JP4511420B2

JP4511420B2 - Dynamic damper

Info

Publication number: JP4511420B2
Application number: JP2005167476A
Authority: JP
Inventors: 和夫三宅
Original assignee: Kurashiki Kako Co Ltd
Current assignee: Kurashiki Kako Co Ltd
Priority date: 2005-06-07
Filing date: 2005-06-07
Publication date: 2010-07-28
Anticipated expiration: 2025-06-07
Also published as: JP2006342847A

Description

本発明は、振動体に付加されてその振動レベルを低下させるダイナミックダンパに関し、特に複数の板部材を積層したウエイトの構造の技術分野に属する。 The present invention relates to a dynamic damper which is added to a vibrating body to reduce its vibration level, and particularly belongs to the technical field of a weight structure in which a plurality of plate members are laminated.

従来より、例えば自動車のエンジンのような振動発生源やエンジンマウント、サスペンションメンバなど振動の伝達経路となる部材（以下、振動体と総称する）に付加振動系を取り付けて、所定の周波数域において振動体の振動を吸収し、その振動レベルを低下させるようにしたダイナミックダンパは公知である（例えば特許文献１、２などを参照）。 Conventionally, for example, an additional vibration system is attached to a vibration transmission path such as an automobile engine, an engine mount, a suspension member, etc. (hereinafter collectively referred to as a vibrating body) to vibrate in a predetermined frequency range. Dynamic dampers that absorb body vibration and reduce the vibration level are known (see, for example, Patent Documents 1 and 2).

そのような公知のダイナミックダンパは、低コスト化等のためにウエイトとして金属片を用い、これをバネ要素であるゴム弾性体を介して振動体に付加することが多い。そして、その付加振動系の固有振動数（共振周波数）を振動体の振動レベルが高い特定の周波数域に合わせるために、ウエイトの質量とゴム弾性体のバネ定数とを適宜、設定するようにしている。 Such a known dynamic damper often uses a metal piece as a weight for cost reduction and the like and adds this to a vibrating body via a rubber elastic body as a spring element. Then, in order to adjust the natural frequency (resonance frequency) of the additional vibration system to a specific frequency range where the vibration level of the vibrating body is high, the weight mass and the elastic constant of the rubber elastic body are appropriately set. Yes.

また、例えば特許文献３には、ステアリングホイールのボス部のように狭いスペースにダイナミックダンパを設置する場合に、そのウエイトを、板金プレス成型品の板部材を積層して構成することが提案されている。こうすることで、ウエイトを例えば鋳造や鍛造等する場合のように大幅なコストアップを招くことなく、その形状の自由度を高めることができるからである。
特開２００４−１１７８７号公報特開平１−２９３０５号公報特開平８−１２７３４７号公報 Further, for example, Patent Document 3 proposes that when a dynamic damper is installed in a narrow space such as a boss portion of a steering wheel, the weight is formed by laminating plate members of sheet metal press-formed products. Yes. By doing so, the degree of freedom of the shape can be increased without incurring a significant cost increase as in the case of casting or forging the weight.
JP 2004-11787 A JP-A-1-29305 JP-A-8-127347

ところで、一般的にダイナミックダンパの性能は共振曲線（図７参照）によって表され、共振点における山の高さ（共振倍率）が高いほど、効果的に振動を低減できるものであるが、前記のようにバネ要素をゴム弾性体によって構成した場合は、そのバネ定数の個体ばらつきが比較的大きくなるため、固有振動数を正確に設定することが難しいという実状がある。 By the way, the performance of a dynamic damper is generally represented by a resonance curve (see FIG. 7), and the higher the peak height (resonance magnification) at the resonance point, the more effectively vibration can be reduced. Thus, when the spring element is made of a rubber elastic body, the individual variation of the spring constant becomes relatively large, so that it is difficult to set the natural frequency accurately.

そのようにバネ定数がばらつくのはゴムの物性がばらつくことにも依るが、ゴム弾性体の寸法がばらつくことの影響も大きい。すなわち、前記のようなダイナミックダンパは、通常、金属製のウエイトを成形型に入れてゴムの加硫と同時に接着するようにしており、その際、成形型の内部でウエイトの位置がずれることにより、ゴム弾性体の寸法にばらつきを生じる。 Such a variation in the spring constant depends on the variation in the physical properties of the rubber, but is also greatly affected by the variation in the size of the rubber elastic body. That is, the dynamic damper as described above is usually configured such that a metal weight is put into a mold and bonded together with the vulcanization of the rubber, and at this time, the position of the weight is shifted within the mold. Variations in the dimensions of the rubber elastic body occur.

特に前記特許文献３のもののように板金プレス成型品の板部材を積層してウエイトを構成する場合には、板部材個々の厚みのばらつきが積み重なる上に、それらの隙間のばらつきも加わってウエイト自体の寸法が大きくばらつくことになるから、ゴム弾性体の寸法のばらつきはかなり大きくなってしまう。 In particular, when a weight is formed by laminating sheet metal press-molded plate members as in the above-mentioned Patent Document 3, the thickness of each of the plate members is accumulated, and the weight itself is added to the gaps. Therefore, the variation in the size of the rubber elastic body becomes considerably large.

そうしてゴム弾性体の寸法のばらつきが大きくなると、そのバネ定数のばらつきも大きくなるから、固有振動数が狙いとする値から大きくずれてしまい、ダイナミックダンパによって振動を効果的に低減できる周波数域と振動体の振動レベルが高い周波数域とが大きくずれて、所期の振動低減効果を得られなくなり、そればかりか、反共振による悪影響を生じる虞れもある。 Thus, when the variation in the size of the rubber elastic body increases, the variation in the spring constant also increases, so the natural frequency deviates significantly from the target value, and the frequency range in which vibration can be effectively reduced by the dynamic damper. And the frequency range in which the vibration level of the vibrating body is greatly shifted, the desired vibration reduction effect cannot be obtained, and there is also a possibility that an adverse effect due to anti-resonance may occur.

本発明は、斯かる点に鑑みてなされたものであり、その目的とするところは、板部材を積層したウエイトの構造に工夫を凝らして、ダイナミックダンパの固有振動数の個体ばらつきを小さくするとともに、該ダイナミックダンパによる振動低減効果が得られる周波数域を拡大して、少々の個体ばらつきがあっても振動を十分に低減できるようにすることにある。 The present invention has been made in view of such points, and the object of the present invention is to devise the structure of the weight in which the plate members are laminated to reduce the individual variation of the natural frequency of the dynamic damper. An object of the present invention is to expand the frequency range where the vibration reduction effect by the dynamic damper can be obtained so that vibration can be sufficiently reduced even if there is a slight individual variation.

前記の目的を達成するために、本発明では、ウエイトを構成する複数の板部材のうち、振動体に最も近い第１の板部材を厚み方向に屈曲する形状とし、これと隣接する第２の板部材との間に空間部を形成して、ここで該第１の板部材を保持することにより、ゴム弾性体と加硫接着する際の位置決め精度を高めるようにした。 In order to achieve the above object, in the present invention, among the plurality of plate members constituting the weight, the first plate member closest to the vibrating body is bent in the thickness direction, and the second plate adjacent thereto is formed. By forming a space between the plate member and holding the first plate member, the positioning accuracy when vulcanized and bonded to the rubber elastic body is increased.

具体的に、請求項１の発明は、複数の板部材が積層されたウエイトを、ゴム弾性体を介して振動体に連結してなるダイナミックダンパが対象であり、それら複数の板部材のうち、前記振動体に最も近い第１板部材及び当該第１板部材に隣接する第２板部材がいずれも中心に貫通穴を有しているとともに当該貫通穴を囲む内周側の部位と外周側の部位との間に厚み方向の段差を有するように皿状に屈曲形成されていて、且つ、当該第１板部材の外周側の部位と当該第２板部材の外周側の部位との間に環状の空間部が形成されるように、積層方向に相互に裏返された状態で互いに内周側の部位において接合されているとともに、前記空間部が前記ゴム弾性体と一体のゴム層により充填されており、このゴム層に、それら両板部材の間の空間部に対応して周方向に延びる凹部が形成されていることを特徴とする。 Specifically, the invention of claim 1 is directed to a dynamic damper formed by connecting a weight in which a plurality of plate members are laminated to a vibrating body through a rubber elastic body, and among these plurality of plate members, The first plate member closest to the vibrating body and the second plate member adjacent to the first plate member both have a through hole at the center and an inner peripheral portion and an outer peripheral side surrounding the through hole. It is bent and formed in a dish shape so as to have a step in the thickness direction between the part and an annular shape between the part on the outer peripheral side of the first plate member and the part on the outer peripheral side of the second plate member in so that the space portion is formed, together are joined at the site of the inner peripheral sides while being flipped from one another in the stacking direction, the space is filled by the rubber elastic body and the rubber layer integral cage, to the rubber layer, versus the space between them two plate members Wherein the recess extending in the circumferential direction and is formed.

前記構成のダイナミックダンパは、ウエイトを構成する積層された複数の板部材のうち、最下層の第１板部材が厚み方向に段差を有するように屈曲形成されて、これと隣接する第２板部材との間に空間部が形成されている。このため、ウエイトをゴムの成形型に入れてゴム弾性体と加硫接着する際に、そのゴム弾性体と直接、接する第１板部材を前記の空間部を利用して保持することができ、これにより成形型に対する位置決め精度を高くすることができる。 The dynamic damper having the above-described configuration is formed by bending the lowermost first plate member among the plurality of stacked plate members constituting the weight so as to have a step in the thickness direction, and is adjacent to the second plate member. A space is formed between the two. For this reason, when the weight is placed in a rubber mold and vulcanized and bonded to the rubber elastic body, the first plate member that is in direct contact with the rubber elastic body can be held using the space portion, Thereby, the positioning precision with respect to a shaping | molding die can be made high.

このことで、前記板部材のそれぞれの厚みにばらつきがあり、さらにそれらの隙間によってウエイト自体の積層方向の寸法が大きくばらついていても、このことによってゴム弾性体の寸法が大きくばらつくことはなく、そのバネ定数のばらつきを小さくすることができる。そうして第２板部材との間の空間部を利用して第１板部材を保持しながら、ウエイトとゴム弾性体とを加硫接着すると、そのための保持具の痕跡として、前記の空間部に対応するウエイト外周上の位置に周方向に延びる凹部が形成されることになる。 Thereby, there is variation in the thickness of each of the plate members, and even if the dimension of the weight itself in the stacking direction varies greatly due to the gap between them, the size of the rubber elastic body does not vary greatly due to this, Variations in the spring constant can be reduced. Then, while holding the first plate member using the space portion between the second plate member and vulcanizing and bonding the weight and the rubber elastic body, the space portion is used as a trace of the holder for that purpose. A recess extending in the circumferential direction is formed at a position on the outer periphery of the weight corresponding to.

また、前記のように第１板部材がその厚み方向に屈曲した形状であると、これが平板状である場合に比べてウエイトが板部材の積層方向に長くなり、その重心位置が振動体から遠ざかることになる。このことで、ダイナミックダンパによって振動を低減できる周波数域が相対的に広くなり、その固有振動数（共振周波数）の個体ばらつきが少々あっても、狙いとする周波数域において振動の低減効果を得ることができる。 In addition, when the first plate member is bent in the thickness direction as described above, the weight is longer in the stacking direction of the plate members than in the case where the first plate member is flat, and the center of gravity is moved away from the vibrating body. It will be. As a result, the frequency range in which vibrations can be reduced by the dynamic damper is relatively wide, and even if there is a slight variation in the natural frequency (resonance frequency), vibration reduction effects can be obtained in the target frequency range. Can do.

前記のようにウエイトの形状及び重心位置が変化すると、振動を低減できる周波数域が変化することについて、質量及びバネ定数の同じ２つの付加振動系について説明すると、例えば模式的に図６(a)，(b)に示す２つの振動系の固有振動数ｆは、ウエイトＷの質量をＭとし、バネ要素であるゴム弾性体Ｒのバネ定数をｋとすると、簡略には
ｆ＝(２π)^−１・(ｋ／Ｍ)^１／２
と表され、両者は同じ値になる。しかし、前記２つの付加振動系の共振曲線は、例えば図７に実線及び破線でそれぞれ示すような形状になり、共振点の山の高さや裾野の広さが異なるものとなる。 As described above, when the shape of the weight and the position of the center of gravity change, the frequency range in which vibration can be reduced changes. The two additional vibration systems having the same mass and spring constant will be described. For example, FIG. , (B), the natural frequency f of the two vibration systems is simply f = (2π) ⁻ , where M is the mass of the weight W and k is the spring constant of the rubber elastic body R as a spring element. ¹・ (k / M) ^1/2
And both have the same value. However, the resonance curves of the two additional vibration systems have shapes as indicated by, for example, the solid line and the broken line in FIG.

そのように共振曲線の形状が変化する理由は、ウエイトの重心周りの回動変位（首振り）に起因すると考えられる。すなわち、図示のようなウエイトＷを備えた付加振動系においては振動の入力によってウエイトＷの重心Ｇが並進移動するとともに、それが重心Ｇの周りに回動（首振り）することから、ゴム弾性体Ｒの歪みはその内部において一定ではなく、或る程度の幅を持つことになる。 The reason why the shape of the resonance curve changes in this way is considered to be due to rotational displacement (swinging) around the center of gravity of the weight. That is, in the additional vibration system having the weight W as shown in the figure, the center of gravity G of the weight W translates and moves around the center of gravity G due to the input of vibration. The distortion of the body R is not constant inside, but has a certain width.

そして、加硫ゴムの性質として、その動バネ定数は歪み振幅とともに低下するので、前記のようにゴム弾性体Ｒの歪みが部位によって異なり、また、ウエイトＷの首振りの大きさによっても異なるものであるとすれば、ゴム弾性体Ｒ全体としての平均的な動バネ定数ｋの値も一定ではなく、或る程度の幅を持つことになる。このため、前記の式によって導かれる固有振動数ｆの値も或る程度の幅を持つものとなり、そのことが前記のような共振曲線の形状の変化として現れるのである。 As a property of vulcanized rubber, since its dynamic spring constant decreases with strain amplitude, the strain of the rubber elastic body R varies depending on the part as described above, and also varies depending on the swing of the weight W. If this is the case, the value of the average dynamic spring constant k of the rubber elastic body R as a whole is not constant but has a certain width. For this reason, the value of the natural frequency f derived by the above formula also has a certain width, which appears as a change in the shape of the resonance curve as described above.

すなわち、例えば前記図６(a)のようにウエイトＷが比較的細長くて、その重心Ｇの高さｈが比較的高い（振動体から遠い）場合には、自ずと首振りが大きくなるので、この付加振動系の共振曲線は図７に破線で示すようになり、共振点における山の高さがやや低くなるものの、その裾野は広がって、振動を低減できる周波数域が比較的広くなる。 That is, for example, when the weight W is relatively long and the height h of the center of gravity G is relatively high (distant from the vibrating body) as shown in FIG. The resonance curve of the additional vibration system is as shown by a broken line in FIG. 7. Although the height of the peak at the resonance point is slightly lowered, the base is widened, and the frequency region where vibration can be reduced becomes relatively wide.

これに対し、図６(b)のようにウエイトＷが比較的扁平で、その重心Ｇの高さｈが比較的低い（振動体に近い）場合には、首振りは小さくなるので、図７に実線で示すように共振曲線の山の高さが高くなって、振動低減効果は高くなるが、一方で、その裾野は狭くなるので、振動を低減できる周波数域は比較的狭くなってしまうのである。 In contrast, when the weight W is relatively flat and the height h of the center of gravity G is relatively low (close to the vibrating body) as shown in FIG. As shown by the solid line, the height of the peak of the resonance curve increases and the vibration reduction effect increases, but on the other hand, the base becomes narrow, so the frequency range where vibration can be reduced becomes relatively narrow. is there.

以上、要するに、前記の如き構成の本発明のダイナミックダンパは、板部材を積層したウエイトを使用する場合でも、このウエイトを振動体に連結するゴム弾性体の寸法のばらつきを抑制して、そのバネ定数のばらつきを小さくし、これにより固有振動数のばらつきを減らすことができるとともに、ウエイトを比較的重心の高い（重心位置を振動体から遠い）形状とすることで、振動低減効果の得られる周波数域を広げることができ、それらの相乗的な効果で、狙いとする周波数域の振動を十分に低減できるようになる。 In short, the dynamic damper of the present invention having the above-described configuration suppresses variation in the size of the rubber elastic body connecting the weight to the vibrating body even when using a weight in which plate members are laminated, and its spring. A frequency that can reduce vibration by reducing the variation in constants, thereby reducing the variation in natural frequency, and making the weight a relatively high center of gravity (the center of gravity is far from the vibrating body). The frequency range can be expanded, and the synergistic effect of them can sufficiently reduce the vibration in the target frequency range.

さらに、第１及び第２の板部材をいずれも中心に貫通穴を有する皿状に形成し、これらを積層方向に相互に裏返した状態で、貫通穴を囲む内周側の部位において接合しているので、皿状に形成された第１板部材の外周部を、その全周においてより確実に保持することができる。また、第２板部材も第１板部材と同様に厚み方向に屈曲されているため、それらが積層されたウエイトの重心位置をより高くすることができ、これにより、振動低減効果の得られる周波数域をより広げることができる。 Furthermore , both the first and second plate members are formed in a dish shape having a through hole at the center, and are joined to each other on the inner peripheral side surrounding the through hole in a state where they are reversed inside each other in the stacking direction. Therefore , the outer peripheral part of the 1st board member formed in the dish shape can be hold | maintained more reliably in the perimeter. Further, since the second plate member is also bent in the thickness direction in the same manner as the first plate member, the center of gravity of the weight on which the second plate member is laminated can be made higher, and thereby the frequency at which the vibration reduction effect can be obtained. The range can be expanded.

その場合に、前記ウエイトの構造として、さらに好ましいのは、前記第１及び第２板部材と同様に中心に貫通穴を有しているとともに当該貫通穴を囲む内周側の部位と外周側の部位との間に厚み方向の段差を有する皿状の第３板部材を備え、この第３板部材と前記第２板部材とを積層方向に相互に裏返した状態で、互いに外周側の部位において接合することである（請求項２）。こうすれば、皿状の第１〜第３板部材が積層されたウエイトの重心位置がさらに高くなるので、振動低減効果の得られる周波数域をより一層、広げることができる。 In this case, the structure of the weight, more preferred, the inner peripheral side surrounding the through hole with which have a through-hole in the center as in the first and second plate member portion and the outer peripheral side of the comprising a dish-shaped third plate members have a stepped thickness direction between the sites, with the turned over and the third plate member and the second plate member to each other in the stacking direction, the site of each other the outer peripheral side (Claim 2 ). By doing so, the center of gravity position of the weight in which the dish-shaped first to third plate members are laminated is further increased, so that the frequency range where the vibration reduction effect can be obtained can be further expanded.

そして、そのように貫通穴を有する皿状の板部材を積層して、ウエイトを構成するのであれば、それらを全て略同一形状とすることで（請求項３）、コストの低減が図られる。 And if the plate-shaped board member which has a through-hole is laminated | stacked in that way and a weight will be comprised, all will be made into substantially the same shape (Claim 3 ), and reduction of cost will be aimed at.

但し、必ずしもそのように全ての板部材を略同一形状とする必要はなく、例えば、前記第２板部材は、中心に貫通穴を有する平板状に形成して、これを前記第１板部材と貫通穴を囲む内周側の部位において接合する構成としてもよい（請求項４）。 However, it is not always necessary to make all the plate members have substantially the same shape. For example, the second plate member is formed in a flat plate shape having a through hole in the center , and this is formed as the first plate member. It may be configured to be bonded at a portion inner periphery of surrounding the through hole (claim 4).

以上、説明したように、本発明に係るダイナミックダンパによると、複数の板部材を積層してウエイトを構成する場合でも、このウエイトを振動体に連結するゴム弾性体の寸法のばらつきを抑制して、そのバネ定数のばらつきを小さくし、これにより、ダイナミックダンパの固有振動数の個体ばらつきを小さくすることができるとともに、そのウエイトを比較的重心の高い（重心位置が振動体から遠い）形状として、振動低減効果の得られる周波数域を広げることができ、それらの相乗的な効果で振動体の所定周波数域の振動を十分に低減することができる。 As described above, according to the dynamic damper according to the present invention, even when a plurality of plate members are stacked to constitute a weight, variation in the size of the rubber elastic body that connects the weight to the vibrating body is suppressed. The variation of the spring constant can be reduced, thereby reducing the individual variation of the natural frequency of the dynamic damper, and the weight is made to have a relatively high center of gravity (the center of gravity is far from the vibrating body). The frequency range where the vibration reduction effect can be obtained can be widened, and the synergistic effect thereof can sufficiently reduce the vibration in the predetermined frequency range of the vibrating body.

特に、全ての板部材を全て略同一の皿状に形成し、それらを交互に裏返して積層するようにすれば、前記の効果を十分に得ながら、コストを低減することができる。 In particular, if all the plate members are formed in substantially the same dish shape, and they are alternately turned over and stacked, the cost can be reduced while sufficiently obtaining the above effects.

以下、本発明の実施形態を図面に基づいて詳細に説明する。尚、以下の好ましい実施形態の説明は、本質的に例示に過ぎず、本発明、その適用物或いはその用途を制限することを意図するものではない。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. It should be noted that the following description of the preferred embodiment is merely illustrative in nature, and is not intended to limit the present invention, its application, or its use.

図２は、本発明に係るダイナミックダンパＡを自動車のエンジンマウント１に適用した実施形態を示し、このエンジンマウント１は、図示しないエンジンと車体との間に介在されて、そのエンジンの静荷重を支持するとともに、エンジンの発生する振動を吸収し、或いは減衰させて車体への伝達を抑制するためのものである。この実施形態では、エンジンマウント１が振動体である。 FIG. 2 shows an embodiment in which the dynamic damper A according to the present invention is applied to an engine mount 1 of an automobile. The engine mount 1 is interposed between an engine (not shown) and a vehicle body to reduce the static load of the engine. In addition to supporting, the vibration generated by the engine is absorbed or attenuated to suppress transmission to the vehicle body. In this embodiment, the engine mount 1 is a vibrating body.

前記エンジンマウント１は、例えば、金属製外套２で補強したゴム製容器の中に液体を封入した上下２つの室を設け、この両室をオリフィスでつないだものであり、前記外套２には車体に取り付けるための車体ブラケット３〜５が設けられている。また、前記ゴム製容器の上部には金属製の支持部材６が結合されていて、この支持部材６にはエンジンに取り付けるためのエンジンブラケット７が締結されるようになっている。 The engine mount 1 includes, for example, two upper and lower chambers in which a liquid is sealed in a rubber container reinforced with a metal mantle 2, and these two chambers are connected by an orifice. Body brackets 3 to 5 are provided for attachment to the vehicle. A metal support member 6 is coupled to the upper portion of the rubber container, and an engine bracket 7 for attaching to the engine is fastened to the support member 6.

すなわち、エンジンから延設されるエンジンブラケット７の端部が前記支持部材６の上面に重ねられていて、そのブラケット７の端部上面にダイナミックダンパＡの後述する取付部材１１が重ねられて、この取付部材１１とブラケット７の端部とがボルト８により支持部材６に共締めされている。 That is, an end of an engine bracket 7 extending from the engine is overlaid on the upper surface of the support member 6, and a mounting member 11 (described later) of the dynamic damper A is overlaid on the upper surface of the end of the bracket 7. The attachment member 11 and the end of the bracket 7 are fastened together with the support member 6 by bolts 8.

ダイナミックダンパＡは、図１(a)に拡大して示すように、前記取付部材１１の上面にゴム弾性体１２を介してウエイト１３（同図(b)に単体で示す）が取付けられたものである。取付部材１１は、円板状の金属板によって形成されていて、その中心に前記ボルト８を挿通するためのボルト穴１１ａが形成されている。また、ゴム弾性体１２は、前記取付部材１１の上面でボルト穴１１ａの周囲を巡り、且つ上方に向かって延びる円筒状に形成されており、その内部に、取付部材１１の上面から離間して上下２枚の環状の板部材１４，１５からなるウエイト１３が埋め込まれている。 In the dynamic damper A, as shown in an enlarged view in FIG. 1A, a weight 13 (shown as a single body in FIG. 1B) is attached to the upper surface of the mounting member 11 via a rubber elastic body 12. It is. The attachment member 11 is formed of a disk-shaped metal plate, and a bolt hole 11a for inserting the bolt 8 is formed at the center thereof. The rubber elastic body 12 is formed in a cylindrical shape that goes around the bolt hole 11 a on the upper surface of the mounting member 11 and extends upward, and is separated from the upper surface of the mounting member 11 inside. A weight 13 composed of two upper and lower annular plate members 14 and 15 is embedded.

前記ゴム弾性体１２は、取付部材１１とその上方に対峙する板部材１５（振動体であるエンジンマウント１に最も近い第１板部材）とに挟まれた部分が、ダイナミックダンパＡのバネ要素として機能する主バネ部１２ａとされている。主バネ部１２ａは、前記板部材１５の外周部の下面付近から取付部材１１の外周を囲む下端部まで、その外径がやや小さくされた小径部である。 The rubber elastic body 12 has a portion sandwiched between the attachment member 11 and a plate member 15 (a first plate member closest to the engine mount 1 as a vibrating body) facing the mounting member 11 as a spring element of the dynamic damper A. The main spring portion 12a functions. The main spring portion 12 a is a small-diameter portion whose outer diameter is slightly reduced from the vicinity of the lower surface of the outer peripheral portion of the plate member 15 to the lower end portion surrounding the outer periphery of the mounting member 11.

前記ウエイト１３を構成する２枚の板部材１４，１５は、いずれも金属製板材をプレス成形して、その中心に前記取付部材１１のボルト穴１１ａよりも大径の貫通穴１４ａ，１５ａを有する皿状に形成したものである。この例では、２枚の板部材は略同じ形状とされ、上下方向に相互に裏返された状態で重ねられて（積層されて）、貫通穴１４ａ，１５ａを囲む内周側の部位において溶接により接合されている。 The two plate members 14 and 15 constituting the weight 13 are both formed by press-molding a metal plate material and have through holes 14a and 15a having a diameter larger than that of the bolt hole 11a of the mounting member 11 at the center thereof. It is formed in a dish shape. In this example, the two plate members have substantially the same shape, are stacked (stacked) in an upside down state, and are welded at the inner peripheral side surrounding the through holes 14a and 15a. It is joined.

より詳しくは、図１(b)にのみ符号を付して示すが、前記板部材１４，１５は、それぞれ、内周フランジ部１４ｂ，１５ｂ及び外周フランジ部１４ｃ，１５ｃが傾斜部１４ｄ，１５ｄにより繋がれて、内外周間に厚み方向の段差ができるように緩やかに屈曲している。そして、両板部材１４，１５の貫通穴１４ａ，１５ａを囲む内周フランジ部１４ｂ，１５ｂ同士が接合されている一方、そこから外周側に向かって徐々に両板部材１４，１５の間隔が広くなっていて、そこにはウエイト１３の全周に亘る環状の空間部Ｓが形成されている。 More specifically, although only the reference numeral is shown in FIG. 1 (b), the plate members 14 and 15 have inner peripheral flange portions 14b and 15b and outer peripheral flange portions 14c and 15c respectively formed by inclined portions 14d and 15d. They are connected and bent gently so that there is a step in the thickness direction between the inner and outer peripheries. And while the inner peripheral flange parts 14b and 15b surrounding the through holes 14a and 15a of both the plate members 14 and 15 are joined, the space | interval of both the plate members 14 and 15 is gradually widened toward the outer peripheral side from there. An annular space S extending over the entire circumference of the weight 13 is formed there.

そして、同図(a)の如く、前記両板部材１４，１５の接合部を除くウエイト１３の表面全てが、主バネ部１２ａに連なるゴム弾性体１２のゴム層により覆われていて、そのうちの前記空間部Ｓに対応する相対的に厚肉のゴム層１２ｂには、板部材１５の外周フランジ部１５ｃの上面付近に沿って、全周に亘る環状の溝部１６（凹部）が形成されている。言い換えると、ゴム弾性体１２の外周には小径の主バネ部１２ａと前記溝部１６とに挟まれて、ちょうど板部材１５の外周フランジ部１５ｃを覆うように環状の畝部１７が形成されている。 As shown in FIG. 5 (a), the entire surface of the weight 13 except for the joint between the plate members 14 and 15 is covered with the rubber layer of the rubber elastic body 12 connected to the main spring portion 12a. In the relatively thick rubber layer 12b corresponding to the space portion S, an annular groove portion 16 (concave portion) is formed over the entire circumference along the vicinity of the upper surface of the outer peripheral flange portion 15c of the plate member 15. . In other words, an annular flange 17 is formed on the outer periphery of the rubber elastic body 12 so as to cover the outer peripheral flange portion 15c of the plate member 15 between the small-diameter main spring portion 12a and the groove portion 16. .

ここで、上述の構成のダイナミックダンパＡを製造するときには、図３に示すように、取付部材１１及びウエイト１３を前記のエンジンマウント１への取付時とは上下反転した状態で成形型Ｄ内のキャビティに設置し、このキャビティに充填したゴムの加硫と同時に、このゴムに接着する。この際、図の下方に位置する板部材１４が内外周側及び下側から下型ｄ１により保持されるとともに、図の上方に位置する板部材１５は、外周フランジ部１５ｃが外周側及び上側から上型ｄ２により保持され、且つ下側から中間型ｄ３によって保持されるようになる。また、取付部材１１は上型ｄ２及び下型ｄ１により挟持される。 Here, when manufacturing the dynamic damper A having the above-described configuration, as shown in FIG. 3, the mounting member 11 and the weight 13 are turned upside down from the time of mounting to the engine mount 1. It is installed in a cavity and bonded to the rubber simultaneously with the vulcanization of the rubber filled in the cavity. At this time, the plate member 14 located at the lower side of the figure is held by the lower mold d1 from the inner and outer peripheral sides and the lower side, and the plate member 15 located at the upper side of the figure has the outer peripheral flange portion 15c from the outer side and the upper side. It is held by the upper mold d2 and from the lower side by the intermediate mold d3. The attachment member 11 is sandwiched between the upper mold d2 and the lower mold d1.

こうして取付部材１１が上下の型ｄ１，ｄ２間に挟持されるとともに、板部材１５は、その外周フランジ部１５ｃを全周に亘って上型ｄ２と中間型ｄ３との間に挟まれた状態になって、いずれも成形型Ｄに対し精度良く位置決めされることになる。そのため、２枚の板部材１４，１５にそれぞれ厚みのばらつきがあり、さらに両者の間に隙間があって、ウエイト１３全体として高さ（厚み寸法）がばらついていても、取付部材１１と板部材１５との間に形成されるゴム弾性体１２の主バネ部１２ａの高さ（厚み寸法）が大きくばらつくことはなく、そのバネ定数のばらつきを小さくすることができる。 In this way, the attachment member 11 is sandwiched between the upper and lower molds d1 and d2, and the plate member 15 is in a state in which the outer peripheral flange portion 15c is sandwiched between the upper mold d2 and the intermediate mold d3 over the entire circumference. Thus, both are accurately positioned with respect to the mold D. Therefore, even if the thickness of the two plate members 14 and 15 varies, and there is a gap between them, and the height (thickness dimension) varies as a whole of the weight 13, the mounting member 11 and the plate member 15, the height (thickness dimension) of the main spring portion 12a of the rubber elastic body 12 formed between the rubber elastic body 12 and the rubber elastic body 12 does not vary greatly, and variations in the spring constant can be reduced.

そうして板部材１５の外周フランジ部１５ｃを上型ｄ２と中間型ｄ３との中間に挟んだ状態で、ゴム弾性体１２を加硫成型すると、上述したように、ゴム弾性体１２の外周には板部材１５の外周フランジ部１５ｃに沿うようにして環状の溝部１６が形成され、この溝部１６と小径の主バネ部１２ａとの間に環状の畝部１７が形成されることになる。 When the rubber elastic body 12 is vulcanized and molded with the outer peripheral flange portion 15c of the plate member 15 sandwiched between the upper mold d2 and the intermediate mold d3, as described above, An annular groove portion 16 is formed along the outer peripheral flange portion 15c of the plate member 15, and an annular flange portion 17 is formed between the groove portion 16 and the small-diameter main spring portion 12a.

したがって、この実施形態のダイナミックダンパＡは、プレス成型した金属製板部材１４，１５を重ね合わせてウエイト１３を構成する場合でも、このウエイト１３を振動体であるエンジンマウント１に連結するゴム弾性体１２においてバネ要素として機能する主バネ部１２ａの寸法のばらつきが抑制されて、そのバネ定数のばらつきが小さくなるので、このことに起因する固有振動数の個体ばらつきが小さくなり、エンジンマウント１の振動を低減する周波数域を精度良く設定することができる。 Therefore, the dynamic damper A of this embodiment is a rubber elastic body that connects the weight 13 to the engine mount 1 that is a vibrating body even when the weight 13 is formed by stacking the press-molded metal plate members 14 and 15. 12, the variation in the dimensions of the main spring portion 12a functioning as a spring element is suppressed, and the variation in the spring constant is reduced. Therefore, the individual variation in natural frequency due to this is reduced, and the vibration of the engine mount 1 is reduced. Can be set with high accuracy.

また、それぞれ厚み方向に屈曲する皿状の板部材１４，１５を相互に裏返して積層したことで、それらが平板状である場合に比べてウエイト１３が積層方向に長くなり、その重心位置が高くなるから、図６，７を参照して上述したように、振動を低減する周波数域を広げて、固有振動数の個体ばらつきが少々あっても、振動低減効果を得ることができる。 In addition, since the plate-like plate members 14 and 15 that are bent in the thickness direction are turned upside down and stacked, the weights 13 are longer in the stacking direction and the center of gravity is higher than when they are flat. Therefore, as described above with reference to FIGS. 6 and 7, the vibration reduction effect can be obtained even if the frequency range for reducing the vibration is widened and there is a little individual variation in the natural frequency.

そして、そのようにダイナミックダンパＡの固有振動数のばらつきが小さくなり、振動を低減する周波数域が精度良く設定できることと、その周波数域が相対的に広くなることとの相乗的な効果で、エンジンマウント１の振動を狙いとする周波数域において十分に吸収し、その振動レベルを低下させることができる。 As a result, the variation in the natural frequency of the dynamic damper A is reduced, and the frequency range for reducing the vibration can be set with high accuracy, and the synergistic effect that the frequency range becomes relatively wide. The vibration can be sufficiently absorbed in the frequency range aimed at the vibration of the mount 1, and the vibration level can be lowered.

加えて、この実施形態では、前記のようにプレス成型した同一形状の板部材１４，１５を重ね合わせて、ウエイト１３を構成するようにしているので、例えば鋳造、鍛造等する場合に比べてウエイト１３の製造コストをかなり低減することができ、これによりダイナミックダンパＡの製造コストも低減できる。 In addition, in this embodiment, the weights 13 are formed by superimposing the plate members 14 and 15 having the same shape that are press-molded as described above. Thus, the manufacturing cost of the dynamic damper A can be reduced.

（他の実施形態）
尚、本発明の構成は、前記実施形態に限定されるものではなく、その他の種々の実施形態を包含するものである。すなわち、前記の実施形態では、ウエイト１３を２枚の皿状の板部材１４，１５により構成しているが、これに限らず、例えば図４に一例を示すように、第１の板部材１５と重ね合わされる第２の板部材１４は、その内周側に貫通穴１４ａを有する略平坦な円板状に形成してもよい。 (Other embodiments)
In addition, the structure of this invention is not limited to the said embodiment, The other various embodiment is included. That is, in the above-described embodiment, the weight 13 is constituted by the two plate-like plate members 14 and 15, but the present invention is not limited to this. For example, as shown in FIG. The second plate member 14 overlapped with may be formed in a substantially flat disk shape having a through hole 14a on the inner peripheral side thereof.

或いは、例えば図５に一例を示すように、２枚の板部材１４，１５と同じ形状の第３の板部材１８を第２の板部材１４に上方から重ね合わせて、積層することもできる。この場合、図示の如く第３の板部材１８及び第２の板部材１４はその積層方向に相互に裏返した状態で、互いに外周フランジ部において接合するのがよい。こうすれば、皿状の３枚の板部材１４，１５，１８を積層したウエイト１３がさらに長くなり、その重心位置がさらに高くなるので、振動低減効果の得られる周波数域をより一層、広げることができる。 Alternatively, for example, as shown in FIG. 5, the third plate member 18 having the same shape as the two plate members 14 and 15 may be stacked on the second plate member 14 from above. In this case, as shown in the drawing, the third plate member 18 and the second plate member 14 are preferably joined to each other at the outer peripheral flange portion in a state in which they are turned upside down in the stacking direction. By doing so, the weight 13 in which the three plate-like plate members 14, 15, 18 are laminated is further lengthened and the center of gravity is further increased, so that the frequency range where the vibration reduction effect can be obtained is further expanded. Can do.

さらに、ウエイト１３を構成する板部材は、前記のような皿状や円板状のものでなくてもよく、例えば平面視で矩形の板部材を折り曲げて厚み方向に段差ができるような形状とするだけでもよい。 Further, the plate member constituting the weight 13 does not have to be in the shape of a dish or a disk as described above, and for example, has a shape that allows a step in the thickness direction by bending a rectangular plate member in plan view. You can just do it.

また、前記実施形態では、ダイナミックダンパＡの製造時に中間型ｄ３によってウエイト１３の板部材１５の全周を保持するようにしており、そのため、ゴム弾性体１２の外周には全周に亘って溝部１６が形成されることになるが、前記板部材１５の外周の一部を保持するようにしてもよく、そうすれば、ゴム弾性体１２の外周には周方向に延びる凹部が形成されることになる。 In the above embodiment, the entire circumference of the plate member 15 of the weight 13 is held by the intermediate mold d3 during the production of the dynamic damper A. Therefore, a groove portion is formed on the outer circumference of the rubber elastic body 12 over the entire circumference. 16 may be formed, but a part of the outer periphery of the plate member 15 may be held, and in this case, a recess extending in the circumferential direction is formed on the outer periphery of the rubber elastic body 12. become.

さらにまた、前記実施形態では、本発明のダイナミックダンパＡを自動車用のエンジンマウント１に取り付けているが、ダイナミックダンパＡの用途は、それに限定されず、例えば、それ以外のエンジンマウント、自動車のサスペンションブッシュ等、種々の用途に用いられる。 Furthermore, in the above-described embodiment, the dynamic damper A of the present invention is attached to the engine mount 1 for an automobile. However, the application of the dynamic damper A is not limited thereto, and for example, other engine mounts and automobile suspensions are used. Used for various applications such as bushing.

以上、説明したように、本発明に係るダイナミックダンパは、板部材を積層して、比較的低コストで形状の自由度が高いウエイトを構成することができるとともに、その場合でも固有振動数の個体ばらつきを抑えて、振動体の振動を狙いとする周波数域において十分に低減できるものなので、例えば自動車のエンジンマウント、サスペンションブッシュを始めとして、各種産業機械などにも好適なものである。 As described above, the dynamic damper according to the present invention can form a weight with a relatively low cost and a high degree of freedom of shape by laminating plate members, and even in that case, an individual having a natural frequency can be formed. Since it can be sufficiently reduced in a frequency range aimed at vibration of the vibrating body while suppressing variations, it is also suitable for various industrial machines including engine mounts and suspension bushes of automobiles, for example.

本発明に係るダイナミックダンパを示す斜視図であり、(a)は一部を切り欠いてダンパの内部構造を示し、(b)はウエイトを単体で示す。It is a perspective view which shows the dynamic damper which concerns on this invention, (a) cuts off a part and shows the internal structure of a damper, (b) shows a weight single-piece | unit. 同ダイナミックダンパを適用したエンジンマウントの正面図である。It is a front view of the engine mount to which the dynamic damper is applied. 同ダイナミックダンパの製造過程を模式的に示す断面図である。It is sectional drawing which shows typically the manufacturing process of the dynamic damper. ウエイトに円板を用いた他の実施形態の図１(a)相当図である。It is the figure equivalent to Drawing 1 (a) of other embodiments using a disk for weight. ウエイトとして３枚の板部材を用いた他の実施形態の図１(a)相当図である。It is the figure equivalent to Drawing 1 (a) of other embodiments using three board members as weight. ウエイトの形状が異なる２つの付加振動系を模式的に示す説明図である。It is explanatory drawing which shows typically two additional vibration systems from which the shape of a weight differs. 同２つの付加振動系の共振曲線を対比して示すグラフ図である。It is a graph which contrasts and shows the resonance curve of the two additional vibration systems.

Ａダイナミックダンパ
１エンジンマウント（振動体）
１２ゴム弾性体
１２ａ主バネ部
１２ｂゴム層
１３ウエイト
１４板部材（第２の板部材）
１４ａ貫通穴
１５板部材（第１の板部材）
１５ａ貫通穴
１６溝部（凹部）
１８板部材（第３の板部材）
Ｓ空間部

A Dynamic damper 1 Engine mount (vibrating body)
12 Rubber elastic body 12a Main spring portion 12b Rubber layer 13 Weight 14 Plate member (second plate member)
14a Through hole 15 Plate member (first plate member)
15a Through hole 16 Groove (recess)
18 Plate member (third plate member)
S space

Claims

A dynamic damper formed by connecting a weight in which a plurality of plate members are laminated to a vibrating body via a rubber elastic body,
Of the plurality of plate members, the first plate member closest to the vibrating body and the second plate member adjacent to the first plate member both have a through hole at the center and surround the through hole. circumferential side of the site and have been bent into a dish shape so as to have a step in the thickness direction between the site of the outer peripheral side, and, an outer periphery of the first plate member outer peripheral side of the site and the second plate member in so that the space of the annular is formed between the portion of the side, they are joined at the site of the inner peripheral sides while being flipped from one another in the stacking direction,
The space is filled with a rubber layer integral with the rubber elastic body ;
Dynamic damper, wherein the rubber layer, the recess extending in the circumferential direction corresponding to the front Kisora between portion.

The dynamic damper according to claim 1 ,
The weights, are bent to the dish-shaped having a step in the thickness direction between the site of the inner periphery portion and the outer peripheral side surrounding the through hole with which have a through-hole in its center, the A dynamic damper, comprising: a third plate member joined to each other at a portion on the outer peripheral side in a state where the second plate member is turned upside down in the stacking direction.

In the dynamic damper according to claim 1 or 2 ,
Dynamic damper, characterized in that all said plate members are substantially the same shape.

A dynamic damper formed by connecting a weight in which a plurality of plate members are laminated to a vibrating body via a rubber elastic body,
Nearest first plate member, the thickness direction between the site of the peripheral side portion and the outer peripheral side of which together have have a through-hole in the center surrounding the through-hole in said vibration member among the plurality of plate members while being bent dished so as to have a stepped, the second plate member adjacent to the first plate member is formed in a plate shape having a through hole in its center,
Said first plate member and the second plate member, as the space of the annular is formed between the portion of the outer peripheral side of the first plate member outer peripheral side of the site and the second plate member, to each other It is joined at the inner peripheral part ,
The space is filled with a rubber layer integral with the rubber elastic body ;
The dynamic damper is characterized in that a concave portion extending in the circumferential direction corresponding to the space portion is formed in the rubber layer .