JP3460884B2 - Vibration suppression device for structures - Google Patents
Vibration suppression device for structuresInfo
- Publication number
- JP3460884B2 JP3460884B2 JP04290895A JP4290895A JP3460884B2 JP 3460884 B2 JP3460884 B2 JP 3460884B2 JP 04290895 A JP04290895 A JP 04290895A JP 4290895 A JP4290895 A JP 4290895A JP 3460884 B2 JP3460884 B2 JP 3460884B2
- Authority
- JP
- Japan
- Prior art keywords
- leaf spring
- vibration
- viscoelastic material
- suppression device
- vibration suppression
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Buildings Adapted To Withstand Abnormal External Influences (AREA)
- Vibration Prevention Devices (AREA)
Description
【発明の詳細な説明】
【０００１】
【産業上の利用分野】本発明は，自動車，鉄道，航空機
などの輸送機械，あるいは産業機械，電化製品，建築構
造物等に取り付けて振動や騒音の抑制を図るための構造
物の振動抑制装置に関する。
【０００２】
【従来の技術】本願発明者らは先に特願平２−２５８３
５１号として振動抑制装置を提案している。この先願発
明は図３に示すように，構造物２上に設けられた支持部
４から左右両方向へ互いに間隔を保って平行に２枚の板
バネ３を突設し，前記板バネ３を粘弾性材料８により層
状に接合し，前記層状に接合された板バネ３の自由端側
にそれぞれ錘７を取り付け，前記板バネ３，粘弾性材料
８及び錘７を前記支持部４を中心として左右対称に配置
してなる構造物の振動抑制装置１として構成されたもの
で，構造物２の振動によって前記板バネ３が支持部４を
中心としてバランスよく共振し，構造物２の振動を抑制
する。
【０００３】
【発明が解決しようとする課題】上記従来技術は粘弾性
材料を２枚の弾性板の間に挟んだ粘弾性板バネ構造を特
徴とするもので，この板バネ構造の固有振動数は粘弾性
材料の剪断弾性係数と板バネの曲げ剛性とによって決定
されるが，粘弾性材料の位置が複合板バネ構造の中立軸
に近づくにつれ，前記固有振動数は粘弾性材料の剪断弾
性係数に支配されることになる。この粘弾性材料の剪断
弾性係数は温度によって変化するので，板バネ構造を有
する振動抑制装置を用いて得られる振動低減量が使用す
る環境の温度によって大きく変動する場合があり，温度
変化の激しい環境での使用に難があった。本発明は上記
従来技術による振動抑制装置に改良を加え，使用する環
境温度の変化に対応させ得る振動抑制装置を提供するこ
とを目的とする。
【０００４】
【課題を解決するための手段】上記目的を達成するため
に本発明が採用する手段は，構造物上に設けられた支持
部から左右両方向へ互いに間隔を保って平行に２枚の板
バネを突設し，前記板バネを粘弾性材料により層状に接
合し，前記層状に接合された板バネの自由端側にそれぞ
れ錘を取り付け，前記板バネ，粘弾性材料及び錘を前記
支持部を中心として左右対称に配置してなる構造物の振
動抑制装置において，前記２枚の板バネのそれぞれの板
厚を異ならせたことを特徴とする構造物の振動抑制装置
として構成される。
【０００５】
【作用】本発明によれば，粘弾性材料を挟んで層状に接
合された２枚の板バネのそれぞれの厚さを異ならせて構
成することにより，粘弾性材料の位置が複合板バネ構造
の中立軸の位置から離れるために，粘弾性材料の剪断弾
性係数が板バネ構造の固有振動数に及ぼす影響が小さく
なり，温度変化に伴う板バネ構造の固有振動数の変化が
減少する。従って，使用する環境温度の影響をほとんど
受けることなく安定した性能を発揮する振動抑制装置を
提供することができる。
【０００６】
【実施例】以下，添付図面を参照して，本発明を具体化
した実施例につき説明し，本発明の理解に供する。尚，
以下の実施例は本発明を具体化した一例であって，本発
明の技術的範囲を限定するものではない。ここに，図１
は本発明の実施例に係る構造物の振動抑制装置の構成を
示す側面図，図２は実施例に係る振動抑制装置の温度特
性を従来装置と比較したグラフである。図１において，
振動抑制装置１０は粘弾性材料１８を挟んで層状に接合
され，それぞれ板厚を異にする２枚の板バネである第１
の鋼板１２と第２の鋼板１３とが，被制振対称物１１上
に支持台１４を介して左右対称に支持されている。ま
た，前記第１の鋼板１２の自由端側には，それぞれ錘１
７が対称に配備されている。
【０００７】この振動抑制装置１０は，構造物１１の振
動によって下記（１）式で求められる固有振動数で支持
部１４を中心として共振し，この共振による鋼板１２，
１３の変形に伴う粘弾性材料１８の剪断変形により，構
造物１１の振動エネルギーが熱エネルギーに変換されて
大気中に放出され，その結果構造物１１の振動が抑制さ
れる。
ｆ＝１／２π＊√（ｋ／ｍ） ……（１）
但し，ｋ：バネ定数，ｍ：錘の質量
上記固有周波数は，粘弾性材料１８の剪断弾性係数と鋼
板１２，１３の曲げ剛性とによって決定されるが，粘弾
性材料１８の位置が従来構造の場合のように板バネ構造
の中立軸にある場合には，この固有振動数は粘弾性材料
１８の剪断弾性係数に支配され，粘弾性材料１８の剪断
弾性係数は温度によって変化するので，従来構造の板バ
ネ構造では，振動低減量が温度によって変化することに
なる。そこで，本実施例においては，上記第１の鋼板１
２と第２の鋼板１３との板厚を異にして形成することに
より，第１の鋼板１２と第２の鋼板１３との間に挟設さ
れた粘弾性材料１８の粘弾性係数が温度によって変化す
ることによる板バネ構造による振動低減量の変化を減少
させることができる。
【０００８】即ち，第１の鋼板１２の板厚ｔ1 と第２の
鋼板１３と板厚ｔ2 とを同一にした従来構造では，図２
のグラフＢに示すように，環境温度によって板バネ構造
の共振周波数の変化が大きいが，本実施例による板厚を
異ならせた構造とすることにより，図２のグラフＡに示
すように，温度による共振周波数の変化は低減してい
る。これは，粘弾性材料１８の位置が板バネ構造の中立
軸の位置から離れるために，粘弾性材料１８の剪断弾性
係数が板バネ構造の固有振動数に及ぼす影響が少なくな
り，温度変化に伴う板バネ構造の固有振動数の変化が減
少するためである。これを振動低減量の温度による変化
でみると，下記表１に示すようになり，粘弾性材料１８
の厚さｔ3 を１００μｍとしたときの振動低減量は，従
来構造のｔ 1 ＝ｔ2 の場合と比べて変化が少なく，温度
の変化にかかわらず安定した振動低減量を示している。
【表１】【０００９】
【発明の効果】以上の説明の通り本発明にれば，粘弾性
材料を挟んで層状に接合された２枚の板バネのそれぞれ
の厚さを異ならせて構成することにより，粘弾性材料の
位置が複合板バネ構造の中立軸の位置から離れるため
に，粘弾性材料の剪断弾性係数が板バネ構造の固有振動
数に及ぼす影響が小さくなり，温度変化に伴う板バネ構
造の固有振動数の変化が減少する。従って，使用する環
境温度の影響をほとんど受けることなく安定した性能を
発揮する振動抑制装置を提供することができる。DETAILED DESCRIPTION OF THE INVENTION
[0001]
BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automobile, a railway, and an aircraft.
Or other transport machinery, or industrial machinery, electrical appliances, building structures
Structure for suppressing vibration and noise by attaching to structures
The present invention relates to a device for suppressing vibration of an object.
[0002]
2. Description of the Related Art The inventors of the present invention have previously described Japanese Patent Application No. Hei 2-2583.
No. 51 proposes a vibration suppression device. This prior application
As shown in FIG. 3, the support is provided on the structure 2.
4 plates in parallel from 4 in the left and right direction, keeping a distance from each other
A spring 3 is protruded, and the leaf spring 3 is formed of a viscoelastic material 8.
Free end side of the leaf spring 3 joined in a layer shape
Weight 7 is attached to each of the leaf springs 3, a viscoelastic material
8 and weight 7 are arranged symmetrically about the support part 4
As a vibration suppressing device 1 for a structure
Then, the leaf spring 3 causes the support portion 4 to move due to the vibration of the structure 2.
Resonates well in the center and suppresses vibration of structure 2
I do.
[0003]
The above prior art is viscoelastic.
Features a viscoelastic leaf spring structure in which the material is sandwiched between two elastic plates.
The natural frequency of this leaf spring structure is viscoelastic
Determined by the shear modulus of the material and the bending stiffness of the leaf spring
However, the position of the viscoelastic material is
As the frequency approaches, the natural frequency is
Sex coefficient. Shear of this viscoelastic material
Since the elastic modulus changes with temperature, it has a leaf spring structure.
The amount of vibration reduction obtained by using the
Temperature may fluctuate greatly depending on the temperature of the environment.
Difficult to use in a rapidly changing environment. The present invention is described above.
The ring used by improving the conventional vibration suppression device
Provide a vibration suppression device capable of responding to changes in ambient temperature
aimed to.
[0004]
[MEANS FOR SOLVING THE PROBLEMS] To achieve the above object
Means adopted by the present invention are the support provided on the structure.
Two plates parallel to each other in the left and right directions from the part
A spring is protruded, and the leaf spring is connected in layers with a viscoelastic material.
To the free ends of the leaf springs joined in layers.
The leaf spring, the viscoelastic material and the weight
Vibration of a structure that is symmetrically placed around the support
In the motion suppressing device, each plate of the two leaf springs
Vibration suppression device for structures characterized by different thickness
Is configured as
[0005]
According to the present invention, the viscoelastic material is sandwiched between layers.
The thickness of each of the two leaf springs
, The position of the viscoelastic material is changed to a composite leaf spring structure
Of the viscoelastic material to move away from the neutral axis
Effect of the elasticity coefficient on the natural frequency of the leaf spring structure is small
And the natural frequency of the leaf spring structure changes with temperature.
Decrease. Therefore, the effect of the ambient temperature
Vibration suppression device that exhibits stable performance without receiving
Can be provided.
[0006]
BRIEF DESCRIPTION OF THE DRAWINGS FIG.
This embodiment will be described to facilitate understanding of the present invention. still,
The following examples are examples embodying the present invention.
It is not intended to limit the technical scope of the invention. Here, Figure 1
Is a configuration of a structure vibration suppression device according to an embodiment of the present invention.
FIG. 2 is a side view showing the temperature characteristic of the vibration suppressing device according to the embodiment.
6 is a graph comparing the performance with a conventional device. In FIG.
The vibration suppressing device 10 is joined in layers with the viscoelastic material 18 interposed therebetween.
And two leaf springs, each having a different thickness.
The second steel plate 13 and the second steel plate 12
Are symmetrically supported via a support base 14. Ma
The free ends of the first steel plate 12 are each provided with a weight 1
7 are arranged symmetrically.
[0007] This vibration suppression device 10 is a
Supported by the natural frequency calculated by the following equation (1)
Resonates around the part 14, and the steel sheet 12,
Due to the shear deformation of the viscoelastic material 18 accompanying the deformation of the
The vibration energy of the structure 11 is converted into heat energy
Released into the atmosphere, resulting in reduced vibration of structure 11
It is.
f = 1 / 2π * √ (k / m) (1)
Here, k: spring constant, m: mass of weight
The natural frequency is determined by the shear modulus of the viscoelastic material 18 and the steel.
Determined by the bending stiffness of the plates 12, 13,
The position of the conductive material 18 is a leaf spring structure as in the case of the conventional structure.
The natural frequency of the viscoelastic material
Governed by the shear modulus of elasticity of the viscoelastic material 18
Since the elastic modulus changes with temperature, the plate
In the structure, the amount of vibration reduction changes with temperature.
Become. Therefore, in the present embodiment, the first steel plate 1
2 and the second steel plate 13 having different thicknesses.
Therefore, the first steel plate 12 and the second steel plate 13
The viscoelastic coefficient of the viscoelastic material 18 changes with temperature.
Change in vibration reduction due to leaf spring structure
Can be done.
That is, the thickness t of the first steel sheet 121And the second
Steel plate 13 and thickness tTwoIn the conventional structure in which
As shown in graph B, the leaf spring structure depends on the ambient temperature.
Although the change of the resonance frequency is large,
By making the structure different, the graph A shown in FIG.
Thus, the change in resonance frequency due to temperature is reduced.
You. This is because the position of the viscoelastic material 18 is a neutral leaf spring structure.
Shearing elasticity of the viscoelastic material 18 to move away from the axis position
The effect of the coefficient on the natural frequency of the leaf spring structure is reduced.
This reduces the change in the natural frequency of the leaf spring structure due to temperature changes.
This is to reduce. This is the change in vibration reduction with temperature.
Table 1 shows that the viscoelastic material 18
Thickness tThreeIs 100 μm, the amount of vibration reduction is
T of conventional structure 1= TTwoThe change is smaller than in the case of
Shows a stable amount of vibration reduction irrespective of the change in.
[Table 1][0009]
As described above, according to the present invention, the viscoelasticity
Each of two leaf springs joined in layers with the material in between
By varying the thickness of the viscoelastic material,
Because the position is away from the position of the neutral axis of the composite leaf spring structure
In addition, the natural elastic vibration of the leaf spring structure
The effect on the number is small, and the leaf spring
The change in the natural frequency of the structure is reduced. Therefore, the ring used
Stable performance with little effect of ambient temperature
It is possible to provide a vibration suppressing device that exerts its effect.
【図面の簡単な説明】
【図１】 本発明の実施例に係る振動抑制装置の構成を
示す側面図。
【図２】 実施例振動抑制装置の環境温度による共振周
波数の変化を従来構造と比較して示すグラフ。
【図３】 従来例振動抑制装置の構成を示す側面図。
【符号の説明】
１０…振動抑制装置
１１…構造物
１２…第１の鋼板（板バネ）
１３…第２の鋼板（板バネ）
１４…支持台
１７…錘
１８…粘弾性材料BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a side view showing a configuration of a vibration suppressing device according to an embodiment of the present invention. FIG. 2 is a graph showing a change in a resonance frequency of the vibration suppression device according to the embodiment with respect to an environmental temperature in comparison with a conventional structure. FIG. 3 is a side view showing a configuration of a conventional vibration suppression device. [Description of Signs] 10 ... Vibration suppression device 11 ... Structure 12 ... First steel plate (leaf spring) 13 ... Second steel plate (leaf spring) 14 ... Support 17 ... Weight 18 ... Viscoelastic material
フロントページの続き (72)発明者 田中 俊光 兵庫県神戸市西区高塚台１丁目５番５号 株式会社神戸製鋼所 神戸総合技術研 究所内 (56)参考文献 特開 平５−26294（ＪＰ，Ａ) 特開 平４−136537（ＪＰ，Ａ) 特開 平４−140531（ＪＰ，Ａ) 特開 平５−26293（ＪＰ，Ａ) (58)調査した分野(Int.Cl.7，ＤＢ名) F16F 15/00 - 15/08 F16F 1/00 - 6/00 E04H 9/02 341 Continuation of the front page (72) Inventor Toshimitsu Tanaka 1-5-5 Takatsukadai, Nishi-ku, Kobe City, Hyogo Prefecture Kobe Steel Ltd. Kobe Research Institute (56) References JP-A-5-26294 (JP, A JP-A-4-136537 (JP, A) JP-A-4-140531 (JP, A) JP-A-5-26293 (JP, A) (58) Fields investigated (Int. Cl. 7 , DB name) F16F 15/00-15/08 F16F 1/00-6/00 E04H 9/02 341
Claims (1)
方向へ互いに間隔を保って平行に２枚の板バネを突設
し，前記板バネを粘弾性材料により層状に接合し，前記
層状に接合された板バネの自由端側にそれぞれ錘を取り
付け，前記板バネ，粘弾性材料及び錘を前記支持部を中
心として左右対称に配置してなる構造物の振動抑制装置
において，前記２枚の板バネのそれぞれの板厚を異なら
せたことを特徴とする構造物の振動抑制装置。(57) [Claim 1] Two leaf springs are protruded from a support portion provided on a structure in parallel in both left and right directions at an interval from each other, and the leaf springs are made viscoelastic. A structure in which the leaf spring, the viscoelastic material, and the weight are arranged symmetrically about the support portion by attaching weights to the free ends of the leaf springs joined in layers, respectively; The vibration suppression device for a structure according to any one of claims 1 to 3, wherein the two plate springs have different plate thicknesses.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04290895A JP3460884B2 (en) | 1995-03-02 | 1995-03-02 | Vibration suppression device for structures |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP04290895A JP3460884B2 (en) | 1995-03-02 | 1995-03-02 | Vibration suppression device for structures |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH08233028A JPH08233028A (en) | 1996-09-10 |
| JP3460884B2 true JP3460884B2 (en) | 2003-10-27 |
Family
ID=12649139
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP04290895A Expired - Fee Related JP3460884B2 (en) | 1995-03-02 | 1995-03-02 | Vibration suppression device for structures |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3460884B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105202105A (en) * | 2015-09-21 | 2015-12-30 | 北京空间飞行器总体设计部 | Omni-directional vibration isolator |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19741627B4 (en) * | 1997-09-20 | 2006-04-13 | Volkswagen Ag | vibration absorber |
| KR101638175B1 (en) | 2008-11-04 | 2016-07-08 | 로오드 코포레이션 | Resonant inertial force generator having stable natural frequency |
| US10308354B2 (en) | 2011-02-04 | 2019-06-04 | Lord Corporation | Rotary wing aircraft vibration control system with resonant inertial actuators |
| JP6746509B2 (en) * | 2017-01-12 | 2020-08-26 | 株式会社神戸製鋼所 | Dynamic vibration absorber and its design method |
| JP7140709B2 (en) * | 2018-12-18 | 2022-09-21 | 株式会社神戸製鋼所 | Dynamic vibration absorber |
-
1995
- 1995-03-02 JP JP04290895A patent/JP3460884B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105202105A (en) * | 2015-09-21 | 2015-12-30 | 北京空间飞行器总体设计部 | Omni-directional vibration isolator |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH08233028A (en) | 1996-09-10 |
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