JP2006207705A

JP2006207705A - Vibration control rubber

Info

Publication number: JP2006207705A
Application number: JP2005020796A
Authority: JP
Inventors: Takeshi Oku; 岳史奥
Original assignee: Toyo Tire and Rubber Co Ltd
Current assignee: Toyo Tire Corp
Priority date: 2005-01-28
Filing date: 2005-01-28
Publication date: 2006-08-10

Abstract

PROBLEM TO BE SOLVED: To provide improved vibration control rubber capable of eliminating metallic abnormal sound due to collision of a supporting member such as a suspension member and an outer cylinder and eliminating or reducing metal fatigue of the outer cylinder. SOLUTION: In this vibration control rubber A composed of an inner cylinder 1, the outer cylinder 2 composed of a boss part 2A having a shaft axis P along the direction of shaft axis of the inner cylinder 1 and an outward facing flange part 2B along the radial direction of the inner cylinder 1, and a rubber part 3 provided among an inner peripheral face of the boss part 2A, an outer face of the flange part 2B, and the inner cylinder 1 to integrate both cylinders 1, 2 mutually by vulcanization bonding, the rubber part 3 is set to such shape that it goes around an outer end of the outward facing flange part 2B and reaches an inner face 2b of the outward facing flange part 2B. COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、自動車のエンジン等の振動発生体を防振懸架するのに用いられる防振ゴムに関するものである。 The present invention relates to an anti-vibration rubber used for anti-vibration suspension of a vibration generator such as an automobile engine.

この種の防振ゴムにおいて、内筒と、この内筒の軸心方向に沿う軸心を有するボス部、及び内筒の径方向に沿う外向きフランジ部から成る外筒と、ボス部の内周面及びフランジ部の外面と内筒との間に介在されて両筒を互いに加硫接着により一体化するゴム部と、を有して構成される構造のものがある。このような防振ゴムの例としては、特許文献１（特に、図４を参照）において開示されたものが知られている。この防振ゴムの使用例として、これ単品で使用されたり、或いは、図１６に示すように、一箇所に２個用いる構造のもの等がある。 In this type of anti-vibration rubber, an inner cylinder, an outer cylinder composed of a boss portion having an axial center along the axial direction of the inner cylinder, and an outward flange portion along the radial direction of the inner cylinder; There is a structure having a rubber part that is interposed between the outer surface of the peripheral surface and the flange part and the inner cylinder and integrates both cylinders by vulcanization adhesion. As an example of such an anti-vibration rubber, one disclosed in Patent Document 1 (especially, see FIG. 4) is known. As an example of use of this anti-vibration rubber, there is a structure that is used alone, or that has two structures as shown in FIG.

図１６において、３１は車体フレーム側の懸架部材、３２はエンジン側で板金材製のマウント部材、３３は取付ボルト、３４はワッシャ、３５はナット、Ａは防振ゴムであり、上下一対の防振ゴムＡ，Ａは、各々の外筒３７が懸架部材３１の装着孔３１ａに挿入され、かつ、互いに向い合せ状態で配備されている。各内筒３６，３６は、互いに当接される状態でマウント部材３２とワッシャとの間で取付ボルト３３とナット３５で締付け固定される。 In FIG. 16, 31 is a suspension member on the vehicle body frame side, 32 is a mounting member made of a sheet metal material on the engine side, 33 is a mounting bolt, 34 is a washer, 35 is a nut, and A is a vibration-proof rubber. The vibration rubbers A and A are arranged such that each outer cylinder 37 is inserted into the mounting hole 31a of the suspension member 31 and facing each other. Each of the inner cylinders 36 and 36 is fastened and fixed by a mounting bolt 33 and a nut 35 between the mount member 32 and the washer while being in contact with each other.

防振ゴムＡは、内筒３６と、断面形状が略Ｌ字状の外筒３７と、これら内外筒３６，３７の間のゴム部３８とから構成されており、外筒３７のボス部分３７ａを、装着孔３１ａに挿入して用いるように設定されている。このように、懸架部材３１の上下それぞれに防振ゴムＡを配置することにより、前後左右に加えて、エンジン（図示省略）のフレームに対する上下方向の動きに対しても有効な防振作用を得ることができている。 The anti-vibration rubber A includes an inner cylinder 36, an outer cylinder 37 having a substantially L-shaped cross section, and a rubber portion 38 between the inner and outer cylinders 36, and a boss portion 37 a of the outer cylinder 37. Is set so as to be inserted into the mounting hole 31a. In this way, by arranging the anti-vibration rubbers A on the upper and lower sides of the suspension member 31, in addition to the front, rear, left and right, an effective anti-vibration action can be obtained even with respect to the vertical movement of the engine (not shown). Is able to.

しかしながら、エンジンが大型で重量が非常に重いといった具合に荷重条件が厳しい状況では、設定される防振ゴムの初期撓み量の範囲内であっても、振動によって外筒３７が懸架部材３１から浮き上がることがあり、外筒３７と懸架部材３１とが再当接する際の衝撃によって金属異音の発生する場合があった。外筒３７は、通常は金属材から形成されており、振動的な衝撃には十分耐える強度を有してはいるが、あまり頻繁に異音発生するような場合は金属疲労の面から芳しいものではない。
特開平８−２８１６６４号公報 However, in a situation where the load conditions are severe, such as a large engine and a heavy weight, the outer cylinder 37 is lifted from the suspension member 31 due to vibration even within the range of the initial deflection amount of the anti-vibration rubber. In some cases, abnormal metal noise may be generated due to an impact when the outer cylinder 37 and the suspension member 31 come into contact again. The outer cylinder 37 is usually formed of a metal material and has a strength sufficient to withstand vibrational impacts. However, if abnormal noise is frequently generated, the outer cylinder 37 is good from the viewpoint of metal fatigue. is not.
JP-A-8-281664

そこで、本発明の目的は、内筒と、内筒の軸心方向に沿う軸心を有するボス部、及び内筒の径方向に沿う外向きフランジ部から成る外筒と、ボス部の内周面及びフランジ部の外面と内筒との間に介在されて両筒を互いに加硫接着により一体化するゴム部と、を有して構成される防振ゴムにおいて、懸架部材等の支持部材と外筒との衝突による金属異音を無くし、外筒の金属疲労が解消若しくは軽減される改善された防振ゴムを提供する点にある。 Accordingly, an object of the present invention is to provide an outer cylinder including an inner cylinder, a boss portion having an axial center along the axial direction of the inner cylinder, and an outward flange portion along the radial direction of the inner cylinder, and an inner circumference of the boss portion. A rubber part that is interposed between the outer surface of the surface and the flange part and the inner cylinder and integrates the two cylinders by vulcanization bonding, and a vibration isolating rubber configured to support a suspension member or the like; An object of the present invention is to provide an improved anti-vibration rubber that eliminates metal noise due to collision with the outer cylinder and eliminates or reduces metal fatigue of the outer cylinder.

請求項１に係る発明は、内筒１と、前記内筒１の軸心方向に沿う軸心Ｐを有するボス部２Ａ、及び前記内筒１の径方向に沿う外向きフランジ部２Ｂから成る外筒２と、前記ボス部２Ａの内周面及び前記フランジ部２Ｂの外面と前記内筒１との間に介在されて前記両筒１，２を互いに加硫接着により一体化するゴム部３と、を有して構成される防振ゴムＡにおいて、
前記ゴム部３は、前記外向きフランジ部２Ｂの外端を回り込んで前記外向きフランジ部２Ｂの内面２ｂに及ぶ形状に設定されていることを特徴とするものである。 The invention according to claim 1 is an outer structure comprising an inner cylinder 1, a boss portion 2 A having an axis P along the axial direction of the inner cylinder 1, and an outward flange portion 2 B along the radial direction of the inner cylinder 1. A cylinder 2 and a rubber part 3 interposed between the inner peripheral surface of the boss part 2A and the outer surface of the flange part 2B and the inner cylinder 1 to integrate the cylinders 1 and 2 by vulcanization bonding. In the anti-vibration rubber A constituted by having
The rubber part 3 is set in a shape that extends around the outer end of the outward flange part 2B and extends to the inner surface 2b of the outward flange part 2B.

請求項２に係る発明は、請求項１に記載の防振ゴムＡにおいて、前記ゴム部３における前記外向きフランジ部２Ｂの前記内面に及ぶフランジ回り込み部３Ｆは、前記内面２ｂの外周部の全周に亘る環状のものに形成されていることを特徴とするものである。 According to a second aspect of the present invention, in the anti-vibration rubber A according to the first aspect, the flange wrap-around portion 3F extending to the inner surface of the outward flange portion 2B in the rubber portion 3 is the entire outer peripheral portion of the inner surface 2b. It is characterized by being formed in an annular shape over the circumference.

請求項３に係る発明は、請求項１に記載の防振ゴムＡにおいて、前記ゴム部３における前記外向きフランジ部２Ｂの前記内面２ｂに及ぶフランジ回り込み部３Ｆは、前記内面２ｂの外周部において周方向に間欠的に形成されていることを特徴とするものである。 According to a third aspect of the present invention, in the anti-vibration rubber A according to the first aspect, the flange wrap-around portion 3F extending to the inner surface 2b of the outward flange portion 2B in the rubber portion 3 is formed at the outer peripheral portion of the inner surface 2b. It is characterized by being intermittently formed in the circumferential direction.

請求項４に係る発明は、請求項２又は３に記載の防振ゴムＡにおいて、前記フランジ回り込み部３Ｆの前記外向きフランジ部２Ｂの内面２ｂに沿うフランジ部分１９の厚みｔ、及び前記フランジ部分１９の前記径方向の幅ｄが、前記ゴム部３の外径をｒ、その厚みをｈとした場合に、次式（１），（２）によって規定されていることを特徴とするものである。
ｔ≦０．１ｈ…（１）
ｄ≦０．１５ｒ…（２） The invention according to claim 4 is the anti-vibration rubber A according to claim 2 or 3, wherein the flange portion 19 has a thickness t along the inner surface 2b of the outward flange portion 2B of the flange wrap portion 3F, and the flange portion. The radial width d of 19 is defined by the following equations (1) and (2) when the outer diameter of the rubber part 3 is r and the thickness is h: is there.
t ≦ 0.1h (1)
d ≦ 0.15r (2)

請求項５に係る発明は、請求項１〜４の何れか一項に記載の防振ゴムＡにおいて、前記ゴム部３は、前記ボス部２Ａの端面に回り込む形状に形成されていることを特徴とするものである。 According to a fifth aspect of the present invention, in the vibration-proof rubber A according to any one of the first to fourth aspects, the rubber portion 3 is formed in a shape that wraps around the end surface of the boss portion 2A. It is what.

請求項６に係る発明は、請求項５に記載の防振ゴムＡにおいて、前記ゴム部３は、前記ボス部２Ａの外周面４にまで及んでいることを特徴とするものである。 The invention according to claim 6 is the anti-vibration rubber A according to claim 5, wherein the rubber portion 3 extends to the outer peripheral surface 4 of the boss portion 2A.

請求項７に係る発明は、請求項６に記載の防振ゴムＡにおいて、前記ゴム部３における前記ボス部２Ａの外周面４に及ぶボス回り込み部３Ｂは、前記ボス部２Ａの周方向に間欠的に形成されていることを特徴とするものである。 According to a seventh aspect of the present invention, in the anti-vibration rubber A according to the sixth aspect, the boss wraparound portion 3B extending to the outer peripheral surface 4 of the boss portion 2A in the rubber portion 3 is intermittent in the circumferential direction of the boss portion 2A. It is characterized by being formed.

請求項１の発明によれば、防振ゴムが装備される金属製等の支持部材と外筒との間にはゴム部が介在されることになって、外筒と支持部材とが直接当接しない構造になるから、金属材で強度補償された防振ゴムとしながらも、金属材どうしの当接が生じないようになり、金属異音や騒音が起きず、従って、外筒の金属疲労が解消若しくは軽減される改善された好ましい防振ゴムを提供することができる。 According to the first aspect of the present invention, the rubber portion is interposed between the outer support and the metallic support member provided with the vibration isolating rubber, so that the outer support and the support member directly contact each other. Since the structure is not in contact with each other, the vibration-proof rubber is compensated for strength by the metal material, but the metal materials do not come into contact with each other, so that there is no metal noise or noise. Therefore, it is possible to provide an improved preferable vibration-proof rubber in which the problem is solved or reduced.

この場合、請求項２のように、回り込み部を外向きフランジ部の内面に及ぶフランジ回り込み部が全周に亘る環状のものとすれば、支持部材に圧接される外向きフランジ部との間にゴム部が介装されることとなり、効果的に金属異音を防止することができる。また、請求項３のように、フランジ回り込み部を周方向で間欠的に設けるようにすれば、防振ゴムの締付け装着に伴うフランジ回り込み部の圧縮による周方向への横拡がり変形が可能となり、回り込み部が全周に亘る環状のものに比べて、外径方向への変形スペースを多く見込まなくても済む利点がある。 In this case, as in the second aspect, if the wraparound portion is an annular one that extends over the entire circumference of the flange wrapping portion that extends to the inner surface of the outward flange portion, the wraparound portion is between the outward flange portion pressed against the support member. A rubber part will be interposed, and metal abnormal noise can be prevented effectively. Further, if the flange wrapping portion is intermittently provided in the circumferential direction as in claim 3, it is possible to perform lateral expansion deformation in the circumferential direction due to compression of the flange wrapping portion accompanying tightening and mounting of the vibration proof rubber, There is an advantage that it is not necessary to expect a large amount of deformation space in the outer diameter direction as compared with an annular shape in which the wraparound portion extends over the entire circumference.

請求項４の発明によれば、フランジ回り込み部の径方向寸法ｄと厚みｔとを式（１），（２）のようにゴム部の外径と厚みと関係付けて規定してあるので、防振ゴムの大きさや厚み等の構成寸法が種々に異なっても、外筒と支持部材との直接当接による異音（騒音）を防止しながら良好な防振性能を有する改善された防振ゴムを提供できる利点がある。 According to the invention of claim 4, since the radial dimension d and the thickness t of the wraparound portion of the flange are defined in relation to the outer diameter and thickness of the rubber portion as in the formulas (1) and (2), Improved anti-vibration performance with good anti-vibration performance while preventing abnormal noise (noise) due to direct contact between the outer cylinder and the support member, even if the size and thickness of the anti-vibration rubber are different. There is an advantage that rubber can be provided.

請求項５の発明によれば、ゴム部は、外筒におけるボス部の端面に回り込む形状とされているので、支持部材等のボス部の端面に当接する部材があるときには、その部材もゴムを介して当接することとなるから、金属材どうしの直接当接等による異音や騒音が回避される防振ゴムとすることができる。 According to the invention of claim 5, since the rubber portion is shaped to wrap around the end surface of the boss portion in the outer cylinder, when there is a member that contacts the end surface of the boss portion such as a support member, the member also has rubber. Therefore, the anti-vibration rubber can be used to avoid noise and noise caused by direct contact between metal materials.

この場合、請求項６のように、ゴム部がボス部の外周面にまで及ぶようにすれば、ボス部の外周面に当接するような部材がある場合において、その部材とボス部外周面とはゴムを介して当接して直接当接は回避され、やはり異音や騒音の解消が可能となる。また、請求項７のように、ボス回り込み部を周方向で間欠的に設けるようにすれば、防振ゴムの締付け装着に伴うボス回り込み部の圧縮による周方向への横拡がり変形が可能となり、回り込み部が全周に亘る環状のものに比べて、外径方向への変形スペースを多く見込まなくても済む利点がある。 In this case, when the rubber part extends to the outer peripheral surface of the boss part as in claim 6, when there is a member that comes into contact with the outer peripheral surface of the boss part, the member and the outer peripheral surface of the boss part The contact is made through rubber and direct contact is avoided, and it is possible to eliminate noise and noise. Further, if the boss wraparound portion is intermittently provided in the circumferential direction as in claim 7, it becomes possible to perform lateral expansion deformation in the circumferential direction due to compression of the boss wraparound portion accompanying tightening and mounting of the vibration isolating rubber, There is an advantage that it is not necessary to expect a large amount of deformation space in the outer diameter direction as compared with an annular shape in which the wraparound portion extends over the entire circumference.

以下に、本発明による防振ゴムの実施の形態を、図面を参照しながら説明する。図１〜図５は実施例１〜５による防振ゴムの構造を示す断面図、図６は実施例６による防振ゴムの底面図と全体斜視図、図７〜図１０は防振ゴムの使用例１〜４を示す要部の断面図、図１１〜図１６は変形例１〜６を示す断面図である。 In the following, embodiments of the anti-vibration rubber according to the present invention will be described with reference to the drawings. 1 to 5 are sectional views showing the structure of the vibration isolating rubber according to Examples 1 to 5, FIG. 6 is a bottom view and an overall perspective view of the vibration isolating rubber according to Example 6, and FIGS. Sectional drawing of the principal part which shows the usage examples 1-4, FIGS. 11-16 is sectional drawing which shows the modifications 1-6.

〔実施例１〕
実施例１による防振ゴムＡは、図１に示すように、円筒状の内筒１と、内筒１の軸心Ｐを共有する（軸心Ｐ方向に沿う軸心を有する）ボス部２Ａ、及び内筒１の径方向に沿う外向きフランジ部２Ｂから成る上下方向視で円形の外筒２と、ボス部２Ａの内周面であり、かつ、外向きフランジ部２Ｂの外面でもある外筒２の上表面４と内筒１の外面５との間に介在されて両筒１，２を互いに加硫接着により一体化するゴム部３と、を有して構成された上下方向視で円形を呈している。内筒１と外筒２とは金属材から形成されている。 [Example 1]
As shown in FIG. 1, the anti-vibration rubber A according to the first embodiment shares a cylindrical inner cylinder 1 and an axial center P of the inner cylinder 1 (having an axial center along the axial center P direction) 2A. , And an outer flange 2B formed of an outward flange portion 2B along the radial direction of the inner tube 1, and an outer surface that is the inner peripheral surface of the boss portion 2A and the outer surface of the outer flange portion 2B. In a vertical view, the rubber portion 3 is interposed between the upper surface 4 of the cylinder 2 and the outer surface 5 of the inner cylinder 1 and integrates both cylinders 1 and 2 by vulcanization adhesion. It has a circular shape. The inner cylinder 1 and the outer cylinder 2 are formed from a metal material.

内筒１は、ボルト挿通用の貫通孔６を有するとともに、上下の外周角部には面取り部８が形成されており、比較的厚肉の円筒部材に形成されている。外筒２には、ボス部２Ａの上部、及び外向きフランジ部２Ｂの内径部とを屈曲形成することにより、上方に凹入した環状の角逃げ湾曲部９が形成されている。ゴム部３は、ボス部２Ａの下端面２ａに回り込む形状に形成されるとともに、ボス部２Ａの下端面２ａと内周面４との境目部分に形成される角部ｋが、二以上の鈍角部を有する多角形状又は曲面形状に形成されている。つまり、角部ｋには、ボス部１の面取り部８と同様な面取り（いわゆるＣ面取り）部１０が形成されている。この面取り部１０は、一般的な面取り加工によって形成されても良い。 The inner cylinder 1 has a through-hole 6 for inserting a bolt, and chamfered portions 8 are formed at upper and lower outer peripheral corners, which are formed in a relatively thick cylindrical member. The outer cylinder 2 is formed with an annular angular relief curved portion 9 that is recessed upward by bending the upper portion of the boss portion 2A and the inner diameter portion of the outward flange portion 2B. The rubber portion 3 is formed in a shape that wraps around the lower end surface 2a of the boss portion 2A, and the corner portion k formed at the boundary portion between the lower end surface 2a of the boss portion 2A and the inner peripheral surface 4 has two or more obtuse angles. It is formed in a polygonal shape having a portion or a curved shape. That is, a chamfer (so-called C chamfer) 10 similar to the chamfer 8 of the boss 1 is formed at the corner k. The chamfered portion 10 may be formed by a general chamfering process.

ゴム部３は、図１に示すように、内筒１の上面１ａと同一の高さレベルを有する上面３ａ、内筒１の底面１ｂと同一の高さレベルを有する内底面３ｂ、外筒２のボス部２Ａの下端面２ａの下方に回り込み形成される中間底面３ｃ、外筒２の外向きフランジ部２Ｂの水平部分２ｂの上面に密着する密着底面３ｄ、内底面３ｂと中間底面３ｃとを結ぶ上方に大きく凹入した略逆Ｕ字状断面を有する凹入底面３ｅ、この凹入底面３ｅに対応するように上面３ａにおいて若干下方に凹入形成された溝面３ｆ、及び上面３ａと密着底面３ｄとを繋ぐ略テーパ面状の外周面３ｇとを有した形状に形成されている。 As shown in FIG. 1, the rubber portion 3 includes an upper surface 3 a having the same height level as the upper surface 1 a of the inner cylinder 1, an inner bottom surface 3 b having the same height level as the bottom surface 1 b of the inner cylinder 1, and the outer cylinder 2. An intermediate bottom surface 3c formed around the lower end surface 2a of the boss portion 2A, a close contact bottom surface 3d closely contacting the upper surface of the horizontal portion 2b of the outward flange portion 2B of the outer cylinder 2, and an inner bottom surface 3b and an intermediate bottom surface 3c. A recessed bottom surface 3e having a substantially inverted U-shaped cross-section that is largely recessed above the tie, a groove surface 3f that is recessed slightly below the upper surface 3a so as to correspond to the recessed bottom surface 3e, and a close contact with the upper surface 3a It is formed in a shape having a substantially tapered outer peripheral surface 3g connecting the bottom surface 3d.

つまり、ゴム部３は、内筒１の外周側で、かつ、外筒２のほぼ上側となる位置において環状のものに形成されており、本体ゴム部３Ｈとフランジ回り込み部３Ｆとボス回り込み部３Ｂとから形成されている。ボス回り込み部３Ｂは、ゴム部３における中間底面３ｃを含む部分と、その中間底面３ｃからボス部２Ａの外面に沿って立ち上がる筒状部分３ｔとを有して構成されている。 That is, the rubber part 3 is formed in an annular shape at a position on the outer peripheral side of the inner cylinder 1 and substantially above the outer cylinder 2, and the main body rubber part 3H, the flange wrap part 3F, and the boss wrap part 3B. And is formed from. The boss wraparound portion 3B includes a portion including the intermediate bottom surface 3c in the rubber portion 3, and a cylindrical portion 3t that rises from the intermediate bottom surface 3c along the outer surface of the boss portion 2A.

フランジ回り込み部３Ｆは、外周面３ｇの下端部における本体ゴム部３Ｈから張出し形成された部分であり、外向きフランジ部２Ｂにおける外周端部の外面（上表面４）に沿う環状の付根部分１７と、外向きフランジ部２Ｂの外端２ｔに沿う環状の繋ぎ部分１８と、外向きフランジ部２Ｂにおける外周端部の内面２ｂに沿う環状のフランジ部分１９とから成り、断面形状は略コ字状を呈している。つまりゴム部３は、外向きフランジ部２Ｂの外端を回り込んで外向きフランジ部２Ｂの内面２ｂに及ぶ形状に設定されている。これら各部分１７〜１９の厚みは、外筒２の厚みのおよそ半分であり、外周面３ｇから径方向の突出量はほぼ外筒２の厚み程度に相当している。 The flange wrapping portion 3F is a portion that is formed to protrude from the main rubber portion 3H at the lower end portion of the outer peripheral surface 3g, and has an annular root portion 17 along the outer surface (upper surface 4) of the outer peripheral end portion of the outward flange portion 2B. The annular connecting portion 18 along the outer end 2t of the outward flange portion 2B and the annular flange portion 19 along the inner surface 2b of the outer peripheral end portion of the outward flange portion 2B, and the cross-sectional shape is substantially U-shaped. Presents. That is, the rubber part 3 is set in a shape that extends around the outer end of the outward flange part 2B and extends to the inner surface 2b of the outward flange part 2B. The thickness of each of these portions 17 to 19 is approximately half of the thickness of the outer cylinder 2, and the amount of protrusion in the radial direction from the outer peripheral surface 3 g is substantially equivalent to the thickness of the outer cylinder 2.

環状のフランジ部分１９の径方向寸法ｄと厚みｔは、図１に示すように、ゴム部３の外径をｒ、ゴム部３の厚み（高さ）をｈとした場合には、
ｄ≦０．１５ｒ……（１）
ｔ≦０．１ｈ……（２）
という上式（１），（２）で規定される範囲の値に設定すると良い。より正確には、
０＜ｄ≦０．１５ｒ……（３）
０＜ｔ≦０．１ｈ……（４）
である。尚、上式（１），（２）は、フランジ部分１９が周方向に間欠的に存在するよう構成された後述構造の防振ゴム（図６参照）においても適用される。 As shown in FIG. 1, when the outer diameter of the rubber part 3 is r and the thickness (height) of the rubber part 3 is h as shown in FIG.
d ≦ 0.15r (1)
t ≦ 0.1h (2)
It is better to set the value within the range defined by the above formulas (1) and (2). More precisely,
0 <d ≦ 0.15r (3)
0 <t ≦ 0.1h (4)
It is. The above formulas (1) and (2) are also applied to a vibration-proof rubber (see FIG. 6) having a later-described structure in which the flange portion 19 is intermittently present in the circumferential direction.

そして、付根部分１７と外周面３ｇとは隅Ｒ（フィレットＲ）面１６で接続されており、それによって滑らかに繋がる形状とされている。つまり、本体ゴム部３Ｈとフランジ回り込み部３Ｆとの境目部分に形成される隅角部の表面が滑らかな凹曲面１６に設定されているのである。これにより、本体ゴム部３Ｈとフランジ回り込み部３Ｆとの境目部分における断面形状の急変が緩和され、その境目部分に応力集中による亀裂等の不具合発生するおそれを未然に防止できるようになっている。 And the root part 17 and the outer peripheral surface 3g are connected by the corner R (fillet R) surface 16, and it is set as the shape connected smoothly by it. That is, the surface of the corner portion formed at the boundary between the main rubber portion 3H and the flange wrap portion 3F is set to a smooth concave surface 16. As a result, sudden changes in the cross-sectional shape at the boundary between the main rubber part 3H and the flange wrap-around part 3F are alleviated, and it is possible to prevent the possibility of problems such as cracks due to stress concentration at the boundary.

このようにゴム部３には、外筒２の外端及び内端のそれぞれに回り込むフランジ回り込み部３Ｆとボス回り込み部３Ｂとが形成されているので、防振ゴムＡを支える図示しない支持部材（図７の符号２１が付された部材を参照）は、金属材で成る外筒２にはフランジ部分１９及び筒状部分３ｔを介して当接することになり、直接当接しない構造になる。その結果、金属材で強度補償された防振ゴムとしながらも、金属材どうしの当接が生ぜす、従って金属異音や騒音が起きない好ましいものとなっている。 As described above, the rubber portion 3 is formed with the flange wrap portion 3F and the boss wrap portion 3B that wrap around each of the outer end and the inner end of the outer cylinder 2, and therefore a support member (not shown) that supports the vibration-proof rubber A ( 7 (refer to the member denoted by reference numeral 21 in FIG. 7) is in contact with the outer cylinder 2 made of a metal material via the flange portion 19 and the cylindrical portion 3t, and does not directly abut. As a result, while the anti-vibration rubber whose strength has been compensated for with the metal material, the metal materials are brought into contact with each other, and therefore, it is preferable that no metal noise or noise occurs.

〔実施例２〕
実施例２による防振ゴムＡは、実施例１の防振ゴムＡ（図１参照）を基本としており、図２に示すように、ボス回り込み部３Ｂにおける筒状部分３ｔが省略されている以外は、図１に示す実施例１の防振ゴムＡと同じである。 [Example 2]
The anti-vibration rubber A according to the second embodiment is based on the anti-vibration rubber A according to the first embodiment (see FIG. 1), except that the cylindrical portion 3t in the boss wrap portion 3B is omitted as shown in FIG. These are the same as the anti-vibration rubber A of Example 1 shown in FIG.

〔実施例３〕
実施例３による防振ゴムＡは、実施例１の防振ゴムＡ（図１参照）を基本としており、図３に示すように、外筒２に施される面取り部１０が、ボス部２Ａの下端の内側角部から外向きフランジ部２Ｂの外周端の上側角部に変更されるとともに、外筒２の外向きフランジ部２Ｂの径が小型化されて付根部分１７の無いフランジ回り込み部３Ｆを有する以外は、図１に示す実施例１の防振ゴムＡと同じである。当然ながら隅Ｒ面１６も存在しない。 Example 3
The anti-vibration rubber A according to the third embodiment is based on the anti-vibration rubber A (see FIG. 1) of the first embodiment. As shown in FIG. 3, the chamfered portion 10 applied to the outer cylinder 2 is a boss portion 2A. Is changed from the inner corner of the lower end to the upper corner of the outer peripheral end of the outward flange portion 2B, and the diameter of the outward flange portion 2B of the outer cylinder 2 is reduced so that the flange wrap portion 3F without the root portion 17 is provided. 1 is the same as the anti-vibration rubber A of Example 1 shown in FIG. Of course, the corner R surface 16 does not exist.

〔実施例４〕
実施例４による防振ゴムＡは、実施例３の防振ゴムＡ（図３参照）を基本としており、図４に示すように、ゴム部３におけるボス回り込み部３Ｂが省略されて、ボス部２Ａの内周面４（外表面４）に沿う薄膜内周部３ｎだけが存在する形状に形成されている。それ以外は図３に示す実施例３の防振ゴムＡと同じである。この場合、薄膜内周部３ｎの底面である中間底面３ｃは、ボス部２Ａの下端面２ａと同一面となる状態に仕上げられている。 Example 4
The anti-vibration rubber A according to the fourth embodiment is based on the anti-vibration rubber A according to the third embodiment (see FIG. 3). As shown in FIG. 4, the boss wraparound portion 3B in the rubber portion 3 is omitted, and the boss portion It is formed in a shape in which only the thin film inner peripheral portion 3n along the inner peripheral surface 4 (outer surface 4) of 2A exists. Other than that is the same as the anti-vibration rubber A of Example 3 shown in FIG. In this case, the intermediate bottom surface 3c, which is the bottom surface of the thin film inner peripheral portion 3n, is finished so as to be flush with the lower end surface 2a of the boss portion 2A.

〔実施例５〕
実施例５による防振ゴムＡは、実施例３の防振ゴムＡ（図３参照）を基本としており、図５に示すように、ゴム部３として、その底面が外向きフランジ部２Ｂの底面と同じ高さレベルとなる状態で角逃げ湾曲部９を埋め尽くす充填部３ｊが形成されている。それ以外は図３に示す実施例３の防振ゴムＡと同じである。 Example 5
The anti-vibration rubber A according to Example 5 is based on the anti-vibration rubber A of Example 3 (see FIG. 3). As shown in FIG. 5, the rubber part 3 has a bottom surface that is the bottom surface of the outward flange part 2B. The filling portion 3j is formed so as to completely fill the corner relief curved portion 9 in a state where the height level is the same as that in FIG. Other than that is the same as the anti-vibration rubber A of Example 3 shown in FIG.

〔実施例６〕
実施例６による防振ゴムＡは、実施例１の防振ゴムＡ（図１参照）を基本としており、図６（ａ），（ｂ）に示すように、フランジ回り込み部３Ｆにおけるフランジ部分１９とボス回り込み部３Ｂにおける筒状部分３ｔとが周方向に間欠的に形成されている以外は、図１に示す実施例１による防振ゴムＡと同じである。尚、実施例６による防振ゴムＡの断面図は図１と同じに付き省略する。 Example 6
The anti-vibration rubber A according to the sixth embodiment is based on the anti-vibration rubber A of the first embodiment (see FIG. 1), and as shown in FIGS. 6 (a) and 6 (b), the flange portion 19 in the flange wrap portion 3F. 1 and the cylindrical portion 3t in the boss wraparound portion 3B are the same as those of the anti-vibration rubber A according to the first embodiment shown in FIG. Incidentally, the cross-sectional view of the anti-vibration rubber A according to Example 6 is the same as FIG.

フランジ部分１９が全周に形成されている場合では、実機に締付け装着されると、圧縮されたフランジ部分１９は径方向に逃げ変形するしかないが、本実施例６による防振ゴムＡでは、隣合うフランジ部分１９，１９どうしの間には空間部が存在するから、実機への圧接装着状態においてフランジ部分１９が無理なく横拡がり変形（周方向に拡がり変形）することができる。 In the case where the flange portion 19 is formed on the entire circumference, when the flange portion 19 is tightened and attached to the actual machine, the compressed flange portion 19 has no choice but to deform in the radial direction. Since there is a space between the adjacent flange portions 19, 19, the flange portion 19 can be laterally expanded and deformed (expanded and deformed in the circumferential direction) in a state of being press-fitted to the actual machine.

次に、上述の防振ゴムＡを用いた防振構造の具体例を、使用例１〜４として説明する。尚、以下の使用例において用いられる防振ゴムＡは、便宜上、実施例１による防振ゴムＡとしてあるが、実施例２や３、或いはその他の実施例による防振ゴムＡを用いても良いのは言うまでもない。 Next, specific examples of the vibration-proof structure using the above-described vibration-proof rubber A will be described as usage examples 1 to 4. The anti-vibration rubber A used in the following use examples is, for convenience, the anti-vibration rubber A according to Example 1. However, the anti-vibration rubber A according to Examples 2 and 3 or other examples may be used. Needless to say.

〔使用例１〕
使用例１は、図７に示すように、自動車の車体フレーム等の支持部材２１と、エンジン等の振動源に固定される防振部材２２と、に跨って１個の防振ゴムＡが取付けられる構成である。具体的には、厚板状の支持部材２１の装着孔２１Ａに外筒２のボス部２Ａを挿入し、支持部材２１の上面２１ａに外向きフランジ部２Ｂを載せ付け、内筒１の上面１ａに防振部材２２を、かつ、装着孔２１Ａの径よりも大きな外径を有する金属円板で成るワッシャ２３を内筒１の下面１ｂにそれぞれあてがった状態で、防振部材２２と内筒１とワッシャ２３との三者を貫通する取付ボルト２４とナット２５とで締付け固定する。尚、この使用例１では、ボス部２Ａの下側にまでゴム部３が回り込むタイプの防振ゴムＡを用いているが、回り込まないタイプのものでも良い。 [Usage example 1]
In use example 1, as shown in FIG. 7, one anti-vibration rubber A is attached across a support member 21 such as a body frame of an automobile and a vibration isolation member 22 fixed to a vibration source such as an engine. It is the structure which is made. Specifically, the boss portion 2A of the outer cylinder 2 is inserted into the mounting hole 21A of the thick plate-like support member 21, the outward flange portion 2B is mounted on the upper surface 21a of the support member 21, and the upper surface 1a of the inner cylinder 1 The vibration isolator 22 and the inner cylinder 1 are attached to the lower surface 1b of the inner cylinder 1 with the vibration isolator 22 and a washer 23 made of a metal disc having an outer diameter larger than the diameter of the mounting hole 21A. And the washer 23 are fastened and fixed with mounting bolts 24 and nuts 25 that pass through the three members. In this usage example 1, the anti-vibration rubber A is used in which the rubber part 3 wraps around to the lower side of the boss part 2A.

この使用例１の構造では、前後左右及び下方にはゴム部３の弾性による防振作用が支持部材２１に発揮され、ワッシャ２３と支持部材２１との当接により、防振部材２２の上方の動きは牽制阻止されるように機能する。外筒２に形成された角逃げ湾曲部９により、支持部材２１の装着孔２１Ａに臨む縁角部２１ｂが、プレス加工等の穿孔加工後に面取り等の仕上げ加工が行われない粗仕上げ状態（バリが存在するような状態）であっても、乗り上がり等の不都合なく嵌合できるようにしてある。また、角逃げ湾曲部９は、外筒２の上下左右のバネ定数を変える機能もある。 In the structure of this usage example 1, the vibration isolating action due to the elasticity of the rubber part 3 is exerted on the support member 21 in the front and rear, right and left, and below, and the contact between the washer 23 and the support member 21 causes the Movement works to be restrained. Due to the corner relief curved portion 9 formed in the outer cylinder 2, the edge corner portion 21b facing the mounting hole 21A of the support member 21 is in a rough finish state in which finishing processing such as chamfering is not performed after punching processing such as pressing. In such a state, the fitting can be performed without any inconvenience such as climbing. Further, the corner relief curved portion 9 also has a function of changing the upper, lower, left and right spring constants of the outer cylinder 2.

尚、予め予備荷重（プリロード）をゴム部３に持たせて、エンジン等の振動源の重量が作用する使用状態でも、図７のようにワッシャ２３が支持部材２１に当接する構造が可能である。また、図示は省略するが、振動源の重量が作用した使用状態では、ワッシャ２３と支持部材２１との間に若干の間隙が生じるように設定することも可能である。さらに、図７の２１が振動源側の防振部材に、かつ、図７の２２が支持部材とする前述とは逆の構成を採ることも可能である。 In addition, a structure in which the washer 23 abuts against the support member 21 as shown in FIG. 7 is possible even when the rubber portion 3 is preliminarily provided with a preload and the weight of a vibration source such as an engine is applied. . Although not shown, it is possible to set so that a slight gap is generated between the washer 23 and the support member 21 in a use state in which the weight of the vibration source is applied. Furthermore, it is also possible to adopt a configuration opposite to that described above in which 21 in FIG. 7 is a vibration isolator on the vibration source side and 22 in FIG. 7 is a support member.

〔使用例２〕
使用例２は、図８に示すように、支持部材２１と、これの下側に配されるワッシャ２３との間にゴム等の弾性部材２４を介装させた点以外は、図７に示す使用例１のものと同じ構成である。弾性部材２４は、ワッシャ２３の外周に沿って全周に亘って形成されるリング状のもので良いし、周方向に間欠的に配備される複数個のものでも良い。このように、弾性部材２４を介装したことにより、前後左右、及び下方に対する防振作用に加えて、上方に対しても防振作用を生じさせることができるので、構造上、上方にも防振が必要であるとか、より防振条件の厳しい箇所といった場合に好適な構成となっている。また、図８の２１が振動源側の防振部材に、かつ、図８の２２が支持部材とする逆の構成を採ることも可能である。 [Usage example 2]
As shown in FIG. 8, Usage Example 2 is shown in FIG. 7 except that an elastic member 24 such as rubber is interposed between the support member 21 and a washer 23 disposed below the support member 21. The configuration is the same as that of the first usage example. The elastic member 24 may be a ring-shaped member formed over the entire circumference along the outer periphery of the washer 23, or may be a plurality of members provided intermittently in the circumferential direction. In this way, by interposing the elastic member 24, in addition to the anti-vibration action for the front, rear, left and right, and the lower part, the anti-vibration action can also be generated for the upper part. This configuration is suitable for cases where vibration is required or where vibration isolation conditions are more severe. Further, it is possible to adopt a reverse configuration in which 21 in FIG. 8 is a vibration isolator on the vibration source side and 22 in FIG. 8 is a support member.

〔使用例３〕
使用例３は、図９に示すように、より厚肉の支持部材２１の装着孔２１Ａに一対の防振ゴムＡ，Ａを向い合せ状態で配備して用いる構成である。つまり、図７に示す使用例１における支持部材２１とワッシャ２３との上下間に、上下逆さま状態の防振ゴムＡを介装したような構造である。この構造では、上下の内筒１，１どうしを密着させて取付ボルト２４で締付けた状態では、各外筒２，２においてはそれらのボス部２Ａ，２Ａどうしの間に間隙が存在するように設定されており、支持部材２１を確実に上下から挟み込めるようになっている。 [Usage example 3]
As shown in FIG. 9, the usage example 3 is a configuration in which a pair of anti-vibration rubbers A and A are disposed and used in the mounting hole 21A of the thicker support member 21 facing each other. That is, it is a structure in which the anti-vibration rubber A in an upside down state is interposed between the upper and lower sides of the support member 21 and the washer 23 in the first usage example shown in FIG. In this structure, when the upper and lower inner cylinders 1 and 1 are brought into close contact with each other and tightened with the mounting bolt 24, the outer cylinders 2 and 2 have a gap between their boss portions 2A and 2A. It is set so that the support member 21 can be securely sandwiched from above and below.

この使用例３では、計２個の防振ゴムＡを上下に配して用いるので、前後左右及び上下の三次元方向に十分な防振が行えるとともに、各防振ゴムＡは互いに同じ部品で済む利点がある。また、図示は省略するが、図９の２１が振動源側の防振部材に、かつ、図９の２２が支持部材とする逆の構成を採ることも可能である。 In this usage example 3, a total of two anti-vibration rubbers A are used in the vertical direction, so that sufficient anti-vibration can be achieved in the front and rear, left and right and upper and lower three-dimensional directions, and each anti-vibration rubber A is the same component. There is an advantage to end. Although not shown, it is possible to adopt a reverse configuration in which 21 in FIG. 9 is a vibration isolator on the vibration source side and 22 in FIG. 9 is a support member.

〔使用例４〕
使用例４は、図１０に示すように、一対の防振ゴムＡ，Ａを、これらの間に防振部材２２を介して背中合わせ状態で用いる構成である。即ち、外筒２のボス部２Ａが嵌入される装着孔２１Ａが形成された支持部材２１が上下一対設けられており、上側の防振ゴムＡは逆さ向きで、かつ、下側の防振ゴムＡは通常姿勢とされ、それぞれの内筒１，１間に防振部材２２を差し込むとともに、上下一対のワッシャ２３，２３を用いて取付ボルト２４及びナット２５で締付け固定される。この使用例４においても、使用例３のものと同様に、前後左右及び上下の三次元方向に十分な防振が行える。また、図示は省略するが、図１０の２１が振動源側の防振部材に、かつ、図１０の２２が支持部材とする逆の構成を採ることも可能である。 [Usage example 4]
As shown in FIG. 10, the usage example 4 is a configuration in which a pair of anti-vibration rubbers A and A are used in a back-to-back state via an anti-vibration member 22 therebetween. In other words, a pair of upper and lower support members 21 having mounting holes 21A into which the boss portions 2A of the outer cylinder 2 are inserted are provided, and the upper vibration isolating rubber A is upside down and the lower vibration isolating rubber. A is in a normal posture, and the vibration isolation member 22 is inserted between the inner cylinders 1 and 1 and is fastened and fixed with a mounting bolt 24 and a nut 25 using a pair of upper and lower washers 23, 23. Also in this usage example 4, as in the usage example 3, sufficient vibration isolation can be performed in the front and rear, right and left, and top and bottom three-dimensional directions. Although illustration is omitted, it is also possible to adopt a reverse configuration in which 21 in FIG. 10 is a vibration isolator on the vibration source side and 22 in FIG. 10 is a support member.

〔変形例１〜６〕
次に、実施例１〜６の防振ゴムの変形例１〜６について説明する。図１１〜図１５に示すように、ゴム部３の外周面（外周側面）３ｇの全周に亘って断面円弧の窪みＦが形成されており、この窪みＦの断面円弧の半径Ｌは、ゴム部３の厚みをＨとしたときに、
Ｈ／５≦Ｌ≦５Ｈ……（Ａ）
であるとともに、窪みの深さをＷとしたときに、
１ｍｍ≦Ｗ≦Ｈ／２……（Ｂ）
であるように設定されている。 [Modifications 1-6]
Next, modified examples 1 to 6 of the vibration-proof rubber of Examples 1 to 6 will be described. As shown in FIGS. 11 to 15, a recess F having a cross-sectional arc is formed over the entire circumference of the outer peripheral surface (outer peripheral side surface) 3 g of the rubber portion 3. When the thickness of the part 3 is H,
H / 5 ≦ L ≦ 5H (A)
And when the depth of the depression is W,
1mm ≦ W ≦ H / 2 (B)
Is set to be.

上記式（Ａ）、（Ｂ）により、圧縮荷重が加えられる前の初期状態でゴム部３の外周面３ｇの自由表面積が大きくなって、大荷重が防振ゴムＡに付加されるときでも、ゴム部３の外周面３ｇの引張り応力が分散されるので、しわやピンホールの発生を防止することができ、ゴム部３の許容歪みを超えることもなく、耐久性の向上に寄与できる利点が追加される。 According to the above formulas (A) and (B), even when the free surface area of the outer peripheral surface 3g of the rubber part 3 is increased in the initial state before the compressive load is applied, and a large load is applied to the anti-vibration rubber A, Since the tensile stress of the outer peripheral surface 3g of the rubber part 3 is dispersed, the generation of wrinkles and pinholes can be prevented, and there is an advantage that it can contribute to the improvement of durability without exceeding the allowable strain of the rubber part 3. Added.

図１１に示す変形例１による防振ゴムＡは、実施例１の防振ゴム（図１参照）を基本としたものであり、図１２に示す変形例２による防振ゴムＡは、実施例２の防振ゴム（図２参照）を基本としたものであり、図１３に示す変形例３による防振ゴムＡは、実施例３の防振ゴム（図３参照）を基本としたものであり、図１４に示す変形例４による防振ゴムＡは、実施例４の防振ゴム（図４参照）を基本としたものであり、図１５に示す変形例５による防振ゴムＡは、実施例５の防振ゴム（図５参照）を基本としたものである。尚、実施例６の防振ゴム（図６参照）を基本とした変形例６による防振ゴムＡの断面形状は、変形例１の断面形状（図１１参照）と同じに付き、図１１で代用して専用の図は省略する。 The anti-vibration rubber A according to the first modification shown in FIG. 11 is based on the anti-vibration rubber according to the first embodiment (see FIG. 1). The anti-vibration rubber A according to the second modification shown in FIG. The anti-vibration rubber A according to the third modification shown in FIG. 13 is based on the anti-vibration rubber according to the third embodiment (see FIG. 3). Yes, the anti-vibration rubber A according to the fourth modification shown in FIG. 14 is based on the anti-vibration rubber according to the fourth embodiment (see FIG. 4). The anti-vibration rubber A according to the fifth modification shown in FIG. This is based on the vibration-proof rubber of Example 5 (see FIG. 5). Note that the cross-sectional shape of the anti-vibration rubber A according to Modification 6 based on the anti-vibration rubber of Example 6 (see FIG. 6) is the same as the cross-sectional shape of Modification 1 (see FIG. 11). Instead, a dedicated figure is omitted.

防振ゴムの構造を示す断面図（実施例１）Sectional view showing structure of anti-vibration rubber (Example 1) 防振ゴムの構造を示す断面図（実施例２）Sectional drawing which shows structure of anti-vibration rubber (Example 2) 防振ゴムの構造を示す断面図（実施例３）Sectional view showing structure of vibration-proof rubber (Example 3) 防振ゴムの構造を示す断面図（実施例４）Sectional drawing which shows structure of anti-vibration rubber (Example 4) 防振ゴムの構造を示す断面図（実施例５）Sectional view showing structure of vibration-proof rubber (Example 5) 防振ゴムの構造を示し、（ａ）は半欠截底面図、（ｂ）は逆さま状態における上方から見た斜視図（実施例６）The structure of an anti-vibration rubber is shown, (a) is a half-notched bottom view, and (b) is a perspective view seen from above in an upside-down state (Example 6). 防振ゴムの使用例１を示す断面図Sectional drawing which shows usage example 1 of anti-vibration rubber 防振ゴムの使用例２を示す断面図Sectional drawing which shows usage example 2 of anti-vibration rubber 防振ゴムの使用例３を示す断面図Sectional drawing which shows usage example 3 of anti-vibration rubber 防振ゴムの使用例４を示す断面図Sectional drawing which shows the usage example 4 of vibration-proof rubber 変形例１及び６による防振ゴムを示す断面図Sectional drawing which shows the vibration-proof rubber by the modification 1 and 6 変形例２による防振ゴムを示す断面図Sectional drawing which shows the vibration-proof rubber by the modification 2 変形例３による防振ゴムを示す断面図Sectional drawing which shows the vibration-proof rubber by the modification 3 変形例４による防振ゴムを示す断面図Sectional drawing which shows the vibration-proof rubber by the modification 4 変形例５による防振ゴムを示す断面図Sectional drawing which shows the vibration proof rubber by the modification 5 従来における防振ゴムの使用例を示す要部の側面図Side view of the main part showing an example of using conventional anti-vibration rubber

Explanation of symbols

１内筒
２外筒
２ｂ外向きフランジ部の内面
２Ａボス部
２Ｂ外向きフランジ部
３ゴム部
３Ｂボス回り込み部
３Ｆフランジ回り込み部
４外周面
１９フランジ部分
ｄフランジ部分の径方向幅
ｔフランジ部分の厚み
ｒゴム部の外径
ｈゴム部の厚み
Ａ防振ゴム
Ｐ軸心 DESCRIPTION OF SYMBOLS 1 Inner cylinder 2 Outer cylinder 2b Inside surface of outward flange part 2A Boss part 2B Outward flange part 3 Rubber part 3B Boss wrap part 3F Flange wrap part 4 Outer peripheral surface 19 Flange part d Radial width of flange part t Thickness of flange part r Outer diameter of rubber part h Thickness of rubber part A Anti-vibration rubber P Shaft center

Claims

An outer cylinder comprising an inner cylinder, a boss portion having an axial center along the axial direction of the inner cylinder, and an outward flange portion along the radial direction of the inner cylinder, and an inner peripheral surface of the boss portion and the flange portion A rubber part that is interposed between the outer surface and the inner cylinder and integrates the two cylinders by vulcanization adhesion,
The rubber part is an anti-vibration rubber set in a shape that extends around an outer end of the outward flange part and extends to an inner surface of the outward flange part.

2. The anti-vibration rubber according to claim 1, wherein a flange wraparound portion that extends to the inner surface of the outward flange portion in the rubber portion is formed in an annular shape over the entire circumference of the outer peripheral portion of the inner surface.

2. The anti-vibration rubber according to claim 1, wherein the flange wrapping portion extending to the inner surface of the outward flange portion in the rubber portion is intermittently formed in the circumferential direction on the outer peripheral portion of the inner surface.

When the thickness t of the flange portion along the inner surface of the outward flange portion of the flange wrap-around portion and the radial width d of the flange portion are r and the thickness of the rubber portion is h. The anti-vibration rubber according to claim 2 or 3, defined by the following formulas (1) and (2):
t ≦ 0.1h (1)
d ≦ 0.15r (2)

The anti-vibration rubber according to any one of claims 1 to 4, wherein the rubber portion is formed in a shape that wraps around an end face of the boss portion.

The anti-vibration rubber according to claim 5, wherein the rubber part extends to an outer peripheral surface of the boss part.

The anti-vibration rubber according to claim 6, wherein a boss wraparound portion that extends to an outer peripheral surface of the boss portion in the rubber portion is formed intermittently in a circumferential direction of the boss portion.