JPH04194432A - Dynamic vibration absorber - Google Patents
Dynamic vibration absorberInfo
- Publication number
- JPH04194432A JPH04194432A JP32667890A JP32667890A JPH04194432A JP H04194432 A JPH04194432 A JP H04194432A JP 32667890 A JP32667890 A JP 32667890A JP 32667890 A JP32667890 A JP 32667890A JP H04194432 A JPH04194432 A JP H04194432A
- Authority
- JP
- Japan
- Prior art keywords
- weight
- bottom plate
- spring body
- insertion hole
- vibration
- 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.)
- Granted
Links
- 239000006096 absorbing agent Substances 0.000 title claims description 14
- 238000006073 displacement reaction Methods 0.000 claims abstract description 14
- 239000012530 fluid Substances 0.000 claims abstract description 6
- 238000003780 insertion Methods 0.000 claims description 22
- 230000037431 insertion Effects 0.000 claims description 22
- 238000013016 damping Methods 0.000 claims description 10
- 230000000149 penetrating effect Effects 0.000 claims 1
- 230000002093 peripheral effect Effects 0.000 abstract description 3
- 230000001276 controlling effect Effects 0.000 abstract 1
- 238000005096 rolling process Methods 0.000 abstract 1
- 238000010521 absorption reaction Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 2
- 229910000881 Cu alloy Inorganic materials 0.000 description 1
- 229920002430 Fibre-reinforced plastic Polymers 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 210000001015 abdomen Anatomy 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 239000011151 fibre-reinforced plastic Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 235000019198 oils Nutrition 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Landscapes
- Vibration Prevention Devices (AREA)
- Foundations (AREA)
- Bridges Or Land Bridges (AREA)
- Buildings Adapted To Withstand Abnormal External Influences (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は床面或は機械本体及びその基礎、その他の外的
強制力を受けて振動する構造物における振動の減衰を増
加させる制振装置、いわゆる動吸振装置（動吸振器或は
ダイナミックダンパともいう）に関する。Detailed Description of the Invention (Industrial Application Field) The present invention is a vibration damping device that increases the attenuation of vibrations in a floor surface, a machine body, its foundation, or other structures that vibrate under external force. , relates to a so-called dynamic vibration absorber (also referred to as a dynamic vibration absorber or dynamic damper).
（従来の技術）
一般に、動吸振装置は、振動源（外力）の振動数と同じ
固有振動数をもつか、或は該外力の振動数より比較的小
さな固有振動数をもった振動系であり、これを主振動系
に付加して、主振動系の振動を低減するものであり、そ
の理論は既に公知である。(Prior Art) In general, a dynamic vibration absorption device is a vibration system that has a natural frequency that is the same as the frequency of a vibration source (external force), or has a natural frequency that is relatively smaller than the frequency of the external force. , which is added to the main vibration system to reduce the vibration of the main vibration system, and its theory is already known.
このような動吸振装置では、従来、実開昭５０−９６３
２５号公報に示されるように、重錘をばね体で支持する
構成が採用されている。Conventionally, in such a dynamic vibration absorption device,
As shown in Japanese Patent No. 25, a structure in which a weight is supported by a spring body is adopted.
（発明が解決しようとする課題）
しかしながら、このような構成によっては重錘の横揺れ
を避けることができず、該重錘の横揺れにより所望の減
衰特性を得ることができない。(Problems to be Solved by the Invention) However, with such a configuration, it is not possible to avoid horizontal shaking of the weight, and desired damping characteristics cannot be obtained due to the horizontal shaking of the weight.
従って、この重錘の横揺れを防止し、上下動のみを案内
する案内手段が望まれるところであるが、通常の案内手
段（例えばローラによるガイド）によっては摩擦力が発
生し、この摩擦力により減衰特性が大幅に減殺され、特
に振幅の小さな微小振動に対してはこの摩擦力により重
錘の動きは完全に阻止され、有効な割振手段とはならな
いものである。Therefore, it would be desirable to have a guide means that prevents the horizontal movement of the weight and guides only the vertical motion. However, with ordinary guide means (for example, guides using rollers), frictional force is generated, and this frictional force causes damping. The characteristics are significantly reduced, and the movement of the weight is completely inhibited by this frictional force, especially for minute vibrations with small amplitudes, making it ineffective as an effective means for allocating vibrations.
このようなことから、重錘の横揺れを容認しつつ、従来
のものが使用されているのが実情である。For this reason, the current situation is that conventional types are used while allowing the weight to oscillate laterally.
また、例えば建物床面にこのような動吸振装置を取り付
けた場合、床面の固有振動周期は設計時と建築竣工時で
多少変化するとともに床面への載荷物によっても変化す
るため、動吸振装置と床面の固有振動周期が一致せず、
このため振動の減衰特性が低下するという問題があった
。In addition, when such a dynamic vibration absorber is installed on the floor of a building, for example, the natural vibration period of the floor changes somewhat between the time of design and the time of construction completion, and also changes depending on the load on the floor. The natural vibration periods of the equipment and the floor do not match,
Therefore, there was a problem in that the vibration damping characteristics deteriorated.
本発明はこのような実情に鑑み案出されたものであって
、重錘の横揺れを防止し、且っ重錘の上下変位時の摩擦
抵抗を無視できるとともに動吸振装置の取り付は後も、
その固有振動数の微調整が可能な動吸振装置を提供する
ことを目的とする。The present invention has been devised in view of the above circumstances, and is capable of preventing the horizontal vibration of the weight, ignoring the frictional resistance when the weight is vertically displaced, and allowing the installation of a dynamic vibration absorber to be carried out later. too,
It is an object of the present invention to provide a dynamic vibration absorption device whose natural frequency can be finely adjusted.
（課題を解決するための手段）
前記目的を達成するため本発明は、取付板と、取付板か
ら立設された側板と、側板の他端に取着された底板とか
らなる外箱と、外箱内に配置された重錘と、前記重錘と
側板との間で、該重錘の周方向に間隔をおいた少な（と
も三か所に設けられ、重錘を支持するとともに重錘の横
方向の変位を規制する薄板ばねと、前記重錘と底板との
間及び重錘と取付板との間に配置され、重錘を支持する
ととも１こ重錘の固有振動数を微調整するばね体とを備
えることを特徴とする。(Means for Solving the Problems) To achieve the above object, the present invention provides an outer box comprising a mounting plate, a side plate erected from the mounting plate, and a bottom plate attached to the other end of the side plate; A weight arranged inside the outer box, and a small number of spaced apart spaces in the circumferential direction of the weight between the weight and the side plate. A thin leaf spring is arranged between the weight and the bottom plate and between the weight and the mounting plate to support the weight and finely adjust the natural frequency of the weight. It is characterized by comprising a spring body.
（作用）
ダね体は重錘をその釣合位置で支持し、薄板ばねは重錘
の変位に追従して可撓する。(Function) The dowel body supports the weight at its balanced position, and the thin plate spring flexes to follow the displacement of the weight.
従？て、主振動系嘉こ作用する強制振動力がこの動吸季
装置のばね体を介して重錘に伝わると、薄板ばねの横剛
性特性により重錘は横方向即ち水平方向のいずれにも殆
ど変位することがない。Follow? When the forced vibration force acting on the main vibration system is transmitted to the weight via the spring body of the dynamic absorption device, the weight will hardly move in the lateral or horizontal direction due to the lateral rigidity of the thin plate spring. No displacement.
これにより、この動吸振装置の重岬は横揺れがな（、−
振力のない上下動のみとなるので、理想的な動吸振作用
を発揮する。As a result, the heavy cape of this dynamic vibration absorber has no horizontal vibration (, -
Since there is only vertical movement without vibration, it exhibits ideal dynamic vibration absorption effect.
（実施例）
以下、本発明の好適一実施例を添付図面を参照して説明
する。(Embodiment) Hereinafter, a preferred embodiment of the present invention will be described with reference to the accompanying drawings.
第１図は装置の一部破断斜視図、第２図は要部断面側面
図、第３図は同底面図を示し、第２図は第３図のＡ−Ｂ
−Ｃ４・Ｄ矢視図、第３図は第２図のＥ−Ｅ矢視図に相
当している。Figure 1 is a partially cutaway perspective view of the device, Figure 2 is a sectional side view of the main part, Figure 3 is a bottom view of the same, and Figure 2 is A-B in Figure 3.
-C4/D arrow view, FIG. 3 corresponds to the E-E arrow view of FIG. 2.
１は動吸振装置で、動吸振装置１は外箱３と、外箱３内
に配設された重錘５と、重錘５を支持するコイルスプリ
ング７．９と、薄板ばね１１及び粘性抵抗部１３を含ん
で構成されている。1 is a dynamic vibration absorber, and the dynamic vibration absorber 1 includes an outer box 3, a weight 5 disposed inside the outer box 3, a coil spring 7.9 supporting the weight 5, a thin plate spring 11, and a viscous resistance. It is configured to include a section 13.
外箱３は、第４図に取付板を取り除いた状態の半部平面
・半部底面図を示し、第５図に半部断面側面図で示すよ
うに、矩形状の底ｉ３：ｏｌと、底板３０１′ｑ）四辺
から立設された側板３０３と、側板３０３の上端にボル
ト・ナツトで着脱可能に取着される矩形状の取付板３０
７とを備え、取付板３０７は該取付板３０７に固定され
たアンカーボルドー３０８を介して主振動系に（支）定
される。The outer box 3 has a rectangular bottom i3:ol, as shown in FIG. 4 as a half plan and half bottom view with the mounting plate removed, and as shown in FIG. 5 as a half sectional side view. Bottom plate 301'q) A side plate 303 that stands up from all four sides, and a rectangular mounting plate 30 that is removably attached to the upper end of the side plate 303 with bolts and nuts.
7, and the mounting plate 307 is (supported) by the main vibration system via an anchor Bordeaux 308 fixed to the mounting plate 307.
底板３０１の中央には粘性抵抗部１３の挿入用の孔３１
１が形成され、また、この孔３１１の周囲で矩形の頂点
に位置するようにコイルスプリング７の挿入用孔３１３
が形成され、更に、この各挿入用孔３１３の間にコイル
スプリング９の挿入用孔３１５が形成されている。A hole 31 for inserting the viscous resistance part 13 is provided in the center of the bottom plate 301.
1 is formed, and an insertion hole 313 for the coil spring 7 is formed around this hole 311 so as to be located at the apex of the rectangle.
are formed, and furthermore, an insertion hole 315 for the coil spring 9 is formed between each insertion hole 313.
重錘５は第６図に半部平面・半部底面図で、第７図及び
第８図に第６図のＡ矢視図、Ｂ矢視図で示すように、平
面視矩形状を呈し、その底面の中心には粘性抵抗部１３
の挿入用凹部５０１が形成されている。The weight 5 has a rectangular shape in plan view, as shown in FIG. 6 in a half plan and half bottom view, and in FIGS. 7 and 8 as a view in the direction of arrow A and arrow B in FIG. , a viscous resistance section 13 is located at the center of its bottom surface.
An insertion recess 501 is formed.
また、凹部５０１の周囲で前記挿入用孔３１３に対応し
た箇所にコイルスプリング７の挿入用凹部５０３が形成
されている。Furthermore, a recess 503 for inserting the coil spring 7 is formed around the recess 501 at a location corresponding to the insertion hole 313 .
また、凹部５０１の周囲で前記挿入用孔３１５に対応し
た箇所にコイルスプリング９の挿入用孔５０５が貫設さ
れ、挿入孔５０５の上半部には雌ねじ５０７が形成され
ている。Further, an insertion hole 505 for the coil spring 9 is provided around the recess 501 at a location corresponding to the insertion hole 315, and a female thread 507 is formed in the upper half of the insertion hole 505.
そして、との雌ねじ５０７には、第９図に側面図で、第
１０図に平面図で示すように、雄ねじ部５１１Ａを有す
る円柱状の雄ねじ部材５１１が螺合されている。As shown in a side view in FIG. 9 and in a plan view in FIG. 10, a cylindrical male screw member 511 having a male screw portion 511A is screwed into the female screw 507.
前記底板３０１の各挿入用孔３１３には夫々蓋３２３が
取着され、各挿入用凹部５０３内で該凹部５０３の上面
と１ｉ３２３とにわたって重錘５を支持するためのコイ
ルスプリング７が挿入されている。A lid 323 is attached to each insertion hole 313 of the bottom plate 301, and a coil spring 7 for supporting the weight 5 is inserted in each insertion recess 503 across the upper surface of the recess 503 and 1i323. There is.
前記底板３０１の各挿入用孔３１５には夫々蓋３２５が
取着され、各挿入用孔５０５内で雄ねじ部材５１１の下
面と蓋３２５とにわたって重錘５を支持するためのコイ
ルスプリング９が挿入されている。A lid 325 is attached to each insertion hole 315 of the bottom plate 301, and a coil spring 9 for supporting the weight 5 is inserted in each insertion hole 505 across the lower surface of the male threaded member 511 and the lid 325. ing.
更に、挿入用孔５０５には、取付板３０７と雄ねじ部材
５１１の上面とにわたって重錘５を下方に付勢するコイ
ルスプリング１−５が挿入されている。Further, a coil spring 1 - 5 is inserted into the insertion hole 505 so as to extend between the mounting plate 307 and the upper surface of the male threaded member 511 and bias the weight 5 downward.
上記コイルスプリング７．９．１５は底板３０１の各挿
入用孔３，１３，３２５から容易に取り付け、取り外し
が可能であり、上記コイルスプリング７．９．１５のば
ね定数や配置個数な変えることにより、動吸振装置１の
取り付は後の固有振動数の微調整が行なわれる。The coil springs 7.9.15 can be easily attached and removed from the insertion holes 3, 13, and 325 of the bottom plate 301, and by changing the spring constant and number of coil springs 7.9.15 arranged. After the dynamic vibration damping device 1 is installed, the natural frequency is finely adjusted.
粘性抵抗部】３は、ロッド１３０】、ナツト１３０３を
介して前記凹部５０１内に垂設された円板状のピストン
１３０５と、底板３０１側に取着されたシリンダ１３０
７とを備える。Viscous resistance part]3 is a rod 130], a disc-shaped piston 1305 vertically installed in the recess 501 via a nut 1303, and a cylinder 130 attached to the bottom plate 301 side.
7.
シリンダ１３０７は底板３０１の孔３１１に取着される
底板１３０７Ａと、底板１３０７Ａから立設された円筒
部１３０７Ｂと、円筒部１３０７Ｂの中間部内壁に固定
され中心に孔１３０７Ｄが形成された中間板１３０７Ｅ
とを備え、シリンダ１３０７内には少なくとも中間板１
３０７Ｅよりも上面まで粘性流体りが充填されている。The cylinder 1307 includes a bottom plate 1307A that is attached to the hole 311 of the bottom plate 301, a cylindrical part 1307B that stands up from the bottom plate 1307A, and an intermediate plate 1307E that is fixed to the inner wall of the intermediate part of the cylindrical part 1307B and has a hole 1307D formed in the center.
and at least an intermediate plate 1 in the cylinder 1307.
The viscous fluid is filled up to the upper surface of 307E.
。
前記ロッド１３０１は孔１３０７Ｄを挿通され、ピスト
ン１３０５が中間板１３０７Ｅと底板１３０７Ａの間に
配置されている。. The rod 1301 is inserted through the hole 1307D, and the piston 1305 is disposed between the intermediate plate 1307E and the bottom plate 1307A.
従って、シリンダ１３０７内には、粘性流体が密に充填
された中間板１３０７Ｅとピストン１３０５による中間
室１３１３と、ピストン１３０５と底板１３０７Ａによ
る下室１３１５が画成されている。Therefore, inside the cylinder 1307, an intermediate chamber 1313 formed by the intermediate plate 1307E and the piston 1305, which are densely filled with viscous fluid, and a lower chamber 1315 formed by the piston 1305 and the bottom plate 1307A are defined.
重錘５の各側面５Ａ上部とこの側面５Ａに対向する外箱
３の側板３０３との間には、第１１図に正面図で、第１
２図に側面図で示すように、断面がＵ字状の薄板ばね１
１がボルト・ナツト１１０１及び支持部材１１０３を介
して２枚ずつ取着されている。Between the upper part of each side 5A of the weight 5 and the side plate 303 of the outer box 3 facing the side 5A, there is a first
As shown in the side view in Figure 2, a thin plate spring 1 with a U-shaped cross section
1 are attached in pairs via bolts and nuts 1101 and support members 1103.
薄板ばね１１としては一般に鋼板が使用されるが、同等
の力学的特性を示すものであれば他の素材、例えば銅合
金や繊維強化プラスチック等も使用できる。Although a steel plate is generally used as the thin plate spring 11, other materials such as copper alloys and fiber reinforced plastics can also be used as long as they exhibit equivalent mechanical properties.
薄板ばね１１はその性質上、第１２図の紙面に沿ういず
れの方向にも可撓性を有するが、第１１図の左右方向、
即ち薄板ばね１１の長手方向に作用する力に対しては剛
性（これを横剛性という）を示す。Due to its nature, the thin plate spring 11 is flexible in any direction along the plane of the paper in FIG. 12, but in the horizontal direction in FIG.
That is, the thin plate spring 11 exhibits rigidity (this is called lateral rigidity) with respect to a force acting in the longitudinal direction.
従って、重錘５は外箱３内において前後左右方向、即ち
水平方向の変位は相殺され、上下方向の変位のみが可能
となり、水平方向には殆ど変位しない。Therefore, the displacement of the weight 5 in the front, rear, left, and right directions, that is, the horizontal direction, within the outer box 3 is canceled out, and only the vertical displacement is possible, and there is almost no horizontal displacement.
（実施例の作用）
動吸振装置１は主振動系の振動モードの腹部に対応する
位置に（例えば床面を支持する梁等に）外箱３の取付板
３０７が適宜固定手段（本実施例ではアンカーボルト）
をもって設置される。(Function of the Embodiment) The dynamic vibration absorber 1 has a mounting plate 307 of the outer box 3 at a position corresponding to the abdomen of the vibration mode of the main vibration system (for example, on a beam supporting the floor surface) with an appropriate fixing means (this embodiment). (Anchor bolt)
It will be installed with.
主振動系が振動を起こすと、この振動は動吸振装置１に
伝えられる。When the main vibration system generates vibration, this vibration is transmitted to the dynamic vibration absorber 1.
そして、外箱３は主振動系と一体的に動くので、この振
動はコイルスプリング７．９．１５を介して重錘５を振
動させる。Since the outer box 3 moves integrally with the main vibration system, this vibration vibrates the weight 5 via the coil spring 7.9.15.
重錘５の外箱３に対する相対的変位は薄板ばね１１の変
位になるが、薄板ばね１１はその長平方向への剛性を有
し、その他の方向へは殆ど抵抗を示さず、薄板ばね１１
は重錘５の四面に配設されているので、結局重錘５は上
下方向のみの変位が許容されることになる。従って重錘
５の振動は横揺れを起こすことなく、上下振動のみとな
る。The relative displacement of the weight 5 with respect to the outer box 3 is the displacement of the thin plate spring 11, but the thin plate spring 11 has rigidity in its longitudinal direction and shows almost no resistance in other directions.
are arranged on the four sides of the weight 5, so that the weight 5 is ultimately only allowed to be displaced in the vertical direction. Therefore, the weight 5 does not vibrate horizontally, but only vibrates vertically.
この重錘５の上下振動において、薄板ばね１１は殆ど抵
抗を示さず、重錘５は微小振動に対して鋭敏に反応する
。In this vertical vibration of the weight 5, the thin plate spring 11 shows almost no resistance, and the weight 5 responds sharply to minute vibrations.
また、粘性抵抗部Ｉ３においては、コイルスプリング７
．９に支持された重錘５の上下振動がそのままピストン
１３０５の変位となり、上室１３１３と下室１３１５と
に容積変化が生じ、この容積変化に伴うピストン１３０
５の外周面と円筒部１３０７Ｂ内面との間の微小間隙を
通過する粘性流体りによって重錘５の変位とは反対方向
に粘性抵抗が生じ、重錘５の振動を減衰させることにな
る。この粘性抵抗は微小振動に対しても鋭敏に反応する
。In addition, in the viscous resistance part I3, the coil spring 7
．． The vertical vibration of the weight 5 supported by the weight 9 directly causes the displacement of the piston 1305, causing a volume change in the upper chamber 1313 and the lower chamber 1315, and due to this volume change, the piston 130
The viscous fluid passing through the minute gap between the outer peripheral surface of the weight 5 and the inner surface of the cylindrical portion 1307B generates viscous resistance in the direction opposite to the displacement of the weight 5, thereby damping the vibration of the weight 5. This viscous resistance responds sensitively even to minute vibrations.
この粘性抵抗部１３の付加機能により、主振動系に対す
る動吸振装置１の固有振動数域帯が広がり、割振作用が
より確実化される。This additional function of the viscous resistance section 13 widens the natural frequency band of the dynamic vibration damping device 1 with respect to the main vibration system, thereby making the allocation action more reliable.
これと共に、薄板ばね１１の微小振動特性と粘性抵抗の
微小振動特性とが相まって微小振動に対する制振効果が
得られる。At the same time, the micro-vibration characteristics of the thin plate spring 11 and the micro-vibration characteristics of the viscous resistance combine to provide a damping effect against micro-vibrations.
また、動吸振装置１の取り付は後も、底板３０１の各挿
入用孔３１３，３１５からコイルスプリング７．９．１
５の取り付け、取り外しが容易にできるので、コイルス
プリング７．９．１５のばね定数を簡単且つ無段階的に
調整することができる。Also, even after the installation of the dynamic vibration absorber 1, the coil springs 7.9.
5 can be easily attached and removed, the spring constant of the coil spring 7.9.15 can be easily and steplessly adjusted.
また、重錘の挿入用孔５０５に雄ねじ部材５１１と、重
錘５を上方ならびに下方に付勢するコイルスプリング９
，１５を設けたので、雄ねじ部材５１１を回動操作して
蓋３２５と雄ねじ部材５１１の下面間の距離及び上蓋３
０７と雄ねじ部材５１１の上面間の距離を変えることに
より：重錘５を所定位置に位置決めできると共にコイル
スプリング９，１５に与張力をあたえ、重ｆ！！！５の
所定変位内では常にコイルスプリング９，１５のばね力
が作用するようばね力を無段階的に調節することができ
る。In addition, a male screw member 511 is inserted into the insertion hole 505 for the weight, and a coil spring 9 that urges the weight 5 upward and downward.
, 15 are provided, the distance between the lid 325 and the lower surface of the male threaded member 511 and the upper lid 3 can be adjusted by rotating the male threaded member 511.
By changing the distance between the upper surface of the male screw member 511 and the weight f! ! ! The spring force of the coil springs 9, 15 can be adjusted steplessly so that the spring force of the coil springs 9, 15 always acts within a predetermined displacement of 5.
更に、実施例では、重錘５に凹部５０３、孔５０５を合
計８つ設けたので、主振動系に合わせ用いるコイルスプ
リング７．９．１５の数を調節することが可能となる。Furthermore, in the embodiment, since a total of eight recesses 503 and eight holes 505 are provided in the weight 5, it is possible to adjust the number of coil springs 7,9,15 used according to the main vibration system.
（発明の効果）
以上の説明で明らかなように本発明によれば、重錘の横
揺れを防止し、且つ重錘の上下変位時の摩擦抵抗を無視
できる動吸振装置が得られ、微小振動に対しても確実な
割振作用を発揮し、更には、動吸振装置の取り付は後も
その固有振動数を調整することも可能となる。(Effects of the Invention) As is clear from the above description, according to the present invention, a dynamic vibration damping device can be obtained which can prevent the horizontal vibration of the weight and ignore the frictional resistance when the weight is vertically displaced. Furthermore, it is possible to adjust the natural frequency of the dynamic vibration absorber even after it is installed.
第１図は装置の一部破断斜視図、第２図は要部断面側面
図、第３図は同底面図、第４図は取付板を取り除いた状
態の外箱の半部平面・半部底面図、第５図は同・半部断
面側面図、第６図は重錘の半部平面・半部底面図、第７
図及び第８図は夫々第６図のＡ矢視図、Ｂ矢視図、第９
図は雄ねじ部材の側面図、第１０図は同・平面図、第１
１図は薄板ばねの正面図、第１２図は同・側面図である
。
尚図中１は動吸振装置、３は外箱、５は重錘、７．９．
１５はコイルスプリング、１１は薄板ばね、工５は粘性
抵抗部である。
特許出願人 フジタ工業株式会社同
オイレス工業株式会社代理人 弁理士
野 １） 茂第１図
第７図
ｂリコ ｂυｊ
第１１図
第９図Figure 1 is a partially cutaway perspective view of the device, Figure 2 is a cross-sectional side view of the main part, Figure 3 is a bottom view of the same, and Figure 4 is a half-plane and half-section of the outer box with the mounting plate removed. Bottom view, Figure 5 is a half-section side view of the weight, Figure 6 is a half-plane and half-bottom view of the weight, and Figure 7 is a half-section side view of the weight.
Figures 6 and 8 are a view in the direction of the A arrow, a view in the direction of the B arrow, and a view in the direction of the B arrow in Figure 6, respectively.
The figure is a side view of the male threaded member, Figure 10 is the same top view, and Figure 1 is the same top view.
Figure 1 is a front view of the thin plate spring, and Figure 12 is a side view of the same. In the figure, 1 is a dynamic vibration absorber, 3 is an outer box, 5 is a weight, and 7.9.
15 is a coil spring, 11 is a thin plate spring, and 5 is a viscous resistance section. Patent applicant Fujita Kogyo Co., Ltd.
Patent attorney representing Oiles Industries Co., Ltd.
Field 1) Shigeru Figure 1 Figure 7 b Rico bυj Figure 11 Figure 9
Claims (5)
他端に取着された底板とからなる外箱と、外箱内に配置
された重錘と、 前記重錘と側板との間で、該重錘の周方向に間隔をおい
た少なくとも三か所に設けられ、重錘を支持するととも
に重錘の横方向の変位を規制する薄板ばねと、 前記重錘と底板との間及び重錘と取付板との間に配置さ
れ、重錘を支持するとともに重錘の固有振動数を微調整
するばね体と、 を備えることを特徴とする動吸振装置。(1) An outer box consisting of a mounting plate, a side plate erected from the mounting plate, and a bottom plate attached to the other end of the side plate, a weight placed inside the outer box, and the weight and the side plate. thin leaf springs provided at at least three locations spaced apart in the circumferential direction of the weight to support the weight and restrict lateral displacement of the weight; the weight and the bottom plate; A dynamic vibration absorbing device comprising: a spring body disposed between the weight and the mounting plate to support the weight and finely adjust the natural frequency of the weight.
体が充填されたシリンダと、重錘側で支持され、重錘の
変位時に前記シリンダ内で粘性流体を移動させ、粘性抵
抗を生じさせるピストンとを備える粘性抵抗部が設けら
れている請求項１記載の動吸振装置。(2) Between the weight and the bottom plate, there is a cylinder supported on the bottom plate side and filled with viscous fluid, and a cylinder supported on the weight side that moves the viscous fluid within the cylinder when the weight is displaced. The dynamic vibration absorbing device according to claim 1, further comprising a viscous resistance section including a piston that generates resistance.
、該孔を覆う取り外し可能な蓋にて支持されている請求
項１記載の動吸振装置。(3) The dynamic vibration absorber according to claim 1, wherein the bottom plate has a spring body insertion hole, and the spring body is supported by a removable lid that covers the hole.
前記一底板に形成されたばね体挿入用孔に対応した箇所
に形成され、この凹部内で該凹部の上面と底板とにわた
って前記ばね体が挿入されている請求項３記載の動吸振
装置。(4) A concave portion of a predetermined depth that opens toward the bottom plate is formed in the weight at a location corresponding to the spring body insertion hole formed in the one bottom plate, and within this concave portion, the concave portion extends between the top surface of the concave portion and the bottom plate. 4. The dynamic vibration absorbing device according to claim 3, wherein the spring body is inserted.
ね体挿入用孔が前記底板に形成されたばね体挿入用孔に
対応した箇所に形成され、この重錘のばね体挿入用孔に
は雄ねじ部材が螺合され、前記ばね体は、重錘のばね体
挿入用孔内で雄ねじ部材の下面と底板及び上面と蓋とに
わたって挿入されている請求項３記載の動吸振装置。(5) A spring body insertion hole penetrating vertically and formed with a female thread is formed in the weight at a location corresponding to the spring body insertion hole formed in the bottom plate, and the spring body insertion hole of the weight is formed in a position corresponding to the spring body insertion hole formed in the bottom plate. 4. The dynamic vibration damping device according to claim 3, wherein a male threaded member is screwed together, and the spring body is inserted across the lower surface and the bottom plate of the male threaded member and the upper surface and the lid within the spring body insertion hole of the weight.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2326678A JP2673606B2 (en) | 1990-11-27 | 1990-11-27 | Dynamic vibration absorber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2326678A JP2673606B2 (en) | 1990-11-27 | 1990-11-27 | Dynamic vibration absorber |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04194432A true JPH04194432A (en) | 1992-07-14 |
| JP2673606B2 JP2673606B2 (en) | 1997-11-05 |
Family
ID=18190437
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2326678A Expired - Lifetime JP2673606B2 (en) | 1990-11-27 | 1990-11-27 | Dynamic vibration absorber |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2673606B2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100365698B1 (en) * | 1999-09-01 | 2002-12-31 | 유니슨산업 주식회사 | A elastomeric bearing which is connected movement restriction device by plate spring |
| JP2003194140A (en) * | 2001-12-21 | 2003-07-09 | Tokai Rubber Ind Ltd | Damper |
| JP2006162026A (en) * | 2004-12-10 | 2006-06-22 | Oiles Ind Co Ltd | Dynamic vibration absorber and dynamic vibration absorbing device using it |
| JP2006250329A (en) * | 2005-03-14 | 2006-09-21 | Mitsubishi Electric Corp | Vibration absorbing device and anti-seismic rack using it |
| JP2015175100A (en) * | 2014-03-13 | 2015-10-05 | 住友ゴム工業株式会社 | Vibration control device |
| CN110886196A (en) * | 2019-12-19 | 2020-03-17 | 湖北工业大学 | Bridge resonance prevention system |
| CN113799917A (en) * | 2021-09-17 | 2021-12-17 | 西北工业大学 | Vibration and noise reduction structure of ship cabin |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5993542A (en) * | 1982-11-18 | 1984-05-30 | Nippon Kokan Kk <Nkk> | Dynamic vibration absorber |
| JPH01153836A (en) * | 1987-12-09 | 1989-06-16 | Oiles Ind Co Ltd | Dynamic vibration reducing device |
-
1990
- 1990-11-27 JP JP2326678A patent/JP2673606B2/en not_active Expired - Lifetime
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5993542A (en) * | 1982-11-18 | 1984-05-30 | Nippon Kokan Kk <Nkk> | Dynamic vibration absorber |
| JPH01153836A (en) * | 1987-12-09 | 1989-06-16 | Oiles Ind Co Ltd | Dynamic vibration reducing device |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100365698B1 (en) * | 1999-09-01 | 2002-12-31 | 유니슨산업 주식회사 | A elastomeric bearing which is connected movement restriction device by plate spring |
| JP2003194140A (en) * | 2001-12-21 | 2003-07-09 | Tokai Rubber Ind Ltd | Damper |
| JP2006162026A (en) * | 2004-12-10 | 2006-06-22 | Oiles Ind Co Ltd | Dynamic vibration absorber and dynamic vibration absorbing device using it |
| JP4687092B2 (en) * | 2004-12-10 | 2011-05-25 | オイレス工業株式会社 | Dynamic vibration absorber and dynamic vibration absorber using the same |
| JP2006250329A (en) * | 2005-03-14 | 2006-09-21 | Mitsubishi Electric Corp | Vibration absorbing device and anti-seismic rack using it |
| JP2015175100A (en) * | 2014-03-13 | 2015-10-05 | 住友ゴム工業株式会社 | Vibration control device |
| CN110886196A (en) * | 2019-12-19 | 2020-03-17 | 湖北工业大学 | Bridge resonance prevention system |
| CN110886196B (en) * | 2019-12-19 | 2020-08-25 | 湖北工业大学 | Bridge resonance prevention system |
| CN113799917A (en) * | 2021-09-17 | 2021-12-17 | 西北工业大学 | Vibration and noise reduction structure of ship cabin |
| CN113799917B (en) * | 2021-09-17 | 2022-07-08 | 西北工业大学 | Vibration and noise reduction structure of ship cabin |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2673606B2 (en) | 1997-11-05 |
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