JPH02221726A - Dynamic damper - Google Patents
Dynamic damperInfo
- Publication number
- JPH02221726A JPH02221726A JP4276389A JP4276389A JPH02221726A JP H02221726 A JPH02221726 A JP H02221726A JP 4276389 A JP4276389 A JP 4276389A JP 4276389 A JP4276389 A JP 4276389A JP H02221726 A JPH02221726 A JP H02221726A
- Authority
- JP
- Japan
- Prior art keywords
- elastic leg
- spring constant
- elastic
- mass body
- leg part
- 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
- 230000000694 effects Effects 0.000 abstract description 13
- 238000013016 damping Methods 0.000 abstract description 11
- 239000000463 material Substances 0.000 description 7
- 238000003384 imaging method Methods 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 239000002184 metal Substances 0.000 description 2
- 229910052751 metal Inorganic materials 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 239000000853 adhesive Substances 0.000 description 1
- 230000001070 adhesive effect Effects 0.000 description 1
- PNEYBMLMFCGWSK-UHFFFAOYSA-N aluminium oxide Inorganic materials [O-2].[O-2].[O-2].[Al+3].[Al+3] PNEYBMLMFCGWSK-UHFFFAOYSA-N 0.000 description 1
- 239000000919 ceramic Substances 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 150000002739 metals Chemical class 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Abstract
Description
【発明の詳細な説明】
［産業上の利用分野］
本発明は振動系の有害振動を抑制するダイナミックダン
パに関する。このダイナミックダンパは、例えば、エン
ジンマウントブラケット、ディファレンシャル、モータ
ハウジング等の各機械要素の有害振動を抑制するために
用いることができる。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a dynamic damper that suppresses harmful vibrations in a vibration system. This dynamic damper can be used, for example, to suppress harmful vibrations of mechanical elements such as an engine mount bracket, a differential, and a motor housing.
［従来の技術］
従来より、例えば自動車のエンジンマウントブラケット
等の振動系では、常用範囲における有害振動を抑制する
ためにダイナミックダンパが用いられている。ダイナミ
ックダンパは、振動系に固定された２個の弾性脚部と、
弾性脚部で弾性支持された１個の質量体とで構成されて
いる。このようなダイナミックダンパを取付けた振動系
では、特定の振動数域の振動に対する吸振効果により常
用範囲における振動系の有害振動を抑制できる。[Prior Art] Dynamic dampers have conventionally been used in vibration systems such as engine mount brackets of automobiles to suppress harmful vibrations in the normal use range. The dynamic damper has two elastic legs fixed to the vibration system,
It consists of one mass body elastically supported by elastic legs. In a vibration system equipped with such a dynamic damper, harmful vibrations of the vibration system in a normal use range can be suppressed by the vibration absorption effect on vibrations in a specific frequency range.
ここで、ダイナミックダンパの共振点は、基本的には、
質量体を振動方向に支持する弾性脚部のバネ定数と質量
体の質量とで定まり、固有振動数は、バネ定数が小さな
程また質量が大きい程、小さいものである。Here, the resonance point of the dynamic damper is basically:
The natural frequency is determined by the spring constant of the elastic legs that support the mass body in the vibration direction and the mass of the mass body, and the smaller the spring constant or the greater the mass, the smaller the natural frequency.
［発明が解決しようとする課題］
ところで上記したダイナミックダンパでは、ある振動数
範囲では振動系の有害振動を防止できるものの、振動系
の振動数がその振動数範囲からずれると、ダイナミック
ダンパによる制振効果が減少する。[Problems to be Solved by the Invention] Although the dynamic damper described above can prevent harmful vibrations in the vibration system within a certain frequency range, if the frequency of the vibration system deviates from that frequency range, the dynamic damper cannot suppress the vibrations. The effect decreases.
本発明は上記した実情に鑑みなされたものであり、その
目的は、より広い振動数範囲において制振効果を奏する
ダイナミックダンパを提供することにある。The present invention was made in view of the above-mentioned circumstances, and its purpose is to provide a dynamic damper that exhibits a damping effect over a wider frequency range.
［課題を解決するための手段］
本発明のダイナミックダンパは、撮動系に固定される少
なくとも２個の弾性脚部と、弾性脚部で弾性支持された
１個の質量体とで構成され、少なくとも１個の弾性脚部
のバネ定数とその弾性脚部で支持する支持質量との比率
を、残りの弾性脚部のバネ定数とその弾性脚部で支持す
る支持質量との比率と異ならせたことを特徴とするもの
である。[Means for Solving the Problems] The dynamic damper of the present invention includes at least two elastic legs fixed to an imaging system and one mass body elastically supported by the elastic legs, The ratio of the spring constant of at least one elastic leg to the support mass supported by the elastic leg is made different from the ratio of the spring constant of the remaining elastic legs to the support mass supported by the elastic leg. It is characterized by this.
この場合、上記した比率を異ならせるには、例えば、各
弾性脚部のバネ定数をそれぞれ異ならせたり、あるいは
、質量体の肉厚を部分的に異ならせたり、あるいは、質
量体の材質を部分的に変える等して質量体の密度を部分
的に異ならせて行なうことができる。In this case, in order to make the above-mentioned ratio different, for example, the spring constant of each elastic leg can be made different, or the wall thickness of the mass body can be made partially different, or the material of the mass body can be made different partially. This can be done by partially varying the density of the mass body by, for example, changing the density of the mass body.
各弾性脚部のバネ定数を異ならせるには、例えば、各弾
性脚部の材質を硬軟に変更したり、各弾性脚部の断面積
や断面形状を変更したり、各弾性脚部の長さを変更した
りして行なうことができる。To make the spring constant of each elastic leg different, for example, you can change the material of each elastic leg to hard or soft, change the cross-sectional area or cross-sectional shape of each elastic leg, or change the length of each elastic leg. This can be done by changing the .
なお、一般的に、弾性脚部の材質はゴム、樹脂、場合に
よってはバネ材とすることができ、質量体の材質は鉄鋼
、ステンレス鋼等の金属、アルミナ等のセラミックスと
することができる。Generally, the material of the elastic legs can be rubber, resin, or in some cases a spring material, and the material of the mass body can be metals such as steel or stainless steel, or ceramics such as alumina.
弾性脚部で質量体を弾性支持するにあたっては、質量体
の振動方向に対して圧縮・引張方向で弾性支持してもよ
く、あるいは、質量体の振動方向に対してせん断方向で
弾性支持することにしてもよい。質量体を圧縮・引張方
向で弾性支持する場合には、上記したバネ定数は圧縮・
引張バネ定数で基本的には定まる。また、せん断方向で
弾性支持する場合には、上記したバネ定数はせん断バネ
定数で基本的には定まる。尚、せん断バネ定数は、その
形状によって異なるがその値は圧縮・引張バネ定数に比
べて、一般的に、数分の１から数百弁の１とかなり小さ
い値となっている。When elastically supporting the mass body with the elastic legs, the mass body may be elastically supported in the compression and tension directions relative to the vibration direction of the mass body, or it may be elastically supported in the shear direction relative to the vibration direction of the mass body. You may also do so. When a mass body is elastically supported in the compression and tension directions, the above spring constant is
It is basically determined by the tension spring constant. Furthermore, in the case of elastic support in the shear direction, the above-mentioned spring constant is basically determined by the shear spring constant. Although the shear spring constant varies depending on its shape, its value is generally quite small, ranging from a fraction of a valve to one of several hundred valves, compared to a compression/tension spring constant.
なお、弾性脚部を撮動系に固定するにあたっては、弾性
脚部を振動系に接着手段で直接固定してもよく、あるい
は、ブラケット等の別の固定部を用いてバンド等で固定
してもよい。In addition, when fixing the elastic legs to the imaging system, the elastic legs may be directly fixed to the vibration system with adhesive means, or they may be fixed with a band or the like using another fixing part such as a bracket. Good too.
［実施例］
以下、本発明のダイナミックダンパの第１実施例につい
て第１図および第２図を参照して説明する。このダイナ
ミックダンパは、振動系に固定される固定部１に保持さ
れたゴム類の２個の弾性脚部２．３と、弾性脚部２．３
で弾性支持された盤状をなす金属製の１個の質量体４と
で構成されている。弾性脚部２はほぼ垂直状の側面２ａ
をもつと共に、質量体４の部位４ａ側の下面部を弾性支
持しており、一方、弾性脚部３は傾斜状の側面３ａ、３
ｂをもつと共に、質量体４の部位４ｂ側の側面部を弾性
支持している。なお、質量体４は膜状被覆部５で被覆さ
れている。[Embodiment] Hereinafter, a first embodiment of the dynamic damper of the present invention will be described with reference to FIGS. 1 and 2. This dynamic damper consists of two elastic legs 2.3 made of rubber that are held on a fixed part 1 that is fixed to a vibration system;
It is composed of a single disk-shaped metal mass body 4 that is elastically supported by. The elastic legs 2 have substantially vertical side surfaces 2a.
and elastically supports the lower surface of the mass body 4 on the side 4a, while the elastic legs 3 support the inclined side surfaces 3a, 3.
b, and elastically supports the side surface of the mass body 4 on the side of the portion 4b. Note that the mass body 4 is covered with a film-like covering portion 5.
本実施例では、質量体４の振動方向における一方の弾性
脚部２のバネ定数をに１とし、その弾性脚部２で支持す
る質量体４の支持質量をＭｌとし、質量体４の振動方向
における他方の弾性脚部３のバネ定数をに２とし、その
弾性脚部３で支持する質量体４の支持質量をＭ２とする
と、バネ定数に１と支持質量Ｍ１との比率は、バネ定数
に２と支持質量Ｍ２との比率と異なるように設定されて
いる。In this embodiment, the spring constant of one elastic leg 2 in the vibration direction of the mass body 4 is set to 1, the support mass of the mass body 4 supported by the elastic leg 2 is Ml, and the spring constant of one elastic leg 2 in the vibration direction of the mass body 4 is If the spring constant of the other elastic leg 3 is 2, and the supported mass of the mass body 4 supported by the elastic leg 3 is M2, then the ratio of the spring constant 1 to the supported mass M1 is the spring constant. 2 and the supporting mass M2.
ここで、仮に、弾性脚部３のバネ定数に２が弾性脚部２
のバネ定数に１よりも小さいと仮定すると、弾性脚部３
側の固有振動数は弾性脚部２側の固有振動数よりも低く
なる。従って第１実施例では撮動系の振動数が次第に増
加していく場合には、まず、バネ定数の大きな弾性脚部
２をほぼ支点として、質量体４の部位４ｂ側がバネ定数
の小さな弾性脚部３を介して矢印Ｐ１方向で共振する。Here, suppose that the spring constant of the elastic leg 3 is 2.
Assuming that the spring constant of is smaller than 1, the elastic leg 3
The natural frequency of the side is lower than the natural frequency of the elastic leg 2 side. Therefore, in the first embodiment, when the frequency of the imaging system gradually increases, first, the elastic leg 2 with a large spring constant is used as a fulcrum, and the part 4b side of the mass body 4 is connected to the elastic leg with a small spring constant. It resonates in the direction of arrow P1 via portion 3.
モして振動数が増加すると、弾性脚部３をほぼ支点とし
て質量体４の部位４ａ側が弾性脚部２を介して矢印Ｐ２
方向で共振する。即ち、振動数の変動につれて、質量体
４の部位４ａが主に共振したり、部位４ｂが主に共振し
たりする。そのため制振効果を得るためのダイナミック
ダンパの振動数域を従来よりも広くするのに有利でおる
。When the vibration frequency increases, the part 4a side of the mass body 4 moves through the elastic leg 2 to the point indicated by the arrow P2, with the elastic leg 3 as a fulcrum.
resonates in the direction. That is, as the frequency changes, the portion 4a of the mass body 4 mainly resonates, and the portion 4b mainly resonates. Therefore, it is advantageous to widen the frequency range of the dynamic damper for obtaining a damping effect compared to the conventional one.
又従来より広い振動数範囲において制振効果を奏するこ
とができるので、ダイナミックダンパの使用環境温度が
変化したため温度の影響で弾性脚部２．３のバネ定数が
変化する場合においても、ダイナミックダンパの制振作
用に与える温度変化の影響を少なくできる。In addition, since the damping effect can be achieved in a wider frequency range than before, even if the spring constant of the elastic leg portion 2.3 changes due to the influence of temperature due to a change in the operating environment temperature of the dynamic damper, the dynamic damper's The influence of temperature changes on vibration damping action can be reduced.
尚、上記した第１実施例では、Ｘ軸を振動数としＹ軸を
応答倍率とした場合において、特性線を模式的にあられ
すと、振動系、弾性脚部２側の部位４ａ、弾性脚部３側
の部位４ｂに対応して、−膜内には、特性線の山部が３
つ生じるものである。In the above-described first embodiment, when the X-axis is the frequency and the Y-axis is the response magnification, the characteristic lines are schematically represented by the vibration system, the part 4a on the elastic leg 2 side, and the elastic leg. Corresponding to the part 4b on the part 3 side, the peak part of the characteristic line is 3 in the - film.
There are two things that occur.
次に、本発明のダイナミックダンパの第２実施例につい
て第３図および第４図を参照して説明する。このダイナ
ミックダンパは、振動系に固定される固定部１に保持さ
れた２個の弾性脚部７．８と、弾性脚部７．８で弾性支
持された盤状をなす１個の質量体９とで構成されている
。弾性脚部７はほぼ垂直状の側面７ａをもつと共に、質
量体９の部位９ａ側の下面部を弾性支持している。弾性
脚部８はほぼ垂直状の側面８ａをもつと共に、質量体９
の部位９ｂ側の下面部を弾性支持している。Next, a second embodiment of the dynamic damper of the present invention will be described with reference to FIGS. 3 and 4. This dynamic damper consists of two elastic legs 7.8 held on a fixed part 1 fixed to a vibration system, and one disk-shaped mass body 9 elastically supported by the elastic legs 7.8. It is made up of. The elastic leg portion 7 has a substantially vertical side surface 7a, and elastically supports the lower surface portion of the mass body 9 on the portion 9a side. The elastic leg portion 8 has a substantially vertical side surface 8a and a mass body 9.
The lower surface portion of the portion 9b side is elastically supported.
弾性脚部８の断面積は弾性脚部７の断面積よりも大きく
設定されている。The cross-sectional area of the elastic legs 8 is set larger than that of the elastic legs 7.
この実施例においても、断面積の小さな弾性脚部７のバ
ネ定数に１が断面積の大きな弾性脚部８のバネ定数に２
よりも小さく設定されている。従って、一方の弾性脚部
７のバネ定数に１とその弾性脚部７で支持する質量体９
の支持質ＩＭ１との比率は、他方の弾性脚部８のバネ定
数に２とその弾性脚部８で支持する質量体９の支持質Ｉ
Ｍ２との比率と異なる。In this embodiment as well, the spring constant of the elastic legs 7 with a small cross-sectional area is 1, and the spring constant of the elastic legs 8 with a large cross-sectional area is 2.
is set smaller than. Therefore, the spring constant of one elastic leg 7 is 1, and the mass body 9 supported by that elastic leg 7
The ratio of the spring constant of the other elastic leg 8 to the supporting material IM1 is 2 and the supporting material I of the mass body 9 supported by the elastic leg 8.
The ratio is different from that of M2.
ここで、前述したように、断面積の小さな弾性脚部７の
バネ定数に１が断面積の大きな弾性脚部８のバネ定数に
２よりも小さく設定されているので弾性脚部７側の固有
振動数が弾性脚部８側の固有振動数よりも小さくなる。Here, as mentioned above, since the spring constant of the elastic leg part 7 with a small cross-sectional area is set to 1 and the spring constant of the elastic leg part 8 with a large cross-sectional area is set to be smaller than 2, the The frequency becomes smaller than the natural frequency of the elastic leg portion 8 side.
従って、振動系の振動数が次第に増加していく場合には
、まず、バネ定数の大きな弾性脚部８をほぼ支点として
、質量体９の部位９ａ側がバネ定数の小さな弾性脚部７
を介して共振する。そして振動数が増加すると、弾性脚
部７をほぼ支点として質量体９の部位９ｂ側が弾性脚部
８を介して共振する。そのため第２実施例においても、
第１実施例の場合と同様に、制振効果を得るためのダイ
ナミックダンパの］騒動数域を広くするのに有利である
。Therefore, when the frequency of the vibration system gradually increases, first, the elastic leg 8 with a large spring constant is used as a fulcrum, and the part 9a side of the mass body 9 is connected to the elastic leg 7 with a small spring constant.
resonate through. When the vibration frequency increases, the portion 9b side of the mass body 9 resonates via the elastic leg 8 with the elastic leg 7 as a fulcrum. Therefore, also in the second embodiment,
As in the case of the first embodiment, this is advantageous in widening the turbulence range of the dynamic damper for obtaining a damping effect.
次に、本発明のダイナミックダンパの第３実施例につい
て第５図および第６図を参照して説明する。このダイナ
ミックダンパは、振動系に固定される固定部１に保持さ
れた２個の弾性脚部１０．１１と、弾性脚部１０．１１
で弾性支持された盤状をなす１個の質量体１２とで構成
されている。Next, a third embodiment of the dynamic damper of the present invention will be described with reference to FIGS. 5 and 6. This dynamic damper consists of two elastic legs 10.11 held on a fixed part 1 fixed to a vibration system;
It is composed of one disk-shaped mass body 12 that is elastically supported by a disk.
質量体１２は薄肉部位１２ａと厚肉部位１２ｂとで形成
されている。弾性脚部１０はほぼ垂直状の側面１０ａを
もつと共に、質量体１２の薄肉部位１２ａ側の下面部を
弾性支持している。一方、弾性脚部１１はほぼ垂直状の
側面１１ａをもつと共に、質量体１２の厚肉部位１２ｂ
側の底面部を弾性支持している。The mass body 12 is formed of a thin section 12a and a thick section 12b. The elastic leg portion 10 has a substantially vertical side surface 10a, and elastically supports the lower surface portion of the mass body 12 on the thin wall portion 12a side. On the other hand, the elastic leg portion 11 has a substantially vertical side surface 11a, and a thick portion 12b of the mass body 12.
The bottom part of the side is elastically supported.
この第３実施例においては、一方の弾性脚部１０のバネ
定数に１と他方の弾性脚部１１のバネ定数に２とはほぼ
同じ値であるが、質量体１２の薄肉部位１２ａの質量は
これの厚肉部位１２ｂの質量よりも小ざい。従って厚肉
部位１２ｂ側の固有振動数は薄肉部位１２ａ側の固有振
動数よりも小さい。In this third embodiment, the spring constant of 1 for one elastic leg 10 and the spring constant of 2 for the other elastic leg 11 are approximately the same value, but the mass of the thin portion 12a of the mass body 12 is It is smaller than the mass of the thick portion 12b. Therefore, the natural frequency of the thick portion 12b is smaller than the natural frequency of the thin portion 12a.
そのため第３実施例では、（騒動系の振動数が次第に増
加していく場合には、まず、弾性脚部１０をほぼ支点と
して質量体１２の厚肉部位１２ｂ側が弾性脚部１１を介
して共振する。そして振動数。Therefore, in the third embodiment, (when the frequency of the commotion system gradually increases, first, the thick portion 12b side of the mass body 12 resonates via the elastic leg 11 with the elastic leg 10 as the fulcrum. And the frequency.
が増加すると、弾性脚部１１をほぼ支点として質量体１
２の薄肉部位１２ａ側が弾性脚部１０を介して揺動する
。そのため第３実施例においても、制振効果を得るため
のダイナミックダンパの振動数域を広くするのに有利で
ある。increases, the mass body 1 is moved around the elastic leg 11 as a fulcrum.
The thin-walled portion 12a side of No. 2 swings via the elastic legs 10. Therefore, the third embodiment is also advantageous in widening the frequency range of the dynamic damper for obtaining a damping effect.
特殊な例では、質量体の平面形状を三角形状とし、その
三角形状の角部分のそれぞれに、バネ定数の異なる弾性
脚部を設けてもよい。場合によっては質量体の平面形状
を円盤形状とし、バネ定数の異なる弾性脚部をその円盤
形状の周方向にそって多数個並設することにしてもよい
。この場合においても、前記した各実施例と同様に広域
用のダイナミックダンバを提供することができる。In a special example, the planar shape of the mass body may be triangular, and elastic legs having different spring constants may be provided at each corner of the triangle. In some cases, the planar shape of the mass body may be a disk shape, and a large number of elastic legs having different spring constants may be arranged in parallel along the circumferential direction of the disk shape. In this case as well, it is possible to provide a wide-area dynamic damper as in each of the embodiments described above.
［発明の作用及び効果］
本発明では、振動系で有害振動が励起されると、ダイナ
ミックダンパの質量体が共振する。これにより撮動系の
有害振動は抑制される。[Operations and Effects of the Invention] In the present invention, when harmful vibrations are excited in the vibration system, the mass body of the dynamic damper resonates. This suppresses harmful vibrations in the imaging system.
本発明によれば、広い振動数範囲において制振効果を奏
するダイナミックダンパを提供することができる。According to the present invention, it is possible to provide a dynamic damper that exhibits a damping effect in a wide frequency range.
殊に、制振効果を奏する振動数範囲を広くできるので、
ダイナミックダンパの使用環境温度が変化したため弾性
脚部のバネ定数が変動する場合においても、温度変化の
影響の少ない制振効果を期待できる。In particular, the frequency range in which the damping effect can be achieved can be widened.
Even if the spring constant of the elastic leg changes due to a change in the operating environment temperature of the dynamic damper, a damping effect that is less affected by temperature changes can be expected.
第１図および第２図は本発明の第１実施例を示し、第１
図はダイナミックダンパの側面図、第２図は第１図のＡ
−Ａ線に沿う断面図である。
第３図および第４図は本発明の第２実施例を示し、第３
図はダイナミックダンパの側面図、第４図は第３図のＢ
−Ｂ線に沿う断面図である。
第５図および第６図は本発明の第３実施例を示し、第５
図はダイナミックダンパの側面図、第６図は第５図のＣ
−Ｃ線に沿う断面図である。
図中、２は弾性脚部、３は弾性脚部、４は質量体を示す
。
特許出願人 東海ゴム工業株式会社代理人
弁理士 大川 宏
第１図
第３図
第４図
第５図
第６図
］
ζ1 and 2 show a first embodiment of the present invention;
The figure is a side view of the dynamic damper, and Figure 2 is A of Figure 1.
- It is a sectional view along the A line. 3 and 4 show a second embodiment of the present invention;
The figure is a side view of the dynamic damper, and Figure 4 is B of Figure 3.
- It is a sectional view along the B line. 5 and 6 show a third embodiment of the present invention;
The figure is a side view of the dynamic damper, and Figure 6 is C of Figure 5.
- It is a sectional view along line C. In the figure, 2 indicates an elastic leg, 3 indicates an elastic leg, and 4 indicates a mass body. Patent applicant Tokai Rubber Industries Co., Ltd. Agent
Patent Attorney Hiroshi Okawa Figure 1 Figure 3 Figure 4 Figure 5 Figure 6] ζ
Claims (1)
、前記弾性脚部で弾性支持された１個の質量体とで構成
され、 少なくとも１個の弾性脚部のバネ定数とその弾性脚部で
支持する支持質量との比率を、残りの弾性脚部のバネ定
数とその弾性脚部で支持する支持質量との比率と異なら
せたことを特徴とするダイナミックダンパ。(1) Consisting of at least two elastic legs fixed to a vibration system and one mass body elastically supported by the elastic legs, the spring constant of the at least one elastic leg and its elasticity A dynamic damper characterized in that the ratio of the supported mass supported by the leg is different from the ratio of the spring constant of the remaining elastic leg to the supported mass supported by the elastic leg.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1042763A JPH06100245B2 (en) | 1989-02-22 | 1989-02-22 | Dynamic damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1042763A JPH06100245B2 (en) | 1989-02-22 | 1989-02-22 | Dynamic damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02221726A true JPH02221726A (en) | 1990-09-04 |
| JPH06100245B2 JPH06100245B2 (en) | 1994-12-12 |
Family
ID=12645018
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1042763A Expired - Fee Related JPH06100245B2 (en) | 1989-02-22 | 1989-02-22 | Dynamic damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH06100245B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10339354A (en) * | 1997-06-09 | 1998-12-22 | Matsushita Electric Ind Co Ltd | Dynamic vibration reducer and disk storage regenerating device using dynamic vibration reducer |
| CN102494081A (en) * | 2011-12-29 | 2012-06-13 | 力帆实业(集团)股份有限公司 | Vibration absorber for fan of automobile water tank |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6622137B2 (en) * | 2016-03-31 | 2019-12-18 | 住友理工株式会社 | Soundproof cover |
| JP6622138B2 (en) | 2016-03-31 | 2019-12-18 | 住友理工株式会社 | Soundproof material |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6268051U (en) * | 1985-10-18 | 1987-04-28 | ||
| JPS62114242U (en) * | 1986-01-10 | 1987-07-21 |
-
1989
- 1989-02-22 JP JP1042763A patent/JPH06100245B2/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6268051U (en) * | 1985-10-18 | 1987-04-28 | ||
| JPS62114242U (en) * | 1986-01-10 | 1987-07-21 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH10339354A (en) * | 1997-06-09 | 1998-12-22 | Matsushita Electric Ind Co Ltd | Dynamic vibration reducer and disk storage regenerating device using dynamic vibration reducer |
| CN102494081A (en) * | 2011-12-29 | 2012-06-13 | 力帆实业(集团)股份有限公司 | Vibration absorber for fan of automobile water tank |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH06100245B2 (en) | 1994-12-12 |
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