JPH03121331A - Dynamic damper - Google Patents
Dynamic damperInfo
- Publication number
- JPH03121331A JPH03121331A JP25909489A JP25909489A JPH03121331A JP H03121331 A JPH03121331 A JP H03121331A JP 25909489 A JP25909489 A JP 25909489A JP 25909489 A JP25909489 A JP 25909489A JP H03121331 A JPH03121331 A JP H03121331A
- Authority
- JP
- Japan
- Prior art keywords
- elastic member
- cylindrical body
- spring constant
- elastic
- 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.)
- Pending
Links
- 238000005452 bending Methods 0.000 abstract description 23
- 230000002093 peripheral effect Effects 0.000 abstract description 6
- 230000000694 effects Effects 0.000 description 5
- 230000033001 locomotion Effects 0.000 description 4
- 239000002184 metal Substances 0.000 description 4
- 238000013016 damping Methods 0.000 description 3
- 230000009977 dual effect Effects 0.000 description 3
- 230000009931 harmful effect Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 239000000463 material Substances 0.000 description 2
- 239000004033 plastic Substances 0.000 description 2
- 230000002238 attenuated effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000003384 imaging method Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000000465 moulding Methods 0.000 description 1
- 238000010008 shearing Methods 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Landscapes
- Motor Power Transmission Devices (AREA)
Abstract
Description
【発明の詳細な説明】
［産業上の利用分野］
本発明は、自動車のドライブシャフト、プロペラシャフ
トなどの回転軸に保持され、その回転軸の共振やパワー
プラントの共振等に伴って発生する有害撮動を減衰させ
るダイナミックダンパに関し、より詳しくは曲げ振動及
び捩り振動に対して有効に振動減衰効果を発揮するデュ
アルタイプのダイナミックダンパに関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention is applied to a rotating shaft such as a drive shaft or a propeller shaft of an automobile, and is designed to reduce harmful effects caused by resonance of the rotating shaft, resonance of a power plant, etc. The present invention relates to a dynamic damper that dampens imaging, and more particularly to a dual-type dynamic damper that effectively exhibits a vibration damping effect against bending vibration and torsional vibration.
［従来の技術］
従来から知られている一般のデュアルタイプのダイナミ
ックダンパは、第３図に示すように、回転軸に取付けら
れるボス部１００と、該ボス部１００の径方向外方に位
置する円筒部１０１と、該ボス部１００と該円筒部１０
１とをつなぐ連結部１０２とを有するダンパープーリ１
０３と、該ダンパープーリ１０３の前記円筒部１０１の
径方向外方に所定距離を隔てて同心状に配置された第１
のダンパーマス１０４と、前記ダンパープーリ１０３の
円筒部１０１と該第１のダンパーマス１０４との間に介
装された第１の弾性部材１０５と、前記ダンパープーリ
１０３の円筒部１０１の内側空間内に同心的に配置され
た円筒状の第２のダンパーマス１０６と、該第２のダン
パーマス１０６の軸方向の端部とそれに対向する前記ダ
ンパープーリ１０３の連結部１０２との間に設けられて
、該第２のダンパーマス１０６を該連結部１０２に支持
せしめ、該第２のダンパーマス１０６の径方向の動きに
対して剪断力を発揮する第２の弾性部材’１０７とから
なるものである（特開昭６２−８８８３８号公報〉。[Prior Art] As shown in FIG. 3, a conventionally known general dual-type dynamic damper has a boss portion 100 attached to a rotating shaft, and a boss portion 100 located radially outward from the boss portion 100. The cylindrical part 101, the boss part 100, and the cylindrical part 10
damper pulley 1 having a connecting portion 102 that connects damper pulley 1 with
03, and a first concentrically arranged radially outward of the cylindrical portion 101 of the damper pulley 103 at a predetermined distance.
a first elastic member 105 interposed between the cylindrical portion 101 of the damper pulley 103 and the first damper mass 104; and an inner space of the cylindrical portion 101 of the damper pulley 103. A cylindrical second damper mass 106 disposed concentrically with the second damper mass 106, and a connecting portion 102 of the damper pulley 103 facing the axial end of the second damper mass 106. , a second elastic member '107 that supports the second damper mass 106 on the connecting portion 102 and exerts a shearing force against the movement of the second damper mass 106 in the radial direction. (Unexamined Japanese Patent Publication No. 62-88838).
そして、第１の弾性部材１０５を介して設けられた第１
のダンパーマス１０４が回転軸の捩り振動に対する副振
動系として作用する一方、第２の弾性部材１０７を介し
て設けられた第２のダンパマス１０６が回転軸の曲げ振
動に対する副振動系として作用することにより、回転軸
の捩り振動及び曲げ振動を吸収している。Then, the first elastic member 105 provided through the first elastic member 105
The damper mass 104 acts as a sub-vibration system for torsional vibration of the rotating shaft, while the second damper mass 106 provided via the second elastic member 107 acts as a sub-vibration system for bending vibration of the rotating shaft. This absorbs torsional vibration and bending vibration of the rotating shaft.
また、他の従来のデュアルタイプのダイナミックダンパ
として、第４図に示すように、三角形状の保持フランジ
２００を介して回転軸に保持され、この保持フランジ２
００の径方向外方に同心状に弾性部材２０１を介して円
筒状のダンパーマス２０２が配設されたものがある（特
公昭５８−５２０９１８公報〉。上記弾性部材２０１は
３つの扇形状部分２０３から構成され、該３つの扇形状
部分２０３の幅広い中間部分には大穴２０４が形成され
るとともに、保持フランジ２００の三角形の頂点の所に
周方向両端に円形穴２０５を有するスリット２０６が形
成されている。As another conventional dual type dynamic damper, as shown in FIG.
00, in which a cylindrical damper mass 202 is disposed concentrically via an elastic member 201 (Japanese Patent Publication No. 58-520918). The elastic member 201 has three fan-shaped portions 203. A large hole 204 is formed in the wide middle part of the three sector-shaped parts 203, and a slit 206 having circular holes 205 at both ends in the circumferential direction is formed at the apex of the triangle of the holding flange 200. There is.
そして、回転方向において、扇形状部分２０３は幅広い
中間部分′１なわち大穴２０４が設（プられている所で
ほぼ単純剪断応力を受（ノ、またスリット２０６の範囲
及び円形穴２０５の所ｒｉ断−圧縮応力又は剪断−引張
り応力を受けることににす、回転軸の捩り振動を吸収す
る構造となっている。In the direction of rotation, the fan-shaped portion 203 is subjected to almost simple shear stress in the wide middle portion '1, that is, in the area where the large hole 204 is formed (in the area where the slit 206 is located and in the area where the circular hole 205 is formed). It has a structure that absorbs torsional vibrations of a rotating shaft subjected to shear-compressive stress or shear-tensile stress.
一方、径方向において、個々の扇形状部分２０３が圧縮
及び剪断応力を受けることにより、回転軸の曲げ振動を
吸収する構造となっている。On the other hand, in the radial direction, each fan-shaped portion 203 receives compressive and shear stress, thereby absorbing bending vibrations of the rotating shaft.
［発明が解決しようとする課題］
ところで、一般（４：２自動車の騒音問題としてこもり
音がおり、このこもり音は低速こもり音、中速こもり音
、高速こもり盲に人別できる。このうら中速こもり音は
４０〜８０１−Ｉ Ｚの振動数をもつ駆動系の捩り共振
を原因として発生し、高速こもり音は１００〜１６０Ｈ
ｚの振動数をもつ駆動系の曲げ共振を原因として発生し
ている。したがって、４０〜８０Ｈ２程度の振動数の捩
り振動を減衰可能に調整された捩り方向のばね定数をも
ち、かつ１００〜１６０Ｈ２程度の振動数の曲げ振動を
減衰可能に調整された曲げ方向のばね定数をもつ弾性部
材を介してダンパーマスを配設すれば、上記中速こもり
音及び高速こもり音を防止することができる。[Problem to be solved by the invention] By the way, muffled noise is a common noise problem in 4:2 automobiles, and this muffled sound can be classified into low speed muffled sound, medium speed muffled sound, and high speed muffled sound. High-speed muffled noise is caused by torsional resonance of the drive system with a frequency of 40 to 801-IZ, and high-speed muffled sound has a frequency of 100 to 160 H.
This is caused by bending resonance of the drive system with a frequency of z. Therefore, it has a spring constant in the torsional direction that is adjusted to be able to attenuate torsional vibrations with a frequency of about 40 to 80H2, and a spring constant in the bending direction that is adjusted to be able to dampen bending vibrations that have a frequency of about 100 to 160H2. By arranging the damper mass via an elastic member having the following characteristics, the above-mentioned medium-speed muffled sound and high-speed muffled sound can be prevented.
すなわち、上記特開昭６２−８８８３８号公報に開示さ
れたデュアルタイプのダイナミックダンパで上記捩り及
び曲げの両ｊ辰動を減衰するには、捩り方向つまり周方
向における第１の弾性部材１０５のばね定数は上記捩り
振動を減衰可能な如く大きく設定し、かつ曲げ方向つま
り径方向における第２の弾性部材１０７のばね定数は上
記曲げ振動を減衰可能な如く小さく設定すればよい。That is, in order to damp both the torsional and bending movements in the dual type dynamic damper disclosed in the above-mentioned Japanese Patent Application Laid-Open No. 62-88838, the spring of the first elastic member 105 in the torsional direction, that is, the circumferential direction is The constant may be set large enough to damp the torsional vibration, and the spring constant of the second elastic member 107 in the bending direction, that is, the radial direction, may be set small so as to damp the bending vibration.
ところが、この従来のデュアルタイプのダイナミックダ
ンパは、上述したように、２つのダンパーマス１０４，
１０６を利用して回転軸の捩り振動及び曲げ振動を吸収
するようにしたものである。However, as described above, this conventional dual type dynamic damper has two damper masses 104,
106 to absorb torsional vibration and bending vibration of the rotating shaft.
したがって、それぞれ第１弾性部材１０５及び第２弾性
部材１０７を介して２つのダンパーマス１０４．１０６
を必要とし、その構造が複雑となるため、製造が面倒で
あり、コスト高にもつながる、。Therefore, the two damper masses 104 and 106 are connected via the first elastic member 105 and the second elastic member 107, respectively.
The structure is complicated, which makes manufacturing cumbersome and leads to high costs.
一方、前記特公昭５８−５２０９１号公報に開示された
ダイナミックダンパで上記捩り及び曲げの両共振を減衰
するには、弾性部材２０１のスリット２０６、円形穴２
０５、及び大穴２０４の形状、大きさ等を変えて減衰可
能な振動数域を調節する必要があり、その調節が困難で
あるとともに、複雑な特殊形状の弾性部材２０３の製造
が面倒であり、コスト高にもつながる。On the other hand, in order to damp both the torsional and bending resonances in the dynamic damper disclosed in Japanese Patent Publication No. 58-52091, the slit 206 of the elastic member 201, the circular hole 2
05 and the shape, size, etc. of the large hole 204 to adjust the dampable frequency range, which is difficult to adjust, and it is troublesome to manufacture the elastic member 203 with a complicated special shape. This also leads to higher costs.
本発明は、弾性部材のばね定数を周方向にａ３いて小さ
く、径方向において大きく設定でき、かつ構造が簡単で
製造も容易なデュアルタイプのダイナミックダンパを提
供することを解決づべき技術課題とするものである。A technical problem to be solved by the present invention is to provide a dual-type dynamic damper in which the spring constant of the elastic member can be set to be small in the circumferential direction and large in the radial direction, and which is simple in structure and easy to manufacture. It is something.
［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、回転軸に保持される第
１筒状体と、該第１筒状体の径方向外方に同心状に配設
された第２筒状体と、該第１筒状体と該第２筒状体との
間で、周方向に等間隔に配設された少なくとも３個以上
の弾性部材とからなり、該弾性部材は該第１ＷＩ状体と
該第２筒状休との間に同心状に位置する弧状断面をもつ
中間板と該中間板の両面側に一体的に固定された弾性部
とからなることを特徴とする。[Means for Solving the Problems] The dynamic damper of the present invention includes a first cylindrical body held on a rotating shaft, and a second cylindrical body concentrically disposed radially outward of the first cylindrical body. It consists of a cylindrical body, and at least three elastic members arranged at equal intervals in the circumferential direction between the first cylindrical body and the second cylindrical body, and the elastic members are arranged at equal intervals in the circumferential direction. It is characterized by comprising an intermediate plate having an arcuate cross section located concentrically between the 1WI-shaped body and the second cylindrical body, and elastic parts integrally fixed to both sides of the intermediate plate.
上記弾性部材は、第１筒状体と第２筒状体との間で、周
方向に等間隔に３個以上配設され、その数はとくに限定
されない。また、場合によっては第１筒状体と第２筒状
体との間に全周に亘って形成することもできる。この弾
性部材は、第１筒状体と第２筒状体との間に同心状に位
置づる弧状断面をもつ中間板と、該中間板の両面側に一
体的に固定された弾性部とからなる。上記中間板と上記
弾性部との周方向にあける長さ関係はとくに限定されな
い。例えば、中間板を周方向全周に亘る環状のものとす
ることもできる。また、中間板の材質もとくに限定され
ず、金属、プラスチックス等とすることができる。Three or more of the elastic members are arranged at equal intervals in the circumferential direction between the first cylindrical body and the second cylindrical body, and the number is not particularly limited. Moreover, depending on the case, it can also be formed over the entire circumference between the first cylindrical body and the second cylindrical body. This elastic member includes an intermediate plate having an arcuate cross section located concentrically between the first cylindrical body and the second cylindrical body, and elastic parts integrally fixed to both sides of the intermediate plate. Become. The circumferential length relationship between the intermediate plate and the elastic portion is not particularly limited. For example, the intermediate plate may be annular in the entire circumferential direction. Furthermore, the material of the intermediate plate is not particularly limited, and may be metal, plastic, or the like.
また、上記各弾性部材の周方向の各中間位置にストッパ
一部材を配設することもできる。このストッパ一部材は
、第１筒状体に固定される第１ストッパ一部と第２筒状
体に固定される第２ストッパ一部とから構成することが
できる。そして、上記第１ストッパ一部及び第２ストッ
パ一部は、それぞれの対向面に相互に遊嵌する凹凸面を
有するものとすることができる。ストッパ一部材の材質
はとくに限定されず、ゴム、プラスチックス等とするこ
とができる。Furthermore, a stopper member may be provided at each intermediate position in the circumferential direction of each of the elastic members. This stopper member can be composed of a part of the first stopper fixed to the first cylindrical body and a part of the second stopper fixed to the second cylindrical body. The first part of the first stopper and the second part of the second stopper may have uneven surfaces on their opposing surfaces that fit loosely into each other. The material of the stopper member is not particularly limited, and may be rubber, plastic, or the like.
［作用コ
本発明のダイナミックダンパは、第１筒状体と第２筒状
体との間に、中間板と該中間板の両側に一体的に固定さ
れた弾性部とからなる弾性部材を周方向に等間隔に３個
以上配設したものである。[Operation] The dynamic damper of the present invention includes an elastic member consisting of an intermediate plate and elastic parts integrally fixed on both sides of the intermediate plate between the first cylindrical body and the second cylindrical body. Three or more are arranged at equal intervals in the direction.
すなわち、上記弾性部材は弾性部の間に中間板が介在さ
れた構成を有するため、この中間板の存在により径方向
における弾性部材のばね定数が大きくなっており、しか
も弾性部材の周方向におけるばね定数は弾性品自身のば
ね定数のままに維持されている。これにより、回転軸に
発生する周波数の低めの捩り振動に対しては、弾性部材
が周方向に小さく設定されたばね定数をもつため第２筒
状体が該捩り振動に対する副振動系として効果的に作用
し、回転軸に発生する周波数の高めの曲げ振動に対して
は、弾性部材が径方向に大きく設定されたばね定数をも
つため第２筒状体が該曲げ振動に対する副振動系として
効果的に作用する。That is, since the elastic member has a structure in which an intermediate plate is interposed between the elastic parts, the presence of the intermediate plate increases the spring constant of the elastic member in the radial direction, and the spring constant of the elastic member in the circumferential direction increases. The constant is maintained at the spring constant of the elastic product itself. This allows the second cylindrical body to effectively act as a sub-vibration system for low-frequency torsional vibrations that occur on the rotating shaft because the elastic member has a spring constant that is set small in the circumferential direction. In response to high-frequency bending vibrations generated on the rotating shaft, the second cylindrical body is effective as a sub-vibration system for the bending vibrations because the elastic member has a spring constant that is set large in the radial direction. act.
したがって、本発明のダイナミックダンパは、上記捩り
及び上記曲げの両振動エネルギーを共振作用で第２筒状
体の振動エネルギーに変換して、回転軸に発生する有害
（騒動を減衰させることができる。Therefore, the dynamic damper of the present invention can convert both the torsional and bending vibration energy into the vibration energy of the second cylindrical body through resonance, thereby damping harmful disturbances occurring at the rotating shaft.
［実施例］
以下、本発明を図面を参照しつつ具体的な実施例により
説明する。[Examples] Hereinafter, the present invention will be explained by specific examples with reference to the drawings.
（実施例１）
第１図は本実施例１のダイナミックダンパの横断面図で
ある。本実施例１のダイナミックダンパは、プロペラシ
ャフトに保持される第１筒状体１と、第１筒状体１の径
方向外方に同心状に配８２された第２筒状体２と、第１
筒状体１と第２筒状体２との間で、周方向に等間隔に４
個配設された弾性部材３とからなる。(Example 1) FIG. 1 is a cross-sectional view of a dynamic damper of Example 1. The dynamic damper of the first embodiment includes a first cylindrical body 1 held on a propeller shaft, a second cylindrical body 2 concentrically disposed 82 radially outward of the first cylindrical body 1, 1st
Between the cylindrical body 1 and the second cylindrical body 2, 4
It consists of individually arranged elastic members 3.
第１筒状体１は金属からなり、装着されるプロペラシャ
フトの外径Ｊ：り僅かに小さい内径をもつ。The first cylindrical body 1 is made of metal and has an inner diameter slightly smaller than the outer diameter J of the propeller shaft to which it is attached.
第２筒状休２は金属からなり、本実施例のダイナミック
ダンパのダンパーマスとして作用する。The second cylindrical suspension 2 is made of metal and acts as a damper mass of the dynamic damper of this embodiment.
弾性部材３は、第１筒状体１と第２筒状体２との間に同
心状に位置する弧状断面をもつ金属製中間板３１と、中
間板３１の両面側に一体的に固定されたゴム弾性部３２
．３２とからなる。The elastic member 3 is integrally fixed to a metal intermediate plate 31 having an arcuate cross section and located concentrically between the first cylindrical body 1 and the second cylindrical body 2, and to both sides of the intermediate plate 31. rubber elastic part 32
．． It consists of 32.
本実施例１のダイナミックダンパは、第１筒状体１、第
２筒状休２、中間板３１を同心状に配置した状態で、ゴ
ム弾性体を第１筒状体１と中間を反３１との間及び第２
筒状体２と中間板３１との間にそれぞれ成形加硫してこ
れらを加硫接着することにより製造することができる。In the dynamic damper of the first embodiment, the first cylindrical body 1, the second cylindrical rest 2, and the intermediate plate 31 are arranged concentrically, and the rubber elastic body is disposed between the first cylindrical body 1 and the intermediate part at an angle 31. and the second
It can be manufactured by molding and vulcanizing the cylindrical body 2 and the intermediate plate 31, respectively, and vulcanizing and adhering them.
本実施例１のダイナミックダンパはプロペラシャフトに
圧入により嵌合固定されて使用される。The dynamic damper of the first embodiment is used by being press-fitted and fixed to the propeller shaft.
このダイナミックダンパは、弾性部材３が弾性部３２．
３２の間に中間板３１が介在された構成を有するため、
この中間板３１の存在により径方向における弾性部材３
のばね定数が大きくなっており、しかも弾性部材３の周
方向におけるばね定数は弾性部３２自身のばね定数のま
まに維持されている。これにより、プロペラシャフトに
発生する周波数の低めの捩り振動に対しては、弾性部材
３が周方向に小さく設定されたばね定数をもつため第２
筒状体２が該捩り振動に対する副振動系として効果的に
作用し、プロペラシャフトに発生する周波数の高めの曲
げ撮動に対しては、弾性部材３が径方向に大きく設定さ
れたばね定数をもつため第２筒状体２が該曲げ撮動に対
する副振動系として効果的に作用する。In this dynamic damper, the elastic member 3 has an elastic section 32.
Since it has a configuration in which an intermediate plate 31 is interposed between 32,
Due to the presence of this intermediate plate 31, the elastic member 3 in the radial direction
The spring constant of the elastic member 3 is increased, and the spring constant of the elastic member 3 in the circumferential direction is maintained as the spring constant of the elastic part 32 itself. As a result, the elastic member 3 has a spring constant that is set small in the circumferential direction, so that the second
The cylindrical body 2 effectively acts as a sub-vibration system for the torsional vibration, and the elastic member 3 has a spring constant set large in the radial direction for high-frequency bending motion occurring in the propeller shaft. Therefore, the second cylindrical body 2 effectively acts as an auxiliary vibration system for the bending motion.
したがって、本実施例１のダイナミックダンパは、上記
捩り及び上記曲げの両娠勅エネルギーを共振作用で第２
筒状体２の振動エネルギーに変換して、プロペラシャフ
トに発生する有害振動を減衰させることができる。Therefore, the dynamic damper of the first embodiment absorbs both the torsional energy and the bending energy by the resonance effect into a second
Harmful vibrations generated in the propeller shaft can be attenuated by converting the vibration energy of the cylindrical body 2 into vibration energy.
（実施例２）
本実施例２のダイナミックダンパは、プロペラシャフト
とミッションとのジヨイント部に保持される第１筒状体
１１と、第１筒状体１１の径方向外方に同心状に配設さ
れた第２筒状体２と、第１筒状体１１と第２筒状体２と
の間で、周方向に等間隔に３個配設された弾性部材３と
、各弾性部材３の周方向の各中間位置に配設された３個
のストッパ一部材４とからなる。(Example 2) The dynamic damper of Example 2 includes a first cylindrical body 11 held at a joint between a propeller shaft and a transmission, and a first cylindrical body 11 arranged concentrically outside the first cylindrical body 11 in the radial direction. Between the first cylindrical body 11 and the second cylindrical body 2, there are three elastic members 3 disposed at equal intervals in the circumferential direction, and each elastic member 3. It consists of three stopper members 4 disposed at respective intermediate positions in the circumferential direction.
第１筒状体１１は、軸方向端部から一体的に径方向内方
に延びる環状の取付は部１１１を有する。The first cylindrical body 11 has an annular attachment portion 111 that integrally extends radially inward from the axial end.
この取付は部１１１には、第１筒状体１１を上記ジヨイ
ント部にボルト固定させるために、周方向に等間隔に４
個のボルト穴１１２が形成されている。In this installation, in order to bolt the first cylindrical body 11 to the joint part, there are four bolts arranged at equal intervals in the circumferential direction in the part 111.
bolt holes 112 are formed.
第２筒状体２及び弾性部材３は、前記実施例１のものと
同様であるため説明を省略する。The second cylindrical body 2 and the elastic member 3 are the same as those in the first embodiment, so their explanation will be omitted.
ストッパ一部材４はゴム製で、第１筒状体１の外周面に
固定される第１ストッパ一部４１と第２筒状体２の内周
面に固定される第２ストッパ一部４２とからなる。この
第１ストッパ一部４１の外周面には凸部４１１が形成さ
れ、第２ストッパー部４２の内周面には上記凸部４１１
と遊ｉＨする凹部４２１が形成されている。なお、スト
ッパ一部材４の形状は、第１筒状体１１と第２筒状体２
との間の過度の回転を規制することができるものでおれ
ばとくに限定されない。例えば、第１ストッパ一部を棒
状のものとし、第２ストッパ一部の内周面にこの棒状の
第１ストッパ一部と遊嵌する凹部を形成してもよい。ま
た、上記第１ストッパー部４１の形状と上記第２ストッ
パ一部４２の形状を逆にすることもできる。The stopper member 4 is made of rubber and includes a first stopper part 41 fixed to the outer peripheral surface of the first cylindrical body 1 and a second stopper part 42 fixed to the inner peripheral surface of the second cylindrical body 2. Consisting of A convex portion 411 is formed on the outer peripheral surface of the first stopper portion 41, and a convex portion 411 is formed on the inner peripheral surface of the second stopper portion 42.
A recessed portion 421 is formed that has a free space. The shape of the stopper member 4 is the same as that of the first cylindrical body 11 and the second cylindrical body 2.
There is no particular limitation as long as it can restrict excessive rotation between the two. For example, a portion of the first stopper may be made into a rod shape, and a recess portion into which the rod-shaped portion of the first stopper loosely fits may be formed on the inner circumferential surface of a portion of the second stopper. Further, the shape of the first stopper portion 41 and the shape of the second stopper portion 42 can be reversed.
本実施例２のダイナミックダンパは、前記実施例１のダ
イナミックダンパと同様の作用、効果を有するほか、第
１ストッパ一部４１の凸部４１１と第２ストッパ一部４
２の凹部４２１とが当接し合うことにより、第１筒状体
１１と第２筒状体２との間の過度の回転が規制される。The dynamic damper of the second embodiment has the same functions and effects as the dynamic damper of the first embodiment, and also has the convex portion 411 of the first stopper part 41 and the second stopper part 4.
By the two recesses 421 coming into contact with each other, excessive rotation between the first cylindrical body 11 and the second cylindrical body 2 is restricted.
このため、弾性部材３の弾性部３２．３２の変形が抑制
され、弾性部材３の耐久性を向上させることもできる。Therefore, deformation of the elastic portions 32, 32 of the elastic member 3 is suppressed, and the durability of the elastic member 3 can also be improved.
［発明の効果］
以上詳述したように、本発明のダイナミックダンパは、
弾性部材を中間板とこの中間板の両面側に一体的に固定
された弾性部とから構成することにより、弾性部材の周
方向におけるばね特性を軟かく維持したまま、径方向に
おけるばね特性を硬くしたものである。したがって、回
転軸に発生する周波数の低めの捩り振動に対しても、ま
た回転軸に発生する周波数の高めの曲げ振動に対しても
効果的に減衰機能を発揮し、上記捩り撮動を原因とする
中速こもり音及び上記曲げ］騒動を原因とする高速こも
り音を確実に防止することができる。[Effects of the Invention] As detailed above, the dynamic damper of the present invention has the following effects:
By configuring the elastic member from an intermediate plate and elastic parts integrally fixed to both sides of the intermediate plate, the spring characteristics of the elastic member in the radial direction can be made hard while maintaining the spring characteristics soft in the circumferential direction. This is what I did. Therefore, it exhibits an effective damping function for both low-frequency torsional vibrations that occur on the rotating shaft as well as high-frequency bending vibrations that occur on the rotating shaft. [Medium-speed muffled sound caused by the above-mentioned bending] High-speed muffled sound caused by the commotion can be reliably prevented.
また、本発明のダイナミックダンパは、弾性部材が中間
板とその両面側に固定された弾性部とからなり、非常に
簡単な構造であるため、容易にかつ低コストで製造する
ことができる。Further, the dynamic damper of the present invention has a very simple structure in which the elastic member is composed of an intermediate plate and elastic parts fixed to both sides of the intermediate plate, and therefore can be manufactured easily and at low cost.
第１図は実施例１のダイナミックダンパの横断面図、第
２図は実施例２のダイナミックダンパの横断面図、第３
図は従来のダイナミックダンパの縦断面図、第４図は従
来の他のダイナミックダンパの横断面図である。
１．１１・・・第１筒状体 ２・・・第２筒状体３・・
・弾性部材 ４・・・ストッパ一部材３１・・
・中間板 ３２・・・弾性部４１・・・第１ス
トッパ一部
４２・・・第２ストッパ一部
第１図Figure 1 is a cross-sectional view of the dynamic damper of Example 1, Figure 2 is a cross-sectional view of the dynamic damper of Example 2, and Figure 3 is a cross-sectional view of the dynamic damper of Example 2.
The figure is a longitudinal cross-sectional view of a conventional dynamic damper, and FIG. 4 is a cross-sectional view of another conventional dynamic damper. 1.11...First cylindrical body 2...Second cylindrical body 3...
・Elastic member 4...stopper member 31...
・Intermediate plate 32...Elastic part 41...Part of first stopper 42...Part of second stopper Fig. 1
Claims (1)
状体と、 該第１筒状体と該第２筒状体との間で、周方向に等間隔
に配設された少なくとも３個以上の弾性部材とからなり
、 該弾性部材は該第１筒状体と該第２筒状体との間に同心
状に位置する弧状断面をもつ中間板と該中間板の両面側
に一体的に固定された弾性部とからなることを特徴とす
るダイナミックダンパ。(1) A first cylindrical body held on a rotating shaft; a second cylindrical body disposed concentrically radially outward of the first cylindrical body; It consists of at least three elastic members disposed at equal intervals in the circumferential direction between the second cylindrical body and the first cylindrical body and the second cylindrical body. A dynamic damper comprising an intermediate plate having an arcuate cross section located concentrically therebetween, and elastic parts integrally fixed to both sides of the intermediate plate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25909489A JPH03121331A (en) | 1989-10-04 | 1989-10-04 | Dynamic damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25909489A JPH03121331A (en) | 1989-10-04 | 1989-10-04 | Dynamic damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH03121331A true JPH03121331A (en) | 1991-05-23 |
Family
ID=17329235
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP25909489A Pending JPH03121331A (en) | 1989-10-04 | 1989-10-04 | Dynamic damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH03121331A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2710381A1 (en) * | 1993-09-23 | 1995-03-31 | Hutchinson | Damper (oscillator) for vibrating bar |
| US5971859A (en) * | 1993-10-20 | 1999-10-26 | Firma Carl Freudenberg | Vibration canceler which is mountable on shaft with enlargements |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5973643A (en) * | 1982-10-15 | 1984-04-25 | Honda Motor Co Ltd | Camshaft vibration suppressor of internal-combustion engine |
-
1989
- 1989-10-04 JP JP25909489A patent/JPH03121331A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5973643A (en) * | 1982-10-15 | 1984-04-25 | Honda Motor Co Ltd | Camshaft vibration suppressor of internal-combustion engine |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2710381A1 (en) * | 1993-09-23 | 1995-03-31 | Hutchinson | Damper (oscillator) for vibrating bar |
| US5971859A (en) * | 1993-10-20 | 1999-10-26 | Firma Carl Freudenberg | Vibration canceler which is mountable on shaft with enlargements |
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