JPH0645078Y2 - Dynamic damper - Google Patents
Dynamic damperInfo
- Publication number
- JPH0645078Y2 JPH0645078Y2 JP8550689U JP8550689U JPH0645078Y2 JP H0645078 Y2 JPH0645078 Y2 JP H0645078Y2 JP 8550689 U JP8550689 U JP 8550689U JP 8550689 U JP8550689 U JP 8550689U JP H0645078 Y2 JPH0645078 Y2 JP H0645078Y2
- Authority
- JP
- Japan
- Prior art keywords
- dynamic damper
- elastic member
- fixing portion
- elastic
- peripheral surface
- 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 - Lifetime
Links
Description
【考案の詳細な説明】 ［産業上の利用分野］ 本考案は自動車のドライブシャフトなどの回転軸の周囲
に取付けて、その回転軸に生ずる有害振動を抑制するダ
イナミックダンパに関する。さらに詳しくは、ダイナミ
ックダンパの性能を維持しつつ、回転軸への取付けがダ
イナミックダンパの一端側のみを回転軸に固定するだけ
で完了するようにして、原価低減を組付け作業性の向上
を図ったダイナミックダンパに関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention relates to a dynamic damper mounted around a rotary shaft such as a drive shaft of an automobile to suppress harmful vibrations generated on the rotary shaft. More specifically, while maintaining the performance of the dynamic damper, installation on the rotary shaft can be completed by fixing only one end of the dynamic damper to the rotary shaft to reduce costs and improve workability. About dynamic damper.
［従来の技術］ 自動車のドライブシャフトやプロペラシャフトなどの回
転軸の回転に伴って生ずる回転アンバランスによる曲げ
振動やねじり振動など、本来発生しないのが望ましい有
害振動を抑制するために、ダイナミックダンパが多く用
いられている。これらのダイナミックダンパは回転軸に
励起される有害振動の卓越振動数に、それ自身の固有振
動数を合せることにより、回転軸の振動エネルギを共振
によりダイナミックダンパの振動エネルギとして変換し
て吸収することでその機能を果たしている。[Prior Art] In order to suppress harmful vibrations that should not occur originally, such as bending vibrations and torsional vibrations due to rotational imbalance caused by the rotation of rotary shafts such as automobile drive shafts and propeller shafts, dynamic dampers are used. Many are used. These dynamic dampers convert the vibration energy of the rotating shaft into the vibration energy of the dynamic damper by resonance and absorb it by matching the natural frequency of itself with the predominant frequency of harmful vibrations excited on the rotation shaft. Fulfills that function.
自動車のドライブシャフトなどに用いられている従来の
ダイナミックダンパとして第４図にその概略断面図を示
すようなものがある。このダイナミックダンパ600は、
回転軸Ｓに挿通保持される固定部材601と、固定部材601
の外周に配設される筒状の質量部材602と、固定部材601
と質量部材602との間に挟装され、これらを連結する弾
性部材603とで構成されている。このダイナミックダン
パ600の固有振動数は、質量部材602の質量と弾性部材60
3のばね定数とによって基本的に決まる。このとき弾性
部材603は、質量部材602の振動に対し圧縮・引張り方向
に荷重を受けることになるため、この弾性部材603は、
圧縮・引張りばね定数を有する方向で質量部材602を支
持している。2. Description of the Related Art As a conventional dynamic damper used for a drive shaft of an automobile, there is a dynamic damper whose schematic sectional view is shown in FIG. This dynamic damper 600 is
A fixing member 601 which is inserted and held on the rotating shaft S, and a fixing member 601.
A cylindrical mass member 602 disposed on the outer periphery of the
And a mass member 602, and an elastic member 603 that connects them. The natural frequency of the dynamic damper 600 depends on the mass of the mass member 602 and the elastic member 60.
It is basically determined by 3 and the spring constant. At this time, since the elastic member 603 receives a load in the compression / pulling direction against the vibration of the mass member 602, the elastic member 603 is
The mass member 602 is supported in a direction having a compression / tensile spring constant.
なお、従来技術ではないが、本考案の考案者は特願昭63
−213289号にて、第３図に示すようなダイナミックダン
パを提案した。このダイナミックダンパ100は、１対の
リング状の固定部材110、110と、回転軸Ｓの外周面より
大きい内周面をもち回転軸Ｓに挿通される質量部材120
と、各固定部材110、110と質量部材120の各端部とを連
結する一対の中空円錐台状の弾性部材130、130とが、一
体的に形成されたものである。また、このダイナミック
ダンパ100の一対の固定部材110、110には、その外周面
を一周する係止溝110a、110aが形成されており、この係
止溝110a、110aにステンレス製などの固定用バンド110
b、110bを巻装して、ダイナミックダンパ100を回転軸Ｓ
に固定する。なお、このダイナミックダンパ100の弾性
部材130は、質量部材120を剪断方向において支持してい
る。Although not a conventional technique, the inventor of the present invention is
No. 213289 proposed a dynamic damper as shown in FIG. The dynamic damper 100 has a pair of ring-shaped fixing members 110, 110 and a mass member 120 having an inner peripheral surface larger than the outer peripheral surface of the rotating shaft S and inserted through the rotating shaft S.
And a pair of hollow frustoconical elastic members 130, 130 that connect the respective fixing members 110, 110 with the respective ends of the mass member 120 are integrally formed. Further, the pair of fixing members 110, 110 of the dynamic damper 100 are formed with locking grooves 110a, 110a that go around the outer peripheral surface thereof, and the locking grooves 110a, 110a are made of a fixing band made of stainless steel or the like. 110
b and 110b are wound and the dynamic damper 100 is attached to the rotation axis S
Fixed to. The elastic member 130 of the dynamic damper 100 supports the mass member 120 in the shearing direction.
［考案が解決しようとする課題］ 従来のダイナミックダンパ600では、固定部材601、弾性
部材603、質量部材602が積層しているため、外径が大き
くなる傾向がある。また、ダイナミックダンパ600の固
有振動数を低く設定する必要がある場合には、弾性部材
603のばね定数を小さくするか、あるいは質量部材602の
質量を大きくする必要がある。しかし、弾性部材603の
ばね定数を小さくするためには、弾性部材603の形状を
振動方向に長くする必要があり、そのことはダイナミッ
クダンパ600の外径を大きくしなければならないことを
意味する。また、質量部材602の質量を大きくするため
には、質量部材602を大きくする必要があり、この場合
もダイナミックダンパ600の外径が大きくなることは避
けられなかった。このように、従来のダイナミックダン
パ600においては、性能を維持しつつ小型化することは
困難であった。[Problems to be Solved by the Invention] In the conventional dynamic damper 600, since the fixing member 601, the elastic member 603, and the mass member 602 are laminated, the outer diameter tends to increase. In addition, if it is necessary to set the natural frequency of the dynamic damper 600 to a low value, the elastic member
It is necessary to reduce the spring constant of 603 or increase the mass of the mass member 602. However, in order to reduce the spring constant of the elastic member 603, the shape of the elastic member 603 needs to be elongated in the vibration direction, which means that the outer diameter of the dynamic damper 600 must be increased. Further, in order to increase the mass of the mass member 602, it is necessary to increase the mass member 602, and in this case as well, it is unavoidable that the outer diameter of the dynamic damper 600 increases. As described above, in the conventional dynamic damper 600, it is difficult to reduce the size while maintaining the performance.
本考案の考案者が特願昭63−213289号にて提案したダイ
ナミックダンパ100は、従来のダイナミックダンパ600の
上記した問題点を解決したものであるが、両端部に配設
された一対の固定部110、110に固定用バンド110b、110b
を巻装して回転軸Ｓに固定しなければならないので、組
付け作業性にやや難があった。The dynamic damper 100 proposed by the inventor of the present invention in Japanese Patent Application No. 63-213289 solves the above-described problems of the conventional dynamic damper 600. Bands 110b and 110b for fixing to the parts 110 and 110
Since it has to be wound around and fixed to the rotating shaft S, the workability of assembling is somewhat difficult.
したがって、本考案はダイナミックダンパの一端側のみ
を固定するだけでダイナミックダンパの回転軸への取付
けが完了するようなダイナミックダンパを提供し、組付
け作業性の向上と原価低減を図ることを目的とする。Therefore, the present invention aims to provide a dynamic damper in which the dynamic damper can be mounted on the rotary shaft by fixing only one end of the dynamic damper to improve the assembling workability and reduce the cost. To do.
［課題を解決するための手段］ 本考案のダイナミックダンパは、回転軸の外周面より大
きい内周面をもち該回転軸に挿通される筒状の質量部材
と、 該回転軸に挿通支持されるリング状の第１固定部と該第
１固定部と前記質量部材の一端とを一体的に連結する第
１弾性部とからなる第１弾性部材と、 該回転軸に挿通支持されるリング状の第２固定部と該第
２固定部と前記質量部材の他端とを一体的に連結する第
２弾性部とからなる第２弾性部材とを有するダイナミッ
クダンパにおいて、 前記第１弾性部材の前記第１固定部はその外周面を一周
するリング状係止溝をもつとともに該第１固定部の内径
は、前記第２弾性部材の前記第２固定部の内径よりも大
きいことを特徴とする。[Means for Solving the Problems] A dynamic damper of the present invention has a cylindrical mass member having an inner peripheral surface larger than the outer peripheral surface of a rotary shaft and inserted through the rotary shaft, and is supported by being inserted through the rotary shaft. A first elastic member including a ring-shaped first fixing portion and a first elastic portion integrally connecting the first fixing portion and one end of the mass member, and a ring-shaped member inserted and supported by the rotation shaft. A dynamic damper having a second fixing member and a second elastic member including a second elastic member that integrally connects the second fixing member and the other end of the mass member, wherein The first fixing portion has a ring-shaped locking groove that goes around the outer peripheral surface of the first fixing portion, and the inner diameter of the first fixing portion is larger than the inner diameter of the second fixing portion of the second elastic member.
［作用および効果］ 本考案のダイナミックダンパにおいては、第１弾性部材
の第１固定部の内径は第２弾性部材の第２固定部の内径
よりも大きく形成されており、さらに第１弾性部材の第
１固定部の外周面のみにその外周面を一周するリング状
係止溝が形成されている。[Operation and Effect] In the dynamic damper of the present invention, the inner diameter of the first fixing portion of the first elastic member is larger than the inner diameter of the second fixing portion of the second elastic member. A ring-shaped locking groove is formed only on the outer peripheral surface of the first fixing portion so as to go around the outer peripheral surface.
かかる構成をダイナミックダンパに採用することによっ
て、第１弾性部材の第１固定部を回転軸に固定する際の
締め代を、第２弾性部の第２固定部を回転軸に固定する
際の締め代よりも小さく設定することができる。する
と、ダイナミックダンパの第１弾性部材の第１固定部が
回転軸に係合する度合いと第２弾性部材の第２固定部が
回転軸に係合する度合いを同一にすることができ、両端
の係合の度合いの不均衡をなくすことができる。したが
って、第１弾性部の第１固定部のみを固定用バンドによ
って回転軸に固定した場合であっても、第１弾性部材の
第１弾性部と第２弾性部材の第２弾性部に生じる剪断ば
ね定数が一致する。このようにして、回転軸に励起され
る有害振動の卓越振動数に合わせたダイナミックダンパ
の固有振動数以外には共振が発生することがなくなる。By adopting such a configuration in the dynamic damper, the tightening margin when fixing the first fixing portion of the first elastic member to the rotation shaft is tightened when fixing the second fixing portion of the second elastic portion to the rotation shaft. It can be set smaller than the bill. Then, the degree of engagement of the first fixing portion of the first elastic member of the dynamic damper with the rotation shaft and the degree of engagement of the second fixing portion of the second elastic member with the rotation shaft can be made equal to each other. An imbalance in the degree of engagement can be eliminated. Therefore, even when only the first fixing portion of the first elastic portion is fixed to the rotating shaft by the fixing band, the shear generated in the first elastic portion of the first elastic member and the second elastic portion of the second elastic member. The spring constants match. In this way, resonance does not occur at frequencies other than the natural frequency of the dynamic damper that matches the predominant frequency of the harmful vibration excited on the rotation axis.
上記したように本考案のダイナミックダンパは、回転軸
へのダイナミックダンパの取付けがその一端側のみを回
転軸に固定するだけで完了するようになるので、組付け
に要する部品点数と工数が減少する。したがって、組付
け作業性は向上し、原価低減も図れる。As described above, in the dynamic damper of the present invention, the mounting of the dynamic damper on the rotary shaft can be completed by fixing only one end of the dynamic damper to the rotary shaft, so that the number of parts and man-hours required for assembly are reduced. . Therefore, the assembling workability is improved and the cost can be reduced.
［実施例］ 以下、本考案のダイナミックダンパの一実施例につき、
第１図と第２図を参照しながら説明する。[Embodiment] An embodiment of the dynamic damper of the present invention will be described below.
A description will be given with reference to FIGS. 1 and 2.
第１図は本実施例のダイナミックダンパをその中心軸に
沿って切断した断面図であり、第２図は本実施例のダイ
ナミックダンパを回転軸へ取付けた状態を示す断面図で
ある。FIG. 1 is a cross-sectional view of the dynamic damper of this embodiment cut along the central axis thereof, and FIG. 2 is a cross-sectional view showing a state in which the dynamic damper of this embodiment is attached to a rotary shaft.
本実施例のダイナミックダンパ１は、筒状の質量部材10
と、質量部材10と一体的に形成された第１弾性部材11
と、質量部材10と一体的に形成された第２弾性部材12と
を有する。このダイナミックダンパ１は、一体的に形成
され、全体として、その中央部分の外径がその両端部分
より大きい外径をもつ円筒形状をしている。The dynamic damper 1 of the present embodiment has a cylindrical mass member 10
And the first elastic member 11 formed integrally with the mass member 10.
And a second elastic member 12 formed integrally with the mass member 10. The dynamic damper 1 is integrally formed and has a cylindrical shape as a whole, the outer diameter of the central portion of which is larger than that of both end portions thereof.
質量部材10は、回転軸Ｓの外周面より大きい内周面をも
ち、回転軸Ｓに挿通されるものである。この質量部材10
は、筒状の厚肉鋼管などの金属製質量体からなり、ダイ
ナミックダンパ１を金型によって加硫成形する際に、弾
性部材11、12を構成する天然ゴムなどのゴム材料で外周
面、内周面とも1mm程度の厚みでコーティングされてい
る。このゴムコーティングされた筒状の金属製質量体が
回転軸Ｓの外周に配設され、これが一体的に質量部材10
として機能する。この質量部材10の内周面と回転軸Ｓの
外周面との間には、約1.5mmの間隙が形成されている。The mass member 10 has an inner peripheral surface larger than the outer peripheral surface of the rotating shaft S and is inserted into the rotating shaft S. This mass member 10
Is made of a metal mass body such as a tubular thick-walled steel pipe, and when the dynamic damper 1 is vulcanized and molded by a die, the outer peripheral surface and the inner surface are made of a rubber material such as natural rubber that constitutes the elastic members 11 and 12. The circumference is coated with a thickness of about 1 mm. This rubber-coated tubular metal mass body is arranged on the outer periphery of the rotary shaft S, and this is integrally formed with the mass member 10.
Function as. A gap of about 1.5 mm is formed between the inner peripheral surface of the mass member 10 and the outer peripheral surface of the rotary shaft S.
第１弾性部材11は、リング状の第１固定部15と、中空円
錐台状の第１弾性部13とからなり、天然ゴムなどのゴム
材料で形成されている。この第１固定部15が回転軸Ｓに
挿通支持される。The first elastic member 11 includes a ring-shaped first fixing portion 15 and a hollow truncated cone-shaped first elastic portion 13, and is made of a rubber material such as natural rubber. The first fixing portion 15 is inserted into and supported by the rotating shaft S.
リング状の第１固定部15の内径（φＡ）は、以下の述べ
る第２弾性部材12の第２固定部16の内径（φＢ）よりも
次のように大きく形成されている。すなわち、回転軸の
外径をφＣとしたとき、第１弾性部材11の第１固定部15
の内径（φＡ）は、φＡ＝φＣ−（0.5〜1.0）mmに、第
２固定部16の内径（φＢ）は、φＢ＝φＣ−（1.2〜2.
5）mmのようにφＡ＞φＢに形成されている。なお、第
１弾性部材11の第１固定部15の内径（φＡ）を、回転軸
の外径（φＣ）の大きさの94〜99％の範囲に設定し、第
２弾性部材12の第２固定部16の内径（φＢ）を、回転軸
の外径（φＣ）の大きさの87〜96％の範囲に設定し、か
つφＡ＞φＢに設定するのが好ましい。The inner diameter (φA) of the ring-shaped first fixing portion 15 is formed larger than the inner diameter (φB) of the second fixing portion 16 of the second elastic member 12 described below. That is, when the outer diameter of the rotating shaft is φC, the first fixing portion 15 of the first elastic member 11 is
The inner diameter (φA) is φA = φC- (0.5 to 1.0) mm, and the inner diameter (φB) of the second fixing portion 16 is φB = φC- (1.2 to 2.
5) It is formed such that φA> φB as in mm. The inner diameter (φA) of the first fixing portion 15 of the first elastic member 11 is set within a range of 94 to 99% of the size of the outer diameter (φC) of the rotating shaft, and the second elastic member 12 It is preferable that the inner diameter (φB) of the fixed portion 16 is set within a range of 87 to 96% of the outer diameter (φC) of the rotary shaft, and φA> φB.
このように第１弾性部材11の第１固定部15を回転軸Ｓに
固定する際の締め代は、第２弾性部材12の第２固定部16
を回転軸Ｓに固定する際のそれよりも小さく設定されて
いる。さらに、第１固定部15の外周面には、その外周面
を一周するリング状の係止溝15aが形成されている。As described above, the tightening margin when fixing the first fixing portion 15 of the first elastic member 11 to the rotation shaft S is the second fixing portion 16 of the second elastic member 12.
Is set to be smaller than that when fixing to the rotation axis S. Further, the outer peripheral surface of the first fixing portion 15 is formed with a ring-shaped locking groove 15a that goes around the outer peripheral surface.
中空円錐台状の第１弾性部13は、第１弾性部材11の第１
固定部15と質量部材10の一端とを以下に述べるように一
体的に連結している。すなわち、第１弾性部13の内周面
13aは、回転軸Ｓに密着する第１固定部15の内周面端部
から内径を少しづつ大きくしながら、質量部材10の内周
面の端部へとテーパ状に形成され、また第１弾性部13の
外周面13bは、第１固定部15の外周面端部から外径を少
しづつ大きくしながら、質量部材10の外周面の端部へと
テーパ状に形成されている。The first elastic portion 13 having a hollow truncated cone shape is the first elastic member 11 of the first elastic member 11.
The fixed portion 15 and one end of the mass member 10 are integrally connected as described below. That is, the inner peripheral surface of the first elastic portion 13
13a is formed in a taper shape toward the end of the inner peripheral surface of the mass member 10 while gradually increasing the inner diameter from the end of the inner peripheral surface of the first fixing portion 15 which is in close contact with the rotation axis S. The outer peripheral surface 13b of the elastic portion 13 is formed in a tapered shape toward the end portion of the outer peripheral surface of the mass member 10 while gradually increasing the outer diameter from the outer peripheral surface end portion of the first fixing portion 15.
第２弾性部材12は、リング状の第１固定部16と、中空円
錐台状の第２弾性部14とからなり、天然ゴムなどのゴム
材料で形成されている。この第２固定部16が回転軸Ｓに
挿通支持される。The second elastic member 12 includes a ring-shaped first fixing portion 16 and a hollow truncated cone-shaped second elastic portion 14, and is made of a rubber material such as natural rubber. The second fixed portion 16 is inserted into and supported by the rotating shaft S.
リング状の第２固定部16の内径（φＢ）は、上記したよ
うに、第１弾性部材11の第１固定部15の内径（φＡ）よ
りも小さく形成されている。すなわち、第２弾性部材12
の第２固定部16を回転軸Ｓに固定する際の締め代は、第
１弾性部材11の第１固定部15を回転軸Ｓに固定する際の
それよりも大きく設定されている。The inner diameter (φB) of the ring-shaped second fixing portion 16 is smaller than the inner diameter (φA) of the first fixing portion 15 of the first elastic member 11, as described above. That is, the second elastic member 12
The tightening margin when fixing the second fixing portion 16 to the rotating shaft S is set to be larger than that when fixing the first fixing portion 15 of the first elastic member 11 to the rotating shaft S.
中空円錐台状の第２弾性部14は、第２弾性部材12の第２
固定部16と質量部材10の一端とを以下に述べるように一
体的に連結している。すなわち、第２弾性部14の内周面
14aは、回転軸Ｓに密着する第２固定部16の内周面端部
から内径を少しづつ大きくしながら、質量部材10の内周
面の端部へとテーパ状に形成され、また第２弾性部14の
外周面14bは、第２固定部16の外周面端部から外径を少
しづつ大きくしながら、質量部材10の外周面の端部へと
テーパ状に形成されている。The second elastic portion 14 in the shape of a hollow truncated cone is the second elastic member of the second elastic member 12.
The fixed portion 16 and one end of the mass member 10 are integrally connected as described below. That is, the inner peripheral surface of the second elastic portion 14
14a is formed in a taper shape toward the end of the inner peripheral surface of the mass member 10 while gradually increasing the inner diameter from the end of the inner peripheral surface of the second fixing portion 16 that is in close contact with the rotation axis S. The outer peripheral surface 14b of the elastic portion 14 is formed in a tapered shape toward the end of the outer peripheral surface of the mass member 10 while gradually increasing the outer diameter from the outer peripheral surface end of the second fixing portion 16.
上記のように構成したダイナミックダンパ１を、以下に
詳述するように回転軸Ｓに取付けて使用する。すなわ
ち、回転軸Ｓを自動車本体に取付ける前に、ダイナミッ
クダンパ１の第１弾性部材11の第１固定部15の内周面を
面転軸Ｓの軸端に合せる。第１弾性部材11の第１固定部
15の内径は、回転軸Ｓの外径よりも0.5〜1.0mm程度小さ
く形成されているため、回転軸Ｓは第１固定部15の内周
面を押し広げて、ダイナミックダンパ１内に圧入され
る。回転軸Ｓをダイナミックダンパ１内にさらに挿通す
ると、第２弾性部材12の第２固定部16の中心軸孔の内径
は、回転軸Ｓの外径よりも1.2〜2.5mm程度小さく形成さ
れているため、回転軸Ｓは第１固定部15の内周面を押し
広げるよりも、さらに一層、第２固定部16の内周面を押
し広げて、ダイナミックダンパ１内に圧入される。この
ようにして、回転軸Ｓの所定の位置にダイナミックダン
パ１を配置した後、第１弾性部材11の第１固定部15の外
周面に形成されている係止溝15aに固定用バンド15bを巻
装して、ダイナミックダンパ１を回転軸Ｓに固定する。The dynamic damper 1 configured as described above is used by being attached to the rotary shaft S as described in detail below. That is, before attaching the rotary shaft S to the automobile body, the inner peripheral surface of the first fixing portion 15 of the first elastic member 11 of the dynamic damper 1 is aligned with the axial end of the surface rolling shaft S. First fixing portion of the first elastic member 11
The inner diameter of 15 is smaller than the outer diameter of the rotating shaft S by about 0.5 to 1.0 mm. Therefore, the rotating shaft S pushes the inner peripheral surface of the first fixing portion 15 and press-fits it into the dynamic damper 1. It When the rotary shaft S is further inserted into the dynamic damper 1, the inner diameter of the central shaft hole of the second fixing portion 16 of the second elastic member 12 is smaller than the outer diameter of the rotary shaft S by about 1.2 to 2.5 mm. Therefore, the rotary shaft S further presses the inner peripheral surface of the second fixing portion 16 further than the inner peripheral surface of the first fixing portion 15 and presses it into the dynamic damper 1. After disposing the dynamic damper 1 at a predetermined position on the rotating shaft S in this manner, the fixing band 15b is attached to the locking groove 15a formed on the outer peripheral surface of the first fixing portion 15 of the first elastic member 11. The dynamic damper 1 is fixed to the rotary shaft S by winding.
第２図に上記のようにダイナミックダンパ１を回転軸Ｓ
に取付けた状態の断面図を示す。この状態において、ダ
イナミックダンパ１の第１弾性部材11の第１固定部15
は、固定用バンド15bによってその中心軸方向に強固に
押圧されている。したがって、第１弾性部材11の第１固
定部15の係止溝15aに固定用バンド15bを巻装することに
よって、第１弾性部材11の第１固定部15を回転軸Ｓに固
定する力と、第２弾性部材12の第２固定部16を回転軸Ｓ
に固定する力がほぼ同程度となって、第１弾性部材11の
第１固定部15および第２弾性部材12の第２固定部16とも
回転軸Ｓに密着している。なお、このように第１固定部
15と第２固定部16を回転軸Ｓに固定する力をほぼ同程度
にして、第１固定部15と第２固定部16を回転軸Ｓに密着
させることができるのは、上記したように第１固定部15
の内径を第２固定部16の内径よりも大きく形成したこと
によるものである。As shown in FIG. 2, the dynamic damper 1 is attached to the rotary shaft S as described above.
FIG. In this state, the first fixing portion 15 of the first elastic member 11 of the dynamic damper 1
Is firmly pressed in the central axis direction by the fixing band 15b. Therefore, by winding the fixing band 15b around the locking groove 15a of the first fixing portion 15 of the first elastic member 11, a force for fixing the first fixing portion 15 of the first elastic member 11 to the rotating shaft S is obtained. , The second fixing portion 16 of the second elastic member 12 to the rotation axis S
The force for fixing the first elastic member 11 to the first elastic member 11 and the second fixed member 16 of the second elastic member 12 are in close contact with the rotation shaft S. In addition, as described above, the first fixing portion
As described above, it is possible to bring the first fixing portion 15 and the second fixing portion 16 into close contact with the rotating shaft S by making the forces for fixing the 15 and the second fixing portion 16 to the rotating shaft S substantially equal to each other. First fixed part 15
This is because the inner diameter of the second fixing portion 16 is larger than the inner diameter of the second fixing portion 16.
回転軸Ｓが回転し、有害な振動が励起されると、その有
害振動の振動数に固有振動数を合せたダイナミックダン
パ１の質量部材10が共振する。この固有振動数の調整は
第１弾性部材11の第１弾性部13および第２弾性部材12の
第２弾性部14の形状が変化することによって行われる。
ここで、固定用バンド15bによって第１弾性部材11の第
１固定部15のみが固定されているが、第１弾性部材11の
第１固定部15の回転軸Ｓに対する係合の度合いと、第２
弾性部材12の第２固定部16の回転軸Ｓに対する係合の度
合いは上記したように同程度であるので、回転軸Ｓが回
転中に、第１弾性部材11の第１弾性部13の変形が第２弾
性部材12の第２弾性部14のそれと相違するということが
ない。したがって、第１弾性部材11の第１弾性部13と第
２弾性部材12の第２弾性部14に生じる剪断ばね定数が相
違することがないので、回転軸Ｓに励起される有害振動
の卓越振動数に合わせたダイナミックダンパ１の固有振
動数以外には共振が発生することもない。When the rotating shaft S rotates and harmful vibration is excited, the mass member 10 of the dynamic damper 1 in which the natural frequency is matched with the frequency of the harmful vibration resonates. The adjustment of the natural frequency is performed by changing the shapes of the first elastic portion 13 of the first elastic member 11 and the second elastic portion 14 of the second elastic member 12.
Here, although only the first fixing portion 15 of the first elastic member 11 is fixed by the fixing band 15b, the degree of engagement of the first fixing portion 15 of the first elastic member 11 with the rotation axis S, and Two
Since the degree of engagement of the second fixing portion 16 of the elastic member 12 with the rotation shaft S is substantially the same as described above, the deformation of the first elastic portion 13 of the first elastic member 11 while the rotation shaft S is rotating. Does not differ from that of the second elastic portion 14 of the second elastic member 12. Therefore, since the shear spring constants generated in the first elastic portion 13 of the first elastic member 11 and the second elastic portion 14 of the second elastic member 12 do not differ, the predominant vibration of the harmful vibration excited on the rotation axis S Resonance does not occur other than the natural frequency of the dynamic damper 1 according to the number.
このように、本実施例のダイナミックダンパ１はその本
来の性能を損なわずに、その第１弾性部材11の第１固定
部15のみに固定用バンド15bを巻装するだけで回転軸Ｓ
に固定できるので、部品点数と組付けに要する工数が減
少する。したがって、上記したような構成の本実施例の
ダイナミックダンパ１を採用することによって、その組
付け作業性は向上し、原価低減も図れる。As described above, the dynamic damper 1 of the present embodiment does not impair its original performance, and only by winding the fixing band 15b around the first fixing portion 15 of the first elastic member 11, the rotary shaft S can be wound.
Since it can be fixed to, the number of parts and man-hours required for assembly are reduced. Therefore, by adopting the dynamic damper 1 of the present embodiment having the above-mentioned structure, the assembling workability is improved and the cost can be reduced.
第１図は本考案の一実施例であるダイナミックダンパを
その中心軸に沿って切断した断面図である。第２図は本
考案の一実施例であるダイナミックダンパを回転軸へ取
付けた状態を示す断面図である。第３図は本考案の考案
者が特願昭63−213289号にて提案したダイナミックダン
パをその中心軸に沿って切断した断面図である。第４図
は従来のダイナミックダンパの概略断面図である。 １…ダイナミックダンパ 10…質量部材 11、12…第１および第２弾性部材 13、14…第１および第２弾性部 15、16…第１および第２固定部 15a…係止溝、15b…固定用バンド Ｓ…回転軸FIG. 1 is a sectional view of a dynamic damper, which is an embodiment of the present invention, taken along the central axis thereof. FIG. 2 is a sectional view showing a state in which a dynamic damper according to an embodiment of the present invention is attached to a rotary shaft. FIG. 3 is a cross-sectional view of the dynamic damper proposed by the inventor of the present invention in Japanese Patent Application No. 63-213289, taken along the central axis thereof. FIG. 4 is a schematic sectional view of a conventional dynamic damper. DESCRIPTION OF SYMBOLS 1 ... Dynamic damper 10 ... Mass member 11, 12 ... 1st and 2nd elastic member 13, 14 ... 1st and 2nd elastic part 15, 16 ... 1st and 2nd fixed part 15a ... Locking groove, 15b ... Fixed Band S ... Rotating shaft
Claims (1)
回転軸に挿通される筒状の質量部材と、 該回転軸に挿通支持されるリング状の第１固定部と該第
１固定部と前記質量部材の一端とを一体的に連結する第
１弾性部とからなる第１弾性部材と、 該回転軸に挿通支持されるリング状の第２固定部と該第
２固定部と前記質量部材の他端とを一体的に連結する第
２弾性部とからなる第２弾性部材とを有するダイナミッ
クダンパにおいて、 前記第１弾性部材の前記第１固定部はその外周面を一周
するリング状係止溝をもつとともに該第１固定部の内径
は、前記第２弾性部材の前記第２固定部の内径よりも大
きいことを特徴とするダイナミックダンパ。1. A cylindrical mass member having an inner peripheral surface larger than an outer peripheral surface of a rotating shaft and inserted through the rotating shaft, a ring-shaped first fixing portion inserted through and supported by the rotating shaft, and the first mass member. A first elastic member including a fixed portion and a first elastic portion that integrally connects one end of the mass member, a ring-shaped second fixed portion that is inserted and supported by the rotating shaft, and the second fixed portion. In a dynamic damper having a second elastic member including a second elastic portion integrally connecting the other end of the mass member, the first fixing portion of the first elastic member has a ring that makes a round around the outer peripheral surface thereof. A dynamic damper having a locking groove and an inner diameter of the first fixing portion is larger than an inner diameter of the second fixing portion of the second elastic member.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8550689U JPH0645078Y2 (en) | 1989-07-20 | 1989-07-20 | Dynamic damper |
| EP90113774A EP0409202B1 (en) | 1989-07-20 | 1990-07-18 | Dynamic damper |
| DE69017292T DE69017292T2 (en) | 1989-07-20 | 1990-07-18 | Dynamic damper. |
| US07/554,894 US5090668A (en) | 1989-07-20 | 1990-07-20 | Dynamic damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8550689U JPH0645078Y2 (en) | 1989-07-20 | 1989-07-20 | Dynamic damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0325048U JPH0325048U (en) | 1991-03-14 |
| JPH0645078Y2 true JPH0645078Y2 (en) | 1994-11-16 |
Family
ID=31634678
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8550689U Expired - Lifetime JPH0645078Y2 (en) | 1989-07-20 | 1989-07-20 | Dynamic damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0645078Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014002156A (en) * | 2008-07-30 | 2014-01-09 | Horiba Instruments Inc | Rotary test system |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4171219B2 (en) * | 2001-02-19 | 2008-10-22 | 東海ゴム工業株式会社 | Vibration control device |
| US7946925B2 (en) * | 2005-09-21 | 2011-05-24 | Honda Motor Co., Ltd. | Dynamic damper |
| DE102009038849B4 (en) * | 2009-08-26 | 2011-07-21 | Horiba Europe GmbH, 64293 | Test bench with vibration absorber |
-
1989
- 1989-07-20 JP JP8550689U patent/JPH0645078Y2/en not_active Expired - Lifetime
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2014002156A (en) * | 2008-07-30 | 2014-01-09 | Horiba Instruments Inc | Rotary test system |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0325048U (en) | 1991-03-14 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |