see FIG. 2 (b)), as will be described later. The position is set so as to be swingable by a rotation support 9 with the position being the swing center 8 (the peripheral portion is rotatable in the vertical direction with respect to the swing center 8).

回転支承９としてはたとえば図示例のようなボールジョイントまたはユニバーサルジョイントを固定部材９ａにより吊り元７に設置したものが好適に採用可能である。回転支承としてのボールジョイントやユニバーサルジョイントをロッキング揺動体６に装着するためには、ロッキング揺動体６を平面的に複数のブロックに分割しておいて各ブロックによりボールジョイントやユニバーサルジョイントを挟み込むようにして全体を一体化するように組み立てるか、あるいは、ロッキング揺動体６の下面にボールジョイントやユニバーサルジョイントを挿入可能な凹部を形成しておき、そこからボールジョイントやユニバーサルジョイントを挿入して重心位置に配置すれば良い。   As the rotation support 9, for example, a ball joint or a universal joint as shown in the example shown in FIG. In order to mount a ball joint or universal joint as a rotary bearing to the rocking rocking body 6, the rocking rocking body 6 is divided into a plurality of blocks in a plane and the ball joint or universal joint is sandwiched between the blocks. As a whole, or assembling so that the whole is integrated, or forming a recess into which the ball joint or universal joint can be inserted on the lower surface of the rocking rocking body 6, and then inserting the ball joint or universal joint into the center of gravity position. Just place it.

ロッキング揺動体６にはそれ自体の揺動により抵抗力を生じて揺動を減衰せしめる減衰機構１０が付加されている。図示例の場合には回転支承９としてのボールジョイントやユニバーサルジョイントに粘性減衰材あるいは摩擦減衰材を組み込んだ構成の減衰機構１０として、それら減衰材の抵抗によりロッキング揺動体６の揺動を速やかに減衰せしめるようにしている。
あるいは、そのような減衰機構に代えて、ロッキング揺動体６の周縁部と固定端（吊り元７の周辺部）との間にダンパーとして機能する適宜の減衰機構を介装するようにしても良い。 The rocking rocker 6 is provided with a damping mechanism 10 that generates a resistance force by its own rocking and attenuates the rocking. In the case of the illustrated example, as the damping mechanism 10 having a configuration in which a viscous damping material or a friction damping material is incorporated in a ball joint or a universal joint as the rotary bearing 9, the rocking rocking body 6 is quickly swung by the resistance of the damping material. It is made to attenuate.
Alternatively, instead of such a damping mechanism, an appropriate damping mechanism that functions as a damper may be interposed between the peripheral portion of the rocking rocking body 6 and the fixed end (the peripheral portion of the suspension base 7). .

そして、ロッキング揺動体６の揺動中心８である重心位置の直下の位置（すなわち実質的にロッキング揺動体６の底面中心点）に吊り点１１が設定されてそこに吊り材１としてのワイヤーの上端が接続されている。
したがって質量体２はその吊り点１１から吊り材１により吊り下げられて振り子として機能するものとなっており、本実施形態の制振構造では振り子としての質量体２の固有振動数と、上記のロッキング揺動体６の揺動の固有振動数を同調させるように各諸元が設定されている。 Then, a suspension point 11 is set at a position immediately below the center of gravity position that is the rocking center 8 of the rocking rocking body 6 (that is, the center point of the bottom surface of the rocking rocking body 6). The upper end is connected.
Therefore, the mass body 2 is suspended from the suspension point 11 by the suspension material 1 and functions as a pendulum. In the vibration damping structure of this embodiment, the natural frequency of the mass body 2 as a pendulum and the above-described Each specification is set so that the natural frequency of the rocking rocking body 6 rocks.

具体的には、（ａ）に示すように質量体２の振り子としての長さ（吊り点１１から質量体２の重心までの距離）L1、揺動中心８から吊り点１１までの距離L2（但し、L1≫L2）、重力加速度ｇ、質量体２の質量Mとすると、質量体２の固有角振動数ω0は

Figure 2011012720
となる。 Specifically, as shown in (a), the length of the mass body 2 as a pendulum (distance from the suspension point 11 to the center of gravity of the mass body 2) L 1 , the distance L from the swing center 8 to the suspension point 11 2 (where L 1 >> L 2 ), gravitational acceleration g, and mass M of mass 2, the natural angular frequency ω 0 of mass 2 is
Figure 2011012720
 It becomes.

一方、揺動中心８から吊り点１１までのロッキング揺動体６の水平剛性khは、長さL2の振り子をもとに

Figure 2011012720
となる。 On the other hand, the horizontal rigidity k h locking oscillator 6 from swing center 8 to the hanging point 11, on the basis of the length L 2 Pendulum
Figure 2011012720
 It becomes.

したがって、回転慣性モーメントIθと回転剛性khL2 2をもつロッキング揺動体６の固有角振動数ωを質量体２の固有角振動数ω0に同調させるためには

Figure 2011012720
なる関係を満足すれば良い。 Therefore, in order to synchronize the natural angular frequency ω of the rocking rocking body 6 having the rotational inertia moment I θ and the rotational rigidity k h L 2 2 with the natural angular frequency ω 0 of the mass body 2.
Figure 2011012720
 It only has to satisfy the relationship.

このように、ロッキング揺動体６の回転慣性モーメントIθは質量体２の質量Mと吊り材１の長さ比だけで設定することができる。
また、ロッキング揺動体６により揺動中心８と吊り材１上端との間に生じる慣性質量ψは

Figure 2011012720
となる。 Thus, the rotational inertia moment I θ of the rocking rocking body 6 can be set only by the ratio of the mass M of the mass body 2 to the length of the hanger 1.
Further, the inertia mass ψ generated by the rocking rocker 6 between the rocking center 8 and the upper end of the suspension member 1 is
Figure 2011012720
 It becomes.

なお、ロッキング揺動体６は単純な円盤状で各部の質量分布が均等なものでも良いが、外周部の質量が大きく内側の質量が小さいものがより合理的である。また、円盤状のような回転対称形であることには限らないが、水平面内（X−Y平面内）のどの軸に対しても回転慣性モーメントIθが同じであることが好ましい。 Note that the rocking rocking body 6 may be a simple disk and have a uniform mass distribution in each part, but it is more reasonable that the mass of the outer peripheral part is large and the inner mass is small. Although not limited to being rotationally symmetrical, such as discoid, (the X-Y plane) in the horizontal plane is preferably also against throat axis rotational moment of inertia I theta is the same.

「設計例」
具体的な設計例を図２に示す。
（ａ）に示すように質量体２の質量M＝4ton、その水平変位x1、吊り点１１（吊り材１のロッキング揺動体６への接続点）での水平変位x2とする。ロッキング揺動体６の回転慣性モーメントIθ、回転減衰係数cθとして、吊り元７と一体化された揺動中心８との間にモデル化する。
ロッキング揺動体６は（ｂ）に示すように質量m＝1tonの錘６ａを４つ使用して１辺5mの正方形の頂点に配置し、それらの錘６ａを連結部材６ｂで連結して剛体となるように一体化する。また対角線上の中心位置（交差部）で片方の連結部材６ｂに回転支承９（ボールジョイントやユニバーサルジョイント）を接続し、他方の連結部材６ｂに吊り材１を接続している。
連結部材６ｂの質量を無視して４つの錘６ａの質量のみを考慮すると、ロッキング揺動体６の質量m＝4ton、回転慣性モーメントIθは Iθ＝4×1.0×2.52＝25ton・m2、揺動中心８から吊り点１１までの距離L2＝0.5mとすると、慣性質量ψは ψ＝Iθ/L2 2＝100ton となる（水平面内の全方向で同じ）。
以上より吊り材１の長さL1は（１）式から

Figure 2011012720
となる。 `` Design example ''
A specific design example is shown in FIG.
Mass M = 4 ton of mass 2 (a), the the horizontal displacement x 1, and horizontal displacement x 2 at the hanging point 11 (point of attachment to the hanging member 1 rocking rocking body 6). As a rotational inertia moment I θ and a rotational damping coefficient c θ of the rocking rocking body 6, modeling is performed between the rocking rocker 6 and the rocking center 8 integrated with the suspension base 7.
The rocking rocking body 6 is arranged at the apex of a square with a side of 5 m using four weights 6a having a mass m = 1 ton as shown in FIG. 5B, and these weights 6a are connected by a connecting member 6b to form a rigid body. Integrate so that Further, at the center position (intersection) on the diagonal line, the rotation support 9 (ball joint or universal joint) is connected to one connecting member 6b, and the suspension member 1 is connected to the other connecting member 6b.
If only the mass of the four weights 6a is considered, ignoring the mass of the connecting member 6b, the mass m of the rocking rocking body 6 is 4 tons, and the rotational inertia moment I θ is I θ = 4 × 1.0 × 2.5 2 = 25 ton · m 2 If the distance L 2 from the swing center 8 to the suspension point 11 is 0.5 m, the inertial mass ψ becomes ψ = I θ / L 2 2 = 100 ton (the same in all directions in the horizontal plane).
From the above, the length L 1 of the suspension material 1 is obtained from the equation (1).
Figure 2011012720
 It becomes.

質量体２に初期変位x0＝0.1mを与えた後の自由振動について検討する。
ロッキング揺動体６の回転角θ、回転慣性モーメントIθ、回転減衰係数cθ、吊り材１の減衰は無視し、重力加速度gとすると、振動方程式は次式となる。

Figure 2011012720
The free vibration after giving the initial displacement x 0 = 0.1 m to the mass body 2 will be examined.
If the rotational angle θ of the rocking rocker 6, the rotational moment of inertia I θ , the rotational damping coefficient c θ , and the damping of the suspension member 1 are ignored and the gravitational acceleration g is assumed, the vibration equation is as follows.
Figure 2011012720

ここで、

Figure 2011012720
とおくと、（３）式は以下のように表される。
Figure 2011012720
 here,
Figure 2011012720
 Then, the equation (3) is expressed as follows.
Figure 2011012720

上記の（２）式と（４）式を連立することで通常の２質点系の振動モデルと同様に扱えることがわかる。   It can be seen that by combining the above equations (2) and (4), it can be handled in the same way as a normal two-mass system vibration model.

以下の条件での検討結果を示す。
質量体２の質量M＝4ton、吊り下げ長さL1＝11.5m、L2＝0.5m、全長L＝12.0m、慣性質量ψ＝100ton、回転減衰cθ＝70kNm/(rad/s)、ロッキング揺動体６の質量m＝4ton（1ton×4）、吊り下げ位置での等価な水平減衰係数ch＝280kNm(m/s)、吊り下げ長さL＝12.0mの振り子の固有振動数は6.95Hz（固有周期0.14秒）である。
比較対象としてロッキング揺動体６の慣性質量がない場合（m＝0）を検討する。減衰がない場合は初期変位x0＝0.1mの正弦波振動が継続するだけなので、回転減衰として従来型の粘性減衰を最適減衰量cθ＝20kNm/(rad/s)として付与した場合を比較対象とし、これを従来型制振とする。 The examination results under the following conditions are shown.
Mass M of mass 2 = 4 ton, hanging length L 1 = 11.5 m, L 2 = 0.5 m, total length L = 12.0 m, inertial mass ψ = 100 ton, rotational damping c θ = 70 kNm / (rad / s), The natural frequency of the pendulum with the mass m of the rocking rocker 6 = 4 ton (1 ton x 4), the equivalent horizontal damping coefficient at the suspended position c h = 280 kNm (m / s), and the suspended length L = 12.0 m 6.95 Hz (natural period 0.14 seconds).
As a comparison object, a case where there is no inertial mass of the rocking rocking body 6 (m = 0) will be examined. When there is no damping, the sinusoidal vibration with initial displacement x 0 = 0.1m only continues, so we compared the case where the conventional viscous damping was applied as the rotational damping with the optimum damping amount c θ = 20kNm / (rad / s) This is the target and this is the conventional vibration control.

質量体２に初期変位x0＝0.1mを与えて自由振動させた場合の時刻歴応答解析を行い、質量体２の変位を従来型制振と比較した結果を図３に示す。（ａ）は従来型制振の場合、（ｂ）は本発明の制振構造の場合である。
図３から、従来型の粘性減衰を付与したものでは振幅が緩やかに減少しているのに対し、本発明では急峻に応答が低減していくことがわかる。 FIG. 3 shows a result of time history response analysis when the mass body 2 is subjected to free vibration by giving an initial displacement x 0 = 0.1 m, and comparing the displacement of the mass body 2 with the conventional vibration damping. (A) is the case of the conventional vibration damping, and (b) is the case of the vibration damping structure of the present invention.
From FIG. 3, it can be seen that the amplitude is gradually decreased in the case where the conventional viscous damping is applied, whereas the response is sharply reduced in the present invention.

以下、本発明の効果を列挙する。
(1)質量体に何ら手を加えずに吊り元の近傍にロッキング揺動体を設置するだけで、質量体の振り子としての振動を急峻に収斂させることができから、制振のための機構の所要高さ寸法が吊り長さに対して充分に小さくて済む。
このような利点は特に建築・土木工事の分野においては以下の用途において有効である。
・クレーンの吊り荷の揺れ防止（工場での天井走行クレーン、建設現場のタワークレーン等）。
・ゴンドラの揺れ防止（清掃用の吊り足場、モノレール等）。
・天井吊り設備機器の揺れ対策（シャンデリア等の照明器具、舞台ホールの吊り設備）。
・下げ振りの振れ防止（鉛直芯だし用）。 The effects of the present invention are listed below.
(1) The vibration of the mass body as a pendulum can be abruptly converged simply by installing a rocking rocker near the suspension source without any modification to the mass body. The required height dimension is sufficiently small relative to the suspension length.
Such advantages are particularly effective in the following applications in the field of construction and civil engineering.
・ Prevents the crane's suspended load from shaking (overhead traveling crane at the factory, tower crane at the construction site, etc.).
・ Prevents the gondola from shaking (cleaning scaffolds, monorails, etc.).
-Countermeasures for shaking equipment on ceiling suspension equipment (lighting fixtures such as chandeliers, suspension equipment for stage halls).
・ Prevents swinging of the downward swing (for vertical centering).

(2)微小振幅から大振幅まで有効なパッシブ型の制振構造であり、外部エネルギーを必要としない。電気やコンピュータ制御が不要であり単純な機構なので、信頼性が高くローコストである。
(3)常時（使用時）の揺れだけでなく、地震時の後揺れにも効果的である。吊り構造は一般的に固有周期が長く減衰が小さい構造であり、地震後にも長時間揺れが持続する傾向にある。これを早期に解消することは、居住者の恐怖心を軽減するだけでなく、吊り構造の疲労特性を改善することにも効果的である。
(4)本発明の制振機構は、固定端（吊り元）にロッキング揺動体の自重を預けることから吊り材への荷重の増加はほとんどない。また、ロッキング揺動体より下方は従来の吊り構造と全く同じなので使い勝手や美観を損なうこともない。 (2) It is a passive vibration control structure that is effective from minute amplitude to large amplitude, and does not require external energy. Electricity and computer control are not required and the mechanism is simple, so it is highly reliable and low cost.
(3) It is effective not only for regular (during use) shaking but also for shaking after an earthquake. A suspended structure generally has a long natural period and a small attenuation, and tends to continue shaking for a long time after an earthquake. Resolving this at an early stage is effective not only in reducing the fear of residents, but also in improving the fatigue characteristics of the suspension structure.
(4) Since the vibration damping mechanism of the present invention deposits the weight of the rocking rocking body at the fixed end (the suspension base), there is almost no increase in the load on the suspension material. In addition, since the portion below the rocking rocking body is exactly the same as the conventional suspension structure, the usability and aesthetics are not impaired.

１ 吊り材（ワイヤー）
２ 質量体
６ ロッキング揺動体
６ａ 錘
６ｂ 連結部材
７ 吊り元（固定端）
８ 揺動中心（重心位置）
９ 回転支承（ボールジョイントまたはユニバーサルジョイント）
９ａ 固定部材
１０ 減衰機構
１１ 吊り点 1 Hanging material (wire)
2 Mass body 6 Rocking rocking body 6a Weight 6b Connecting member 7 Suspension origin (fixed end)
8 Oscillation center (center of gravity)
9 Rotating bearing (ball joint or universal joint)
9a Fixing member 10 Damping mechanism 11 Hanging point

Claims (2)

曲げ剛性を有しない吊り材によって質量体が吊り下げられて振り子として振動する吊り構造物を対象とする吊り制振構造であって、
重心位置を揺動中心とするロッキング揺動体を吊り元に回転支承を介して揺動自在に設置するとともに、該ロッキング揺動体の揺動により抵抗力を生じてその揺動を減衰せしめる減衰機構を付加し、
前記ロッキング揺動体の重心位置の直下を吊り点としてその吊り点から前記質量体を前記吊り材により吊り下げるとともに、
前記吊り材の長さにより定まる前記質量体の固有振動数と、前記揺動中心から前記吊り点までの距離により定まる前記ロッキング揺動体の揺動における固有振動数とを同調させたことを特徴とする吊り制振構造。 A suspension damping structure for a suspension structure in which a mass body is suspended by a suspension member having no bending rigidity and vibrates as a pendulum,
A rocking oscillating body with the center of gravity as the oscillating center is installed so as to be able to oscillate via a rotating support with a suspension base, and a damping mechanism that generates a resistance force by oscillating the rocking oscillating body and attenuates the oscillation Add
The mass body is suspended from the suspension point by the suspension member, with the suspension point being directly below the center of gravity of the rocking rocking body, and
The natural frequency of the mass body determined by the length of the suspension member is synchronized with the natural frequency of the rocking rocking body rocked by the distance from the rocking center to the hanging point. Suspended vibration control structure. 請求項１記載の吊り制振構造であって、
前記ロッキング揺動体の揺動による回転慣性モーメントIθを、前記質量体の質量Mと、前記吊り点からの前記質量体の振り子としての長さL1と、前記揺動中心から前記吊り点までの距離L2とに基づき、
Iθ＝M(L1＋2L2)L2、L1≫L2
の関係を満たすように設定したことを特徴とする吊り制振構造。 The suspension damping structure according to claim 1,
Rotational inertia moment I θ due to rocking of the rocking rocking body, mass M of the mass body, length L 1 as the pendulum of the mass body from the suspension point, and from the swing center to the suspension point Based on the distance L 2 of
I θ = M (L 1 + 2L 2 ) L 2 , L 1 >> L 2
Suspension damping structure characterized by being set to satisfy the relationship
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