JP2013087532A - Low frequency noise reduction device - Google Patents

Low frequency noise reduction device Download PDF

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JP2013087532A
JP2013087532A JP2011230316A JP2011230316A JP2013087532A JP 2013087532 A JP2013087532 A JP 2013087532A JP 2011230316 A JP2011230316 A JP 2011230316A JP 2011230316 A JP2011230316 A JP 2011230316A JP 2013087532 A JP2013087532 A JP 2013087532A
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bridge
vibration
frequency noise
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noise reduction
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JP5795936B2 (en
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Nauemon Uno
名右衛門 宇野
Hideaki Kasabo
英彰 笠坊
Akira Miyata
明 宮田
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IHI Infrastructure Systems Co Ltd
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Abstract

PROBLEM TO BE SOLVED: To suppress low frequency noise due to a vibration of 10 to 20 Hz of a bridge.SOLUTION: A low frequency noise reduction device 100 is fixed to a bridge 110 and reduces low frequency noise generated from the bridge. The low frequency noise reduction device 100 comprises: a spring part 120 constituted of a plurality of disc springs 122 provided in conjunction, directly receiving the vibration of the bridge, and vibrating in association with the vibration of the bridge; and a weight 130 connected to the spring part in a vibration direction thereof. The resonance frequency of a vibration system constituted of the spring part and the weight is adjusted to a frequency included in a range between 10 Hz and 20 Hz.

Description

本発明は、橋梁の振動による低周波騒音の発生を抑制する低周波騒音低減装置に関する。   The present invention relates to a low-frequency noise reduction device that suppresses generation of low-frequency noise due to bridge vibration.

従来、高架橋等の橋梁の振動の抑制のために様々な手法が用いられている。例えば、トラックといった車両等が路面を走行する際の橋梁の振動を抑制するため、路面の平準化、ノージョイント化、エクスパンジョン・ジョイント（Ｅｘｐ．Ｊ．）の改良等が行われている。   Conventionally, various methods are used for suppressing vibration of a bridge such as a viaduct. For example, in order to suppress bridge vibration when a vehicle such as a truck travels on a road surface, road surface leveling, no-joint, expansion joint (Exp. J.), and the like have been performed.

また、橋梁の振動を抑制する制振装置としては、ＴＭＤ（Tuned Mass Damper）を用いる構成（例えば、特許文献１）や、ＡＭＤ（Active Mass Damper）を用いる構成が提案されている（例えば、特許文献２）。特許文献１に記載の制振装置では、橋梁の３Ｈｚ程度の振動を低減することができる。この橋梁の３Ｈｚ程度の振動は、地盤を伝わって付近の建築物等を振動させ、この建築物等の振動に伴って騒音を生じさせる。   In addition, as a vibration control device that suppresses vibration of a bridge, a configuration using TMD (Tuned Mass Damper) (for example, Patent Document 1) and a configuration using AMD (Active Mass Damper) have been proposed (for example, patents). Reference 2). In the vibration damping device described in Patent Document 1, it is possible to reduce vibration of the bridge of about 3 Hz. The vibration of about 3 Hz of this bridge is transmitted through the ground to vibrate nearby buildings and the like, and noise is generated along with the vibration of the buildings and the like.

また、特許文献２に記載の制振装置では、アクチュエータによって重錘の振動の周波数を調整することで、振動の抑制対象となる周波数を調整でき、例えば、橋梁の風等による振動を低減することができる。   Further, in the vibration damping device described in Patent Document 2, the frequency of vibration suppression can be adjusted by adjusting the vibration frequency of the weight by the actuator, for example, reducing vibration due to wind of the bridge, etc. Can do.

特開平８−２３９８０５号公報JP-A-8-239805 特許第４４８１４７６号Japanese Patent No. 4481476

ところで、高架橋等の橋梁に車両が進入するとき、橋梁の振動によって、低周波、例えば１０Ｈｚ〜２０Ｈｚの空気振動が発生し、空気を伝わって周辺環境に伝播してしまう場合がある。このような低周波の空気振動は人の聴覚では音として認識され難いが、人に不快感を与える要因となるおそれがある（低周波騒音）。   By the way, when a vehicle enters a bridge such as a viaduct, air vibration of a low frequency, for example, 10 Hz to 20 Hz is generated due to vibration of the bridge, and may be transmitted to the surrounding environment through air. Such low-frequency air vibrations are not easily recognized as sounds by human hearing, but may cause discomfort to humans (low-frequency noise).

上述した特許文献１の制振装置では、橋梁の３Ｈｚ程度の振動を低減することはできるが、低周波騒音を生じさせる橋梁の振動は比較的周波数が高い分、振幅が小さくなるため、このような振動を抑制することが難しかった。また、特許文献２の制振装置では、構造が複雑であるためコストが高くなってしまう。   The above-described vibration damping device of Patent Document 1 can reduce the vibration of the bridge of about 3 Hz, but the vibration of the bridge that generates low-frequency noise has a relatively high frequency and thus has a small amplitude. It was difficult to suppress excessive vibration. Moreover, in the damping device of patent document 2, since structure is complicated, cost will become high.

本発明は、このような課題に鑑み、橋梁の１０Ｈｚ〜２０Ｈｚの振動による低周波騒音を抑制可能な、低周波騒音低減装置を提供することを目的としている。   In view of such a problem, an object of the present invention is to provide a low-frequency noise reduction device capable of suppressing low-frequency noise due to vibrations of 10 Hz to 20 Hz of a bridge.

上記課題を解決するために、本発明の低周波騒音低減装置は、橋梁に固設して橋梁から発生する低周波騒音を低減する低周波騒音低減装置であって、複数の皿ばねを連接してなり、橋梁の振動を直接的に受け、橋梁の振動に連動して振動するばね部と、ばね部の振動方向に連結された重錘と、を備え、ばね部および重錘によって構成される振動系の共振周波数は、１０〜２０Ｈｚの範囲に含まれる周波数に調整されていることを特徴とする。   In order to solve the above problems, a low-frequency noise reduction apparatus according to the present invention is a low-frequency noise reduction apparatus that is fixed to a bridge to reduce low-frequency noise generated from the bridge, and that connects a plurality of disc springs. A spring part that directly receives vibration of the bridge and vibrates in conjunction with the vibration of the bridge, and a weight connected in the vibration direction of the spring part, and is constituted by the spring part and the weight. The resonance frequency of the vibration system is adjusted to a frequency included in a range of 10 to 20 Hz.

ばね部は、重錘を挟んで対称的に複数配されてもよい。   A plurality of spring portions may be arranged symmetrically across the weight.

本発明によれば、橋梁の１０Ｈｚ〜２０Ｈｚの振動による低周波騒音を抑制可能となる。   According to the present invention, it is possible to suppress low-frequency noise due to vibrations of 10 Hz to 20 Hz of the bridge.

低周波騒音低減装置の概略的な構成を説明するための説明図である。It is explanatory drawing for demonstrating the schematic structure of a low frequency noise reduction apparatus. 車両の振動モデルを説明するための説明図である。It is explanatory drawing for demonstrating the vibration model of a vehicle. 図１（ａ）のＡ矢視図である。It is A arrow view of FIG. モデル橋梁の２次のねじり振動の概念図を示す。The conceptual diagram of the secondary torsional vibration of the model bridge is shown. 低周波騒音低減装置の設置位置を説明するための説明図である。It is explanatory drawing for demonstrating the installation position of a low frequency noise reduction apparatus. ばね部を説明するための説明図である。It is explanatory drawing for demonstrating a spring part.

以下に添付図面を参照しながら、本発明の好適な実施形態について詳細に説明する。かかる実施形態に示す寸法、材料、その他具体的な数値等は、発明の理解を容易とするための例示にすぎず、特に断る場合を除き、本発明を限定するものではない。なお、本明細書及び図面において、実質的に同一の機能、構成を有する要素については、同一の符号を付することにより重複説明を省略し、また本発明に直接関係のない要素は図示を省略する。   Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. The dimensions, materials, and other specific numerical values shown in the embodiments are merely examples for facilitating the understanding of the invention, and do not limit the present invention unless otherwise specified. In the present specification and drawings, elements having substantially the same function and configuration are denoted by the same reference numerals, and redundant description is omitted, and elements not directly related to the present invention are not illustrated. To do.

（低周波騒音低減装置１００）
図１は低周波騒音低減装置１００の概略的な構成を説明するための説明図である。特に、図１（ａ）は、橋梁１１０の下部に配された低周波騒音低減装置１００の橋梁１１０の側方から見た図を示し、図１（ｂ）は、低周波騒音低減装置１００の鉛直上方からの上面図を示す。 (Low frequency noise reduction device 100)
FIG. 1 is an explanatory diagram for explaining a schematic configuration of the low-frequency noise reduction device 100. In particular, FIG. 1A shows a view of the low-frequency noise reduction device 100 arranged at the lower part of the bridge 110 as viewed from the side of the bridge 110, and FIG. 1B shows the low-frequency noise reduction device 100. A top view from above is shown.

高架橋等の橋梁１１０において、トラック等の車両１１２が橋梁１１０を走行すると、騒音が発生する場合がある。この騒音の要因は、車両１１２全体の振動と、車両１１２のサスペンション等のばねより下の質量（以下、ばね下質量と称す）の振動と、が挙げられる。   In a bridge 110 such as a viaduct, noise may be generated when a vehicle 112 such as a truck travels on the bridge 110. Factors of the noise include vibration of the entire vehicle 112 and vibration of a mass below a spring such as a suspension of the vehicle 112 (hereinafter referred to as unsprung mass).

図２は、車両１１２の振動モデルを説明するための説明図である。ここでは、図２に示すように、車両１１２の振動を２自由度系の振動モデルに置き換える。また、振動モデルにおける各部のパラメータは、表１に示す値を例に挙げる。

Figure 2013087532
FIG. 2 is an explanatory diagram for explaining a vibration model of the vehicle 112. Here, as shown in FIG. 2, the vibration of the vehicle 112 is replaced with a two-degree-of-freedom vibration model. In addition, the values shown in Table 1 are given as examples of the parameters of each part in the vibration model.
Figure 2013087532

この場合、車両１１２全体は１．５Ｈｚ程度で振動し、ばね下質量は１６Ｈｚ程度で振動することとなる。このうち、ばね下質量の振動は、橋梁１１０を強制振動させ、床板がスピーカのコーンの役割を果たして周囲の空気を振動させて、低周波騒音として付近に伝達され、実際の音としては認識され難いが人に不快感を与える、所謂低周波騒音の要因となる可能性がある。   In this case, the entire vehicle 112 vibrates at about 1.5 Hz, and the unsprung mass vibrates at about 16 Hz. Among these, the vibration of unsprung mass causes the bridge 110 to vibrate forcibly, the floor board acts as a speaker cone, vibrates the surrounding air, is transmitted to the vicinity as low-frequency noise, and is recognized as an actual sound. This may cause so-called low-frequency noise that is difficult but uncomfortable to humans.

実際に橋梁付近の低周波騒音を測定すると、その周波数は、１６Ｈｚを含む範囲、例えば１０Ｈｚ〜２０Ｈｚ程度の値である。このように、低周波騒音の周波数に幅があるのは以下の理由による。   When actually measuring low-frequency noise near the bridge, the frequency is in a range including 16 Hz, for example, about 10 Hz to 20 Hz. The reason why there is a range in the frequency of low frequency noise is as follows.

橋梁１１０に進入してくる車両１１２は、様々な固有振動数を持ち、ランダムなタイミングで橋梁１１０に進入する。このように、複数の車両１１２が位相をずらして橋梁１１０に進入し、橋梁１１０に強制振動を発生させるため、位相がずれた複数の振動が重なり合い周波数に幅が生じていると推定できる。   The vehicle 112 entering the bridge 110 has various natural frequencies and enters the bridge 110 at random timing. In this way, since the plurality of vehicles 112 enter the bridge 110 with a phase shift and generate a forced vibration in the bridge 110, it can be estimated that a plurality of vibrations with a phase shift overlap and a width is generated in the frequency.

図１に示す、本実施形態の低周波騒音低減装置１００は、橋梁１１０の鉛直下側の橋桁１１０ａに固設され、橋梁１１０から発生する低周波騒音を低減するもので、ばね部１２０と、重錘１３０とを含んで構成される。   A low-frequency noise reduction device 100 of the present embodiment shown in FIG. 1 is fixed to a bridge girder 110a vertically below the bridge 110, and reduces low-frequency noise generated from the bridge 110. And a weight 130.

図３は、図１（ａ）のＡ矢視図である。本実施形態の橋梁１１０の橋桁１１０ａは、図３に示すように、例えば、Ｈ型鋼等で構成され、複数、本実施形態においては、鉛直方向および水平方向に２本ずつ、延伸方向が平行となるように計４本が配される。   FIG. 3 is a view taken in the direction of arrow A in FIG. As shown in FIG. 3, the bridge girder 110a of the bridge 110 according to the present embodiment is made of, for example, H-shaped steel or the like, and in the present embodiment, two in the vertical direction and two in the horizontal direction are parallel in the extending direction. A total of four are arranged.

ばね部１２０は、複数の皿ばね１２２を連接してなり、鉛直方向に並んだ２本の橋桁１１０ａの間に配され、橋梁１１０の振動を直接的に受けて、橋梁１１０の振動に連動して振動する。ここで、「直接的に受ける」は、例えば、てこの原理等を利用した機構を介さず、橋梁１１０の振動が、橋桁１１０ａや橋脚１１０ｂを介して直接伝達されることを意味する。   The spring portion 120 is formed by connecting a plurality of disc springs 122, and is arranged between two bridge beams 110a arranged in the vertical direction. The spring portion 120 directly receives the vibration of the bridge 110 and interlocks with the vibration of the bridge 110. Vibrate. Here, “directly receive” means that the vibration of the bridge 110 is directly transmitted via the bridge girder 110a and the bridge pier 110b, for example, without using a mechanism using the principle of a lever or the like.

重錘１３０は、例えば、大きさによって質量が調整された２枚の金属板で構成される。２枚の金属板は、ボルトやナット等の固定具１３０ａで重ね合わせた状態で固定される。そして、重錘１３０は、ばね部１２０の振動方向に連結される。図３に示すように、重錘１３０の上下にはばね部１２０が配される。換言すれば、ばね部１２０は、ばね部１２０の振動方向に直列に、重錘１３０を挟んで対称的に複数配される。   The weight 130 is composed of, for example, two metal plates whose masses are adjusted according to the size. The two metal plates are fixed in a state where they are overlapped with a fixture 130a such as a bolt or a nut. The weight 130 is connected in the vibration direction of the spring portion 120. As shown in FIG. 3, spring portions 120 are arranged above and below the weight 130. In other words, a plurality of spring parts 120 are arranged in series in the vibration direction of the spring part 120 with the weight 130 interposed therebetween.

重錘１３０を挟んでばね部１２０を配することで、重錘１３０の上方への揺れも、下方への揺れも、確実にばね部１２０が吸収でき、重錘１３０の振動によって橋梁１１０の構成部材に与える負荷を抑制することが可能となる。   By arranging the spring portion 120 with the weight 130 interposed therebetween, the spring portion 120 can reliably absorb both the upward and downward swings of the weight 130, and the configuration of the bridge 110 by the vibration of the weight 130. It is possible to suppress the load applied to the member.

（低周波騒音低減装置１００の橋梁１１０への取り付け位置）
制振装置の計画にあたっては、スピーカのコーンに相当する平板が、１０〜２０Ｈｚの範囲で振動している部位を特定し、振幅の大きい位置に制振装置を取り付ける必要がある。ここで想定する橋梁１１０をモデル化したモデル橋梁では、この１０〜２０Ｈｚの範囲の振動は２次のねじり振動となる。 (Installation position of the low frequency noise reduction device 100 to the bridge 110)
In planning the vibration damping device, it is necessary to identify a portion where the flat plate corresponding to the cone of the speaker vibrates in the range of 10 to 20 Hz and attach the vibration damping device to a position with a large amplitude. In the model bridge obtained by modeling the bridge 110 assumed here, the vibration in the range of 10 to 20 Hz is a secondary torsional vibration.

図４は、モデル橋梁２００および２次のねじり振動の概念図である。図４では、モデル橋梁２００のねじれの状態を理解し易くするため、モデル橋梁２００の表面に破線のメッシュを示す。２次のねじり振動によって、モデル橋梁２００は、図４に矢印で示す部分の近傍が最もよく変動する。   FIG. 4 is a conceptual diagram of the model bridge 200 and secondary torsional vibration. In FIG. 4, a broken-line mesh is shown on the surface of the model bridge 200 in order to facilitate understanding of the twisted state of the model bridge 200. Due to the secondary torsional vibration, the model bridge 200 changes most in the vicinity of the portion indicated by the arrow in FIG.

モデル橋梁２００と同様に、橋梁１１０にもねじり振動が起きることから、本実施形態のように、低周波騒音低減装置１００を、橋梁１１０における当該橋梁１１０の幅方向の外側、すなわち外桁近傍に配置することで、効果的に制振できる。   Since the torsional vibration also occurs in the bridge 110 as in the model bridge 200, the low-frequency noise reduction device 100 is placed on the outside of the bridge 110 in the width direction of the bridge 110, that is, in the vicinity of the outer girder as in this embodiment. By arranging, vibration can be effectively suppressed.

図５は、低周波騒音低減装置１００の設置位置を説明するための説明図であり、橋梁１１０の床板１１０ｃの上面視に、低周波騒音低減装置１００の設置位置を破線の円で示す。   FIG. 5 is an explanatory diagram for explaining the installation position of the low-frequency noise reduction device 100, and the installation position of the low-frequency noise reduction device 100 is indicated by a broken-line circle in a top view of the floor plate 110 c of the bridge 110.

図５に示すように、低周波騒音低減装置１００は、上述したモデル橋梁２００の矢印の位置に相当する、橋梁１１０における橋長方向の全長Ｌの１／４点と３／４点の部位の外桁内側に取り付けるものとする。   As shown in FIG. 5, the low-frequency noise reduction device 100 corresponds to the position of the arrow of the model bridge 200 described above, and the 1/4 point and 3/4 point of the total length L in the bridge length direction of the bridge 110. It shall be installed inside the outer girder.

（橋梁１１０の振幅の推定）
以下、橋梁１１０の振動の振幅について検討する。振動数ｆが１６Ｈｚの場合、円振動数ωは以下の数式１によって導出される。

Figure 2013087532
…（数式１）
したがって、橋梁１１０の振動の振幅Ａが１ｃｍであると仮定すると、加速度ａは、以下の数式２によって導かれる。
Figure 2013087532
 …（数式２）
この加速度ａの値は、大凡重力加速度の１０倍程度である。 (Estimation of bridge 110 amplitude)
Hereinafter, the vibration amplitude of the bridge 110 will be examined. When the frequency f is 16 Hz, the circular frequency ω is derived by the following formula 1.
Figure 2013087532
 ... (Formula 1)
Therefore, assuming that the vibration amplitude A of the bridge 110 is 1 cm, the acceleration a is derived by the following Equation 2.
Figure 2013087532
 ... (Formula 2)
The value of the acceleration a is about 10 times the gravitational acceleration.

しかし、上記の数式２で導出された加速度ａは、ねじりの２次モードとしては値が大きすぎる。加速度ａが取り得る常識的な範囲を考慮すると、振幅Ａは、１ｃｍの１０分の１である１ｍｍ程度と推定される。一般に、低音スピーカ等では、１ｍｍ程度の振幅で音を発することが可能である。このことから、この推定値である１ｍｍは、騒音の要因となる振動の振幅として十分な大きさであると判断される。   However, the value of the acceleration a derived by the above equation 2 is too large as a secondary mode of torsion. Considering a common sense range that the acceleration a can take, the amplitude A is estimated to be about 1 mm, which is 1/10 of 1 cm. In general, a bass speaker or the like can emit sound with an amplitude of about 1 mm. From this, it is determined that 1 mm that is the estimated value is sufficiently large as the amplitude of vibration that causes noise.

続いて、上述した低周波騒音低減装置１００の設計例を以下に示す。かかる設計例は一例であって、低周波騒音低減装置１００は、設計例として以下に記載した数値に限定されない。   Then, the design example of the low frequency noise reduction apparatus 100 mentioned above is shown below. Such a design example is an example, and the low-frequency noise reduction device 100 is not limited to the numerical values described below as a design example.

（重錘１３０の質量）
ねじりの２次モードの場合、振動に寄与する質量の橋梁１１０全体の質量に対する割合（以下、寄与割合と称す）は１／８程度と考えられる。ここで、寄与割合を１／８としたのは以下の根拠による。すなわち、ねじり振動であることから橋梁１１０の幅方向の中心付近は振動しないため、橋梁１１０全体の質量の１／２程度は振動に寄与しない。また、低周波騒音低減装置１００は橋梁１１０と４点で接続されていることから、負荷が分散されるため、各点ではそれぞれ１／４の質量を受ける。そのため、寄与割合は１／２と１／４を掛け合わせた１／８となる。 (Mass of weight 130)
In the case of the secondary mode of torsion, the ratio of mass contributing to vibration to the mass of the entire bridge 110 (hereinafter referred to as contribution ratio) is considered to be about 1/8. Here, the reason why the contribution ratio is set to 1/8 is as follows. In other words, since it is a torsional vibration, the vicinity of the center in the width direction of the bridge 110 does not vibrate, so about half of the mass of the entire bridge 110 does not contribute to the vibration. Moreover, since the low frequency noise reduction apparatus 100 is connected to the bridge 110 at four points, the load is distributed, so that each point receives ¼ mass. Therefore, the contribution ratio is 1/8, which is obtained by multiplying 1/2 and 1/4.

また、寄与割合のより詳細な計算手段として、例えば、橋梁１１０の全面積のモード鉛直成分の二乗和を、低周波騒音低減装置１００を接続する４点の位置のモード鉛直成分の二乗和で除算した値を、寄与割合としてもよい。   As a more detailed means for calculating the contribution ratio, for example, the sum of squares of the mode vertical components of the entire area of the bridge 110 is divided by the sum of squares of the mode vertical components at the four points connecting the low-frequency noise reduction apparatus 100. The value obtained may be used as the contribution ratio.

橋梁１１０の鉛直方向の単位面積当たりの重量を１トン、橋長を３０ｍ、総幅８ｍ２０ｃｍと仮定すると、橋梁１１０全体の質量は２４６トンとなる。そのため、振動に寄与する質量は１／８の約３０トンとなる。   Assuming that the weight per unit area in the vertical direction of the bridge 110 is 1 ton, the bridge length is 30 m, and the total width is 8 m20 cm, the total mass of the bridge 110 is 246 tons. Therefore, the mass contributing to vibration is about 30 tons, which is 1/8.

ここでは、重錘１３０の質量Ｍを、この橋梁１１０の振動に寄与する質量３０トンの２％、すなわち、約６００ｋｇとする。   Here, the mass M of the weight 130 is 2% of the mass of 30 tons contributing to the vibration of the bridge 110, that is, about 600 kg.

（ばね部１２０の設計）
重錘１３０の質量Ｍが６００ｋｇ、制振の対象とする振動の固有振動数ωが１６Ｈｚとすると、ばね部１２０のばね定数Ｋは、以下の数式３によって導かれる。

Figure 2013087532
…（数式３） (Design of spring part 120)
When the mass M of the weight 130 is 600 kg and the natural frequency ω of the vibration to be controlled is 16 Hz, the spring constant K of the spring portion 120 is derived by the following mathematical formula 3.
Figure 2013087532
 ... (Formula 3)

ここでは、ばね部１２０の片振幅を２ｃｍ程度、すなわち、橋梁１１０の振幅とばね部１２０の振幅の比Ｂを２０倍と設定する。すると、ばね部１２０の反力Ｐは、以下の数式４によって導かれる。

Figure 2013087532
…（数式４） Here, the half amplitude of the spring part 120 is set to about 2 cm, that is, the ratio B between the amplitude of the bridge 110 and the amplitude of the spring part 120 is set to 20 times. Then, the reaction force P of the spring part 120 is derived by the following mathematical formula 4.
Figure 2013087532
 ... (Formula 4)

重錘１３０は４点支持とする。この場合、各点に配される４つのばね部１２０それぞれのばね定数は１／４、すなわち、１．５３ｋＮ／ｍｍとなる。   The weight 130 is supported at four points. In this case, the spring constant of each of the four spring portions 120 disposed at each point is 1/4, that is, 1.53 kN / mm.

図６は、ばね部１２０を説明するための説明図である。特に、図６（ａ）は、皿ばね１２２を示し、図６（ｂ）は、棒部材１２４を示し、図６（ｃ）は、皿ばね１２２と棒部材１２４とを組み合わせたばね部１２０を示す。   FIG. 6 is an explanatory diagram for explaining the spring portion 120. 6A shows the disc spring 122, FIG. 6B shows the bar member 124, and FIG. 6C shows the spring portion 120 in which the disc spring 122 and the bar member 124 are combined. .

例えば、ばね部１２０のばねには皿ばね１２２を使用する。この皿ばね１２２は、例えば、軽荷重用で、変形能の最大値（図６（ａ）に示すｈ）が３．２ｍｍ、変形量が１．６ｍｍ（変形能の最大値の５０％）のときの反力Ｐδ０．５は１３．７２ｋＮ、変形量が２．４ｍｍ（変形能の最大値の７５％）のときの反力Ｐδ０．７５は１８．２５ｋＮとする。 For example, a disc spring 122 is used as the spring of the spring portion 120. The disc spring 122 is, for example, for a light load and has a maximum deformability (h shown in FIG. 6A) of 3.2 mm and a deformation of 1.6 mm (50% of the maximum deformability). reaction force P Deruta0.5 of time 13.72KN, reaction force P Deruta0.75 when the deformation amount is 2.4 mm (75% of the maximum value of the deformability) of the 18.25KN.

また、ばね部１２０としては、皿ばね１２２を向かい合わせとなるように２枚重ねにしたものを１組として（図６（ａ）参照）、複数組、ここでは１１組で構成される。ただし、理解を容易とするため、図１（ａ）、図３、図６（ｃ）においては数を減らして示す。   Moreover, as the spring part 120, what was piled up so that the disk springs 122 may be faced each other is made into one set (refer Fig.6 (a)), and is comprised by multiple sets, 11 sets here. However, in order to facilitate understanding, the numbers are reduced in FIGS. 1 (a), 3 and 6 (c).

皿ばね１２２を向かい合わせに組み合わせることで、皿ばね１２２が変形したときに皿ばね１２２同士の摩擦を効率的に減衰として作用させることが可能となる。   By combining the disc springs 122 face to face, the friction between the disc springs 122 can be efficiently acted as a damping when the disc springs 122 are deformed.

図６（ｃ）に示すように、ばね部１２０および重錘１３０には、それぞれ貫通孔１２０ａ、１３０ｂが設けられており、その貫通孔に棒部材１２４が挿通され、両端の皿ばね１２２の外側からワッシャー１２６ａを介してナット１２６ｂで締め付けられている。   As shown in FIG. 6 (c), the spring portion 120 and the weight 130 are provided with through holes 120a and 130b, respectively, and rod members 124 are inserted into the through holes, and the outer sides of the disc springs 122 at both ends. And is tightened with a nut 126b through a washer 126a.

１つの皿ばね１２２の変形量が仮に１．６ｍｍであった場合、１つのばね部１２０（皿ばね×２枚重ね×１１組）のばね定数Ｋ１は、以下の数式５によって導出できる。

Figure 2013087532
…（数式５） If the amount of deformation of one disc spring 122 is 1.6 mm, the spring constant K1 of one spring portion 120 (disc spring × 2 sheets × 11 sets) can be derived by the following Equation 5.
Figure 2013087532
 ... (Formula 5)

ばね部１２０は、橋梁１１０の橋長の１／４点、３／４点にそれぞれ８つずつ、すなわち、全部で１６個が配される。この１６個のばね部１２０全体のばね定数は、Ｋ１の１６倍、すなわち、６．２４ｋＮ／ｍｍとなる。   Eight spring portions 120 are arranged at each of the 1/4 point and 3/4 point of the bridge length of the bridge 110, that is, a total of 16 spring portions 120 are arranged. The total spring constant of the 16 spring portions 120 is 16 times K1, that is, 6.24 kN / mm.

同様に、１つの皿ばね１２２の変形量が仮に２．４ｍｍであった場合、１つのばね部１２０のばね定数Ｋ１は、以下の数式６によって導出できる。

Figure 2013087532
…（数式６） Similarly, if the deformation amount of one disc spring 122 is 2.4 mm, the spring constant K1 of one spring portion 120 can be derived by the following Equation 6.
Figure 2013087532
 ... (Formula 6)

そして、１６のばね部１２０全体のばね定数は、Ｋ１の１６倍、すなわち、５．５３ｋＮ／ｍｍとなる。   The spring constant of the entire 16 spring portions 120 is 16 times K1, that is, 5.53 kN / mm.

また、１つのばね部１２０の最大変形量は、３．２×２２＝７０．４２ｍｍである。仮に、初期プレ圧縮量を２５ｍｍとすると、振幅２０ｍｍの振動によって、ばね部１２０は、圧縮量５ｍｍ〜４５ｍｍの範囲で振動する。この設計例において、ばね部１２０は、最も変形したときで、ばね部１２０の変形能の最大値の６４．０％程度の幅で変形をしていることとなる。   Further, the maximum deformation amount of one spring portion 120 is 3.2 × 22 = 70.42 mm. Assuming that the initial pre-compression amount is 25 mm, the spring portion 120 vibrates in the compression amount range of 5 mm to 45 mm due to vibration with an amplitude of 20 mm. In this design example, when the spring part 120 is most deformed, it is deformed with a width of about 64.0% of the maximum value of the deformability of the spring part 120.

以上、低周波騒音低減装置１００の設計例を示したが、低周波騒音低減装置１００は、このような設計によって、ばね部１２０および重錘１３０によって構成される振動系の共振周波数が、１０〜２０Ｈｚの範囲に含まれる周波数に調整されている。   The design example of the low-frequency noise reduction device 100 has been described above, but the low-frequency noise reduction device 100 has a resonance frequency of 10 to 10 which is configured by the spring portion 120 and the weight 130 by such a design. The frequency is adjusted to be included in the range of 20 Hz.

そして、低周波騒音低減装置１００は、ばねとして皿ばね１２２を用いたＴＭＤ（Tuned Mass Damper）であるため、ばね定数がコイルばねに比べて高く、例えば、１ｍｍ程度の小さな振幅しか生じない振動も抑制できる。そのため、低周波騒音低減装置１００は、１ｍｍ程度の小さな振幅の振動による低周波騒音の発生を確実に抑制可能となる。   And since the low frequency noise reduction apparatus 100 is TMD (Tuned Mass Damper) using the disc spring 122 as a spring, the spring constant is high compared with a coil spring, for example, the vibration which produces only a small amplitude of about 1 mm. Can be suppressed. Therefore, the low-frequency noise reduction device 100 can reliably suppress the generation of low-frequency noise due to vibration with a small amplitude of about 1 mm.

また、低周波騒音低減装置１００は、構造が単純であり、かつ、皿ばね１２２を使っているためコイルばねを使う場合に比べ小型化が可能となり、製造コストを抑制できる上、既存の橋梁１１０に対して、橋梁１１０の補強などをほとんど行わずとも容易に取り付けることができる。   The low-frequency noise reduction device 100 has a simple structure and uses a disc spring 122, so that it can be downsized as compared with the case where a coil spring is used. On the other hand, the bridge 110 can be easily attached with little reinforcement.

以上、添付図面を参照しながら本発明の好適な実施形態について説明したが、本発明はかかる実施形態に限定されないことは言うまでもない。当業者であれば、特許請求の範囲に記載された範疇において、各種の変更例または修正例に想到し得ることは明らかであり、それらについても当然に本発明の技術的範囲に属するものと了解される。   As mentioned above, although preferred embodiment of this invention was described referring an accompanying drawing, it cannot be overemphasized that this invention is not limited to this embodiment. It will be apparent to those skilled in the art that various changes and modifications can be made within the scope of the claims, and these are naturally within the technical scope of the present invention. Is done.

本発明は、橋梁の振動による低周波騒音の発生を抑制する低周波騒音低減装置に利用することができる。   INDUSTRIAL APPLICABILITY The present invention can be used for a low-frequency noise reduction device that suppresses generation of low-frequency noise due to bridge vibration.

１００ …低周波騒音低減装置
１１０ …橋梁
１２０ …ばね部
１２２ …皿ばね
１３０ …重錘 DESCRIPTION OF SYMBOLS 100 ... Low frequency noise reduction apparatus 110 ... Bridge 120 ... Spring part 122 ... Disc spring 130 ... Weight

Claims (2)

橋梁に固設して該橋梁から発生する低周波騒音を低減する低周波騒音低減装置であって、
複数の皿ばねを連接してなり、前記橋梁の振動を直接的に受け、該橋梁の振動に連動して振動するばね部と、
前記ばね部の振動方向に連結された重錘と、
を備え、
前記ばね部および前記重錘によって構成される振動系の共振周波数は、１０〜２０Ｈｚの範囲に含まれる周波数に調整されていることを特徴とする低周波騒音低減装置。 A low-frequency noise reduction device for reducing low-frequency noise generated from the bridge by being fixed to the bridge,
A plurality of disc springs connected to each other, directly receiving the vibration of the bridge, and a spring portion that vibrates in conjunction with the vibration of the bridge;
A weight connected in the vibration direction of the spring portion;
With
A low-frequency noise reduction device, wherein a resonance frequency of a vibration system constituted by the spring portion and the weight is adjusted to a frequency included in a range of 10 to 20 Hz. 前記ばね部は、前記重錘を挟んで対称的に複数配されることを特徴とする請求項１に記載の低周波騒音低減装置。   The low-frequency noise reduction device according to claim 1, wherein a plurality of the spring portions are arranged symmetrically with the weight interposed therebetween.
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Publication number Priority date Publication date Assignee Title
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