JPS60179542A - Liquid containing bushing - Google Patents
Liquid containing bushingInfo
- Publication number
- JPS60179542A JPS60179542A JP3476284A JP3476284A JPS60179542A JP S60179542 A JPS60179542 A JP S60179542A JP 3476284 A JP3476284 A JP 3476284A JP 3476284 A JP3476284 A JP 3476284A JP S60179542 A JPS60179542 A JP S60179542A
- Authority
- JP
- Japan
- Prior art keywords
- fluid
- communication path
- metal fitting
- orifice
- cylindrical metal
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
- F16F13/1427—Units of the bushing type, i.e. loaded predominantly radially characterised by features of flexible walls of equilibration chambers; decoupling or self-tuning means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、ゴム弾性体の弾性変形と非圧縮性流体の粘性
抵抗（流通抵抗）とによって防振機能を果たす流体入り
ブツシュに係り、特に振動モードに応じた良好な非線形
特性を示す流体入りブツシュに関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a fluid-filled bushing that achieves a vibration damping function by using the elastic deformation of a rubber elastic body and the viscous resistance (flow resistance) of an incompressible fluid, and particularly relates to a fluid-filled bushing that achieves a vibration damping function by using elastic deformation of a rubber elastic body and viscous resistance (flow resistance) of an incompressible fluid. The present invention relates to a fluid-filled bushing exhibiting nonlinear characteristics.
従来より、自動車の車体に対して差動装置や車輪等をむ
架するために、各種のアーム、ロンド。Conventionally, various types of arms and ronds have been used to mount differential gears, wheels, etc. to the car body.
リンク等の懸架部材が各種方向に揺動可能に設けられ、
それら懸架部材の両端の枢着部には、一般に防振のため
にサスペンションブツシュが組み込まれるのが普通であ
る。また、エンジンと車体との間に配設されて振動の伝
達を抑制するようにしたエンジンマウントも用いられて
いる。Suspension members such as links are provided so as to be swingable in various directions,
Suspension bushings are generally incorporated into the pivot joints at both ends of these suspension members for vibration isolation. Also used are engine mounts that are disposed between the engine and the vehicle body to suppress the transmission of vibrations.
ところで、このようなサスペンションブツシュ。By the way, such a suspension bush.
エンジンマウント等の防振支持体たるブ、７シユは、互
いに同心的に配置された内筒金具と外筒金具との間に、
ゴム弾性体が介在せしめられた構造を有し、このゴム弾
性体の弾性変形によって防振機能を果たすようになって
いるが、近年になって、流体の粘性抵抗を利用すること
により、ブツシュの減衰機能を高めるようにした複合ブ
ツシュ、換言すれば、流体入りブツシュが提案されるに
至った。The anti-vibration support for the engine mount, etc., is provided between an inner cylinder metal fitting and an outer cylinder metal fitting that are arranged concentrically with each other.
It has a structure in which a rubber elastic body is interposed, and the vibration damping function is achieved by the elastic deformation of this rubber elastic body.In recent years, however, by utilizing the viscous resistance of fluid, Composite bushings, in other words, fluid-filled bushings, have been proposed to enhance the damping function.
このような流体入りブツシュは、上記ゴム弾性体に所定
の非圧縮性流体がそれぞれ封入される１組の流体室が形
成され、かつ、それら流体室間を相互に連通せしめる連
通路が設けられた構造を有し、加振入力時において、一
方の流体室内に封入された流体が」二記連通路（オリフ
ィス）を通じて他方の流体室内に流通する際に発生する
粘性抵抗により、振動に対する減衰作用を果たさせるよ
うにしたものである。In such a fluid-filled bushing, a pair of fluid chambers each filled with a predetermined incompressible fluid are formed in the rubber elastic body, and a communication path is provided to allow the fluid chambers to communicate with each other. The structure has a damping effect against vibrations due to the viscous resistance that occurs when the fluid sealed in one fluid chamber flows through the two communication passages (orifice) into the other fluid chamber during vibration input. It was designed to be fulfilled.
しかしながら、かがる従来の流体入りブツシュにおいて
は、連通路（オリフィス）の絞り皿を如何に定めるかが
非糸′に難しく、低周波振動域において高Ｕを得るべく
連通路の径を小さくすると、そのことが高周波振動域で
の振動の遮断に妨げとなり（振動伝達力が上がってしま
う）、逆に、高周波域での振動伝達力を低く押さえるべ
く連通路の径を大きくすると、低周波振動に対する減衰
効果が小さくなってしまう問題があった。However, in conventional fluid-filled bushings that can be bent, it is difficult to determine the constriction plate of the communication passage (orifice), and it is difficult to determine the diameter of the communication passage in order to obtain a high U in the low frequency vibration range. This hinders the isolation of vibrations in the high frequency range (the vibration transmission force increases), and conversely, if the diameter of the communication path is increased to keep the vibration transmission force low in the high frequency range, low frequency vibrations There was a problem that the damping effect for
また、大変位をもたらす振動荷重が作用する場合には、
前記外筒金具と円筒金具との大きな相対変位、ひいては
ゴム弾性体の過大変形を防止するることが望ましいので
あるが、従来の流体入りブツシュではそれが殆ど期待で
きない。もっとも、連通路の径をできる限り小さくして
、上記流体に与える粘性抵抗を高めれば、成る程度はゴ
ム弾性体の過大変形を抑えることが可能ではあるが、特
に衝撃的な大荷重の作用時にはそれでも不充分であり、
しかも高周波域での振動の伝達力を下げる必要上、連通
路の径を余りに小さくすることはできないから、ゴムｉ
ｉ！ｉｊ性体の過大変形を防止することは、非常に期待
薄と言わざるを得ないのである。In addition, when vibration loads that cause large displacements are applied,
Although it is desirable to prevent large relative displacement between the outer cylindrical metal fitting and the cylindrical metal fitting, and thus excessive deformation of the rubber elastic body, this is hardly expected with conventional fluid-filled bushings. However, if the diameter of the communicating path is made as small as possible to increase the viscous resistance given to the fluid, excessive deformation of the rubber elastic body can be suppressed to a certain extent, but especially when a large impact load is applied. However, it is still insufficient;
Moreover, since it is necessary to reduce the transmission force of vibration in the high frequency range, the diameter of the communication passage cannot be made too small, so rubber i
i! It must be said that there is very little hope of preventing excessive deformation of the ij-like body.
本発明は、以上のような事情を背景としてなされたもの
であり、その目的とするところは、高周波域での振動の
伝達力を低く保ちながら、低周波域での高い減衰力をｉ
Ｕることができ、しかも衝撃的な加振力に対して、ゴム
弾性体の過大変形を確実に防止することのできる流体入
りプツシ１を提供することにある。The present invention was made against the background of the above-mentioned circumstances, and its purpose is to maintain a high damping force in the low frequency range while keeping the vibration transmission force low in the high frequency range.
To provide a fluid-filled pusher 1 capable of reliably preventing excessive deformation of a rubber elastic body against an impulsive excitation force.
このような目的を達成すべく、本発明にあっζは、前述
のような内筒金具、外筒金具およびゴＪ、弾性体と、１
組の流体室およびそれら流体室を相互に連通せしめる連
通路とが設けられた構造の流体入りブツシュにおいて、
Ｉ１１上記流体室内に、円筒金具に固定され且つ内筒金
具から外筒金具に延びる所定高さのストッパ手段を設け
て、そのストッパ手段に上記外筒金具が当接し得るよう
にすると共に、（ｂ）上記連通路に、その連通路を遮断
する位置と遮断しない位置とに移動可能であって、前記
流体の流通に伴う押圧力によってその連通路を遮断する
位置に移動せしめられる可動部材を設け、（Ｃ１更に、
その可動部材によって前記連通路が遮断された状態にお
いても、前記双方の流体室同士を相互に、且つ上記流体
の流通に対して該連通路より大きな流通抵抗を与える状
態で連通せしめるオリフィス手段を設けたのである。In order to achieve such an object, the present invention includes the above-mentioned inner cylinder metal fitting, outer cylinder metal fitting, gong J, elastic body, and the like.
In a fluid-filled bushing having a structure in which a set of fluid chambers and a communication path for making the fluid chambers communicate with each other,
I11 A stopper means fixed to the cylindrical fitting and having a predetermined height extending from the inner cylindrical fitting to the outer cylindrical fitting is provided in the fluid chamber so that the outer cylindrical fitting can come into contact with the stopper means, and (b) ) a movable member is provided in the communicating path, which is movable between a position where the communicating path is blocked and a position where the communicating path is not blocked, and which is moved to a position where the communicating path is blocked by a pressing force accompanying the flow of the fluid; (C1 Furthermore,
Orifice means is provided for allowing the two fluid chambers to communicate with each other and in a state that provides greater flow resistance than the communication path to the flow of the fluid even when the communication path is blocked by the movable member. It was.
このようにすれば、高周波振動時には振動振幅が小さい
ので、上記可動部材が連通路を遮１１１ｉするには至ら
ず、双方の流体室に封入された流体が連通路を経て自由
に流通することが許容され、そのために動ばね定数が低
く保たれて、高周波域での振動の伝達力を小さく抑える
ことができる。一方、低周波振動時には振動振幅が大き
いので、流体の押圧力によって上記可動部材が連通路を
遮断する位置に移動せしめられ、その結果、流動する流
体は、その連通路より大きな流通抵抗を与えるオリフィ
ス手段を経なければ両流体室間を相互に流通することが
できない状態となるため、そのオリフィス手段を流通す
る際に生ずる抵抗によって高い減衰力を得ることができ
るのである。In this way, since the vibration amplitude is small during high frequency vibration, the movable member does not block the communication path 111i, and the fluid sealed in both fluid chambers can freely flow through the communication path. Therefore, the dynamic spring constant is kept low, and the vibration transmission force in the high frequency range can be kept small. On the other hand, since the vibration amplitude is large during low frequency vibration, the movable member is moved to a position where it blocks the communication path by the pressing force of the fluid, and as a result, the flowing fluid passes through the orifice which provides greater flow resistance than the communication path. Since the two fluid chambers cannot be mutually communicated without passing through the orifice means, a high damping force can be obtained due to the resistance generated when the fluid flows through the orifice means.
しかも、低周波でｉ＋ｊ撃的な大加振力が作用した場合
にも、その」リフイス手段が流体に与える流通抵抗によ
って、内筒金具と外筒金具との相対的な大変位、ひいて
はゴム弾性体の過大変形が抑制され、更にそのような緩
衝作用が生じた後に、前記ストッパ手段に対して外筒金
具が当接せしめられることにより、ゴム弾性体の過大変
形が確実に防止され得て、その耐久性の向上を図り、ま
た機能部品の干渉の問題等を回避できることとなったの
である。特に、かかる大変位に対してオリフィス手段に
よる緩衝作用の後に、ストッパ手段によって最終的に大
変位が規制されるため、ｆｉｉ 撃が小さく滑らかな状
態で過大変位を確実に阻止することができる。言い換え
れば、ゴム弾性体とストッパ手段と非圧縮性流体との３
者の相剰効果により、非電に滑らかな非線形特性を有し
、且つ高周波域においても、低周波域においても、良好
な防振特性を有する複合的なブツシュを提供することが
可能となったのである。Moreover, even when a large excitation force of i + j impact is applied at low frequency, the flow resistance that the rewiring means gives to the fluid causes a large relative displacement between the inner and outer cylindrical fittings, and eventually the rubber elasticity. After excessive deformation of the rubber elastic body is suppressed and such a buffering effect is generated, the outer cylindrical metal fitting is brought into contact with the stopper means, whereby excessive deformation of the rubber elastic body can be reliably prevented, This made it possible to improve its durability and avoid problems such as interference between functional parts. In particular, after the orifice means acts as a buffer against such large displacement, the stopper means finally restricts the large displacement, so that excessive displacement can be reliably prevented with a small and smooth fii impact. In other words, the rubber elastic body, the stopper means, and the incompressible fluid.
Due to the mutual effect of the two, it has become possible to provide a composite bushing that has non-electrically smooth nonlinear characteristics and good vibration isolation characteristics in both high and low frequency ranges. It is.
以下、本発明を自動車のサスペンションブツシュに適用
した場合の−、二の実施例を図面に基づいて８’（＝細
に説明する。Hereinafter, two embodiments in which the present invention is applied to an automobile suspension bushing will be described in detail with reference to the drawings.
第１図および第２図には、そのようなザスペンションゾ
ソシ：ＬｌＯが示されている。このブツシュ１０は、そ
の最内側に比較的厚肉の内筒金具１２を備え、その外側
には外筒金具１４が所定比離隔てて同心的に配置され、
かつ、これら内筒金具１２と外筒金具１４との間にゴム
弾性体として機能する円環状のゴムスリーブ１６が同心
的に組み込まれている。このゴムスリーブ１６は、その
内周面が内筒金具１２に加硫接着される一方、゛外周面
には円筒状の金属リング１８が加硫接着されている。さ
らに、このゴムスリーブ１６には、内筒金具１２を挟ん
で互いに対称な位置に、周方向に延びる二つの凹所２０
が外周面にそれぞれ開口するように形成されており、こ
れら凹所２０の開口部に対応して上記金属リング１８に
は、窓部２２がそれぞれ形成されている。In FIGS. 1 and 2, such a suspension is shown. This bushing 10 has a relatively thick inner cylindrical metal fitting 12 on its innermost side, and an outer cylindrical metal fitting 14 is arranged concentrically at a predetermined distance on the outside thereof.
Moreover, an annular rubber sleeve 16 functioning as a rubber elastic body is concentrically assembled between the inner cylindrical metal fitting 12 and the outer cylindrical metal fitting 14. The inner peripheral surface of the rubber sleeve 16 is vulcanized and bonded to the inner cylindrical metal fitting 12, while a cylindrical metal ring 18 is vulcanized and bonded to its outer peripheral surface. Furthermore, this rubber sleeve 16 has two recesses 20 extending in the circumferential direction at mutually symmetrical positions with the inner cylinder fitting 12 in between.
are formed to open on the outer circumferential surface, and windows 22 are formed in the metal ring 18 corresponding to the openings of these recesses 20, respectively.
一方、この全都リング１８の外側に位置する外筒金具１
４は、その内周面に薄いゴム層２４を一体的に備え、こ
のゴム層２４を介して金属リング１８の外周面に密着さ
せられるとともに、両ｆ’７ｊ：ｌの周縁部が金属リン
グ１８に対してカシメられており、その結果、各凹所２
０の開口部が液密に塞がれて互いに対称的な１組の流体
室２６．２６が画成されている。そして、こうして画成
された流体室２６．２６内には、例えばポリアルキレン
ゲリコール、シリコーン油、あるいは水等の所定の非圧
縮性流体（以下、単に流体という）がそれぞれ封入され
ている。On the other hand, the outer cylinder metal fitting 1 located on the outside of this Zento ring 18
4 is integrally provided with a thin rubber layer 24 on its inner peripheral surface, and is brought into close contact with the outer peripheral surface of the metal ring 18 via this rubber layer 24, and the peripheral edges of both f'7j:l are attached to the metal ring 18. As a result, each recess 2
0 openings are fluid-tightly closed to define a pair of mutually symmetrical fluid chambers 26,26. A predetermined incompressible fluid (hereinafter simply referred to as fluid) such as polyalkylene gellicol, silicone oil, or water is sealed in each of the fluid chambers 26 and 26 thus defined.
また、内筒金具１２の軸方向の中間部には、金属製のブ
ロック体２８が中心孔において圧入され、内筒金具１２
と一体化されている。このプロ・２り体２８は、内筒金
具１２の半径方向の両側にそれぞれ突出する一対のスト
ッパ部３０と、それらストッパ部３０とは内筒金具１２
を挟んで直角な方向にそれぞれ延びる突出部３２とを備
えて、はぼ十字形の断面形状を有している。各スト・ツ
ノく部３０は、前記１組の流体室２６内にそれぞれ位置
せしめられ、内筒金具１２の外周面から外筒金具１４の
内壁面に延びる所定の高さを有し、その先端面は外↑６
Ｊ金具Ｉ４の内壁面にほぼ対応する円筒面状に形成され
、かつ、その表面にゴム層３４が固着されてストソバ面
を構成している。そして、これらストッパ部３０のスト
ッパ面が、内筒金具１２と外筒金具１４とが同心的な状
態において、外筒金具１４の内壁面にそれぞれ等しい距
離を隔てて対向さ−Ｕられ、双方の金具１２および１４
間に半径方向の大きな相対変位が生じた時に、外筒金具
１４を当接せし、めるストッパ手段を構成しているので
ある。Further, a metal block body 28 is press-fitted into the center hole in the axially intermediate portion of the inner cylinder fitting 12.
It is integrated with. This pro-two body 28 has a pair of stopper portions 30 that protrude from both sides of the inner tube fitting 12 in the radial direction, and these stopper portions 30 are connected to the inner tube fitting 12.
The projecting portions 32 each extend in a direction perpendicular to each other, and have a cross-sectional shape of a cross. Each stop horn portion 30 is located within the pair of fluid chambers 26, has a predetermined height extending from the outer peripheral surface of the inner cylindrical fitting 12 to the inner wall surface of the outer cylindrical fitting 14, and has a predetermined height. Face is outside ↑6
It is formed into a cylindrical surface shape that substantially corresponds to the inner wall surface of the J metal fitting I4, and a rubber layer 34 is fixed to the surface to form a flat surface. Then, the stopper surfaces of these stopper parts 30 are opposed to the inner wall surface of the outer cylinder fitting 14 at an equal distance apart from each other when the inner cylinder fitting 12 and the outer cylinder fitting 14 are in a concentric state. Metal fittings 12 and 14
This constitutes a stopper means that brings the outer cylindrical metal fitting 14 into contact and stops when a large relative displacement in the radial direction occurs between the two.
一方、ブロック体２８の各突出部３２は、ストッパ部３
０の高さ方向とは直角な両側方向に延びており、コムス
リーブ１６によって取り即まれ、それに加硫接着されて
いるが、各々の突出部３２には、内筒金具１２・外周面
にまたがる矩形断面の連通孔３（ｉ、３６が形成されて
いる。これらの連通孔３６は、ストソバ部３０の高さ方
向と平行な方向に各突出部３２を貫通して設けられ、前
記双方の流体室２６．２６を相互に連通せしめる連通路
の役割を果たしている。On the other hand, each protruding portion 32 of the block body 28 is connected to the stopper portion 3
It extends in both directions perpendicular to the height direction of 0, is surrounded by the comb sleeve 16, and is vulcanized and bonded to it. Communication holes 3 (i, 36) with a rectangular cross section are formed.These communication holes 36 are provided to penetrate each protrusion 32 in a direction parallel to the height direction of the soba part 30, and are arranged to pass through each protrusion 32 in a direction parallel to the height direction of the soba part 30. It serves as a communication path that allows the chambers 26, 26 to communicate with each other.
そして、各連通孔３６には、可動部材として機能するゴ
ム製の可動体３８．３８がそれぞれ配設されている。こ
の可動体３８は、第３図および第４図から明らかなよう
に、四角柱状の胴部の両端部に環状のフランジ４０．４
０を備え、第２図に示されるように、その四角柱状の１
Ｆｉｌ Ｂ＋＜が連通孔３６内にその四つの孔壁面との
間に径方向の隙間を隔てた状態で位置せしめられるとと
もに、両端のフランジ／１０．４０が突出部３２を両側
から挟む状態で、かつ、連通孔３６の開口周縁部との間
に軸方向の隙間が生じ得る状態で組み込まれている。A rubber movable body 38, 38 functioning as a movable member is disposed in each communication hole 36, respectively. As is clear from FIGS. 3 and 4, this movable body 38 has annular flanges 40.4 at both ends of a quadrangular prism body.
0, and as shown in FIG.
Fil B+< is positioned in the communication hole 36 with a radial gap between it and the four hole wall surfaces, and the flanges /10.40 at both ends sandwich the protrusion 32 from both sides, In addition, it is assembled in such a manner that an axial gap may be generated between the opening peripheral edge of the communication hole 36 and the opening periphery of the communication hole 36 .
したがって、これら可動体３８はその軸方向隙間の範囲
内で連通孔３６の中心線方向に移動することができ、い
ずれかのフランジ４０がその開口周縁部に着座した状態
では、当該連通孔３６を遮断するようになっている。言
い換えれば、その連通孔３６を遮断する位置と遮断しな
い位置とに移動可能とされているのである。Therefore, these movable bodies 38 can move in the direction of the center line of the communication hole 36 within the range of the axial clearance, and when one of the flanges 40 is seated on the peripheral edge of the opening, the movable body 38 can move in the direction of the center line of the communication hole 36. It is designed to be blocked. In other words, it is movable between a position where the communication hole 36 is blocked and a position where it is not blocked.
なお、連通孔３６の両側の開口周縁部は、フランジ４０
の内面を密着状態で着座させるべく、平面状に形成され
ており、また、かかる連通孔３８が金属製のブロック体
２８に形成されているため、ゴノ、スリーブ１６の弾性
変形にかかわらず、その断面寸法が常に一定に保たれ、
可動体３８の円滑な移動が保址される。Note that the opening peripheral portions on both sides of the communication hole 36 are formed by flanges 40.
It is formed into a planar shape so that the inner surface of the gong and sleeve 16 can be seated in close contact with each other, and the communication hole 38 is formed in the metal block body 28, so that regardless of the elastic deformation of the gono and sleeve 16, Its cross-sectional dimensions are always kept constant,
Smooth movement of the movable body 38 is maintained.
さらに、これらの可動体３８には、第３図からも明らか
なように、一方のフランジ４０から胴部の側面を経て他
方のフランジ４０に至るオリフィス溝４２が軸方向に形
成されている。このオリフィス溝４２は、可動体３８が
連通孔３６を遮断した状態においても、前記双方の流体
室２６．２６同士を相互に神道せしめるオリフィス手段
として機能するものであって、その遮断状態において双
方の流体室２６間で前記流体の流通を許容する役割を果
たす。Furthermore, as is clear from FIG. 3, these movable bodies 38 have an orifice groove 42 formed in the axial direction from one flange 40 to the other flange 40 via the side surface of the body. This orifice groove 42 functions as an orifice means that connects the two fluid chambers 26 and 26 to each other even when the movable body 38 blocks the communication hole 36. It plays a role of allowing the fluid to flow between the fluid chambers 26.
可動体３８のフランジ４０が連通孔３６の開口周縁部に
着座していない状態においては、そのフランジ４０と開
口周縁部との間の隙間を経て双方の流体室２６の流体が
相互に流動することが許容されるが、その際に流体に与
えられる粘性抵抗は比較的小さい。これに対して、可動
体３８が連通孔３６を遮断した状態でオリフィス溝４２
を流体が流通せしめられる際には、その流体に与えられ
る粘性抵抗が非遮断状態よりも大きくなるように、オリ
フィス溝４２の断面積等が定められている。When the flange 40 of the movable body 38 is not seated on the periphery of the opening of the communication hole 36, the fluids in both fluid chambers 26 flow into each other through the gap between the flange 40 and the periphery of the opening. is allowed, but the viscous resistance imparted to the fluid is relatively small. On the other hand, with the movable body 38 blocking the communication hole 36, the orifice groove 42
The cross-sectional area of the orifice groove 42 is determined so that when the fluid is allowed to flow through the orifice groove 42, the viscous resistance given to the fluid is greater than in the non-blocked state.
なお、遮断状態においてオリフィス溝４２を流通せしめ
られる流体は、連通孔３６の壁面と可動体３８の壁面と
の間の隙間を流通することも許容されるため、厳密に言
えば、オリフィス溝４２のフランジ４０に形成された部
分が、実質的なオリフィスとしての役割を果たすことと
なる。Note that the fluid that is allowed to flow through the orifice groove 42 in the blocked state is also allowed to flow through the gap between the wall surface of the communication hole 36 and the wall surface of the movable body 38, so strictly speaking, the fluid that is allowed to flow through the orifice groove 42 The portion formed on the flange 40 essentially functions as an orifice.
ところで、このようなサスペンションブツシュ１０は、
例えば次のような工程を経て製作することができる。By the way, such a suspension bushing 10 is
For example, it can be manufactured through the following steps.
まず、内筒金具１２にブロック体２８を圧入して一体化
したものを用意しく連通孔３６はその圧入前もしくは圧
入後に形成し、また、ゴム層３４は予め加硫接着してお
く）１、そして、そのように一体化されたものと前記金
属リング１８とを所定の金型内に同心的にセットして、
それらの間にゴムスリーブ１６を加硫成形し、併せて一
対の凹所２０を形成する。次いで、そのようにして得ら
れた加硫成形品の連通孔３６の各々に、ゴム製の可動体
３８を強制的に弾性変形させつつ組み込む。First, the block body 28 is press-fitted into the inner cylindrical metal fitting 12 and integrated. The communication hole 36 is formed before or after the press-fitting, and the rubber layer 34 is vulcanized and bonded in advance)1. Then, the thus integrated member and the metal ring 18 are set concentrically in a predetermined mold, and
A rubber sleeve 16 is vulcanized and molded between them to form a pair of recesses 20. Next, a movable body 38 made of rubber is inserted into each of the communication holes 36 of the vulcanized molded product thus obtained, while being forcibly elastically deformed.
その際、可動体３８のオリフィス溝４２がそれの弾性変
形を容易にする上で有効となる。一方、外筒金具１４の
内周面には薄いゴム層２４を予め加硫接着しておく。At this time, the orifice groove 42 of the movable body 38 becomes effective in facilitating elastic deformation of the movable body 38. On the other hand, a thin rubber layer 24 is previously vulcanized and bonded to the inner peripheral surface of the outer cylinder fitting 14.
そして、前述のような流体が収容された液槽内において
、可動体３８がそれぞれ組み込まれた加硫成形品（ブツ
シュアッセンブリ）の外側に、外筒金具１４を嵌合する
とともに、その外筒金具１４を外側から絞り加工し、ゴ
ム層２４を介して外筒金具１４の内壁面と金属リング１
８の外周面とを液密に密着させることにより、各流体室
２６を画成すると同時に、その内部に前記流体を封入せ
しめる。その後、外筒金具１４の両端部の周縁をカシメ
加工し、さらに必要に応じて製品の外径を整える絞り加
工を施して、第１図および第２図に示されるようなサス
ペンションブツシュ１０が完成するのである。Then, in the liquid tank containing the fluid as described above, the outer cylindrical fitting 14 is fitted to the outside of the vulcanized molded product (butcher assembly) in which the movable bodies 38 are respectively incorporated, and the outer cylindrical The metal fitting 14 is drawn from the outside, and the inner wall surface of the outer cylinder metal fitting 14 and the metal ring 1 are connected via the rubber layer 24.
By liquid-tightly contacting the outer peripheral surfaces of the fluid chambers 8 and 8, each fluid chamber 26 is defined, and at the same time, the fluid is sealed inside the fluid chamber 26. Thereafter, the peripheral edges of both ends of the outer cylinder fitting 14 are caulked, and if necessary, a drawing process is applied to adjust the outer diameter of the product to obtain the suspension bushing 10 as shown in FIGS. 1 and 2. It will be completed.
このようなサスペンションブツシュ１０は、内筒金具１
２の内側に、例えば車体やアクセルハウジング側の枢軸
が嵌挿せしめられる一方、外筒金具１２が、例えば車体
に対して差動装置や車輪等をＩＹ！、架するアーム、ロ
ンドあるいはリンクのボス部に嵌合された状態で使用さ
れることとなる。Such a suspension bushing 10 has an inner cylinder fitting 1.
For example, a pivot shaft on the vehicle body or the accelerator housing side is inserted into the inside of the IY! It is used in a state where it is fitted to the boss part of a hanging arm, rond or link.
そして、高周波で小変位の振動入力時には、内ｔ、↑１
金具１２と外筒金具１４との相対変位に伴う両流体室２
６．２６の容積変化により、可動体３８の各々がその軸
方向に流体の押圧作用を受けるが、高周波振動時には振
動振幅も小さいため、各可動体３８が連通孔３６を遮断
するには至らず、そのフランジ４０と連通孔３６の開口
周縁部との間の隙間を経て、双方の流体室２６．２６間
で流体の流通がいわば自１１１に召Ｔ１容される状態に
あり、その流通の際に大きな粘性抵抗は生じない。した
がって、当該ブツシュ１０の動ばね常数が低く保たれて
柔かいばね特性が維持されるため、高周波域での振動遮
断特性が高く、言い換えれば、振動伝達力が低（抑えら
れて、こもり音等を効果的に低減させることができる。When inputting vibration with high frequency and small displacement, the inner t, ↑1
Both fluid chambers 2 due to relative displacement between the metal fitting 12 and the outer cylinder metal fitting 14
Due to the volume change in 6.26, each of the movable bodies 38 is subjected to a fluid pressure action in its axial direction, but since the vibration amplitude is small during high-frequency vibration, each movable body 38 does not block the communication hole 36. Through the gap between the flange 40 and the peripheral edge of the opening of the communication hole 36, the fluid is allowed to flow between the two fluid chambers 26 and 26, so to speak. No large viscous resistance occurs. Therefore, the dynamic spring constant of the bushing 10 is kept low and the soft spring characteristics are maintained, so the vibration isolation characteristics in the high frequency range are high. It can be effectively reduced.
一方、低周波で大変位をもたらす振動入力時には、流体
室２６．２６の容積の変化が大きく、各可動体３８が流
体から受ける押圧力も大きくなるま
ため、可動体３８の両？Ｉ：：５のフランジ４０が交互
に連通孔３６の開口周縁部に着座して、そこを遮断する
状態となる。その結果、両流体室２６．２６の流体は、
実質的に可動体３８に形成されたオリフィス溝４２のみ
を介して相互に流通せしめられることとなり、その際に
生ずる粘性抵抗によって低周波振動に対する有効な減衰
力が発生し、発進時や急停車時等に生ずる振幅の大きな
振動を速やかに低減させる効果が得られるのである。On the other hand, when a vibration is input that causes a large displacement at a low frequency, the volume of the fluid chambers 26 and 26 changes greatly, and the pressing force that each movable body 38 receives from the fluid also increases. The flanges 40 of I::5 are alternately seated on the periphery of the opening of the communication hole 36 to block it. As a result, the fluid in both fluid chambers 26.26 is
They are essentially allowed to communicate with each other only through the orifice groove 42 formed in the movable body 38, and the viscous resistance generated at this time generates an effective damping force against low-frequency vibrations, such as when starting or suddenly stopping. This has the effect of quickly reducing large-amplitude vibrations that occur in the
しかも、衝撃的な大荷重が作用した場合には、」二連の
ようにオリフィス溝４２を流体が流通せしめられること
により大きな振動減衰力が生ずる上に、最終的に外筒金
具１４の内壁面がスト・ツバ部３０に当接せしめられる
ことにより、そのような大荷重に基づくゴムスリーブ１
６の過大変形が確実に防止され得て、ゴムスリーブ１６
の耐久性を高めることができる。特に、大変位の振動が
十分に減衰ゼしめられた後に、ストッパ部３０に対、し
て外筒金具１４が当接せしめられるため、当接の衝撃が
小さく、非當に沿らかなストッパ作用が得られるのであ
る。また、ストッパ部３０のスト・７パ面には、ゴム層
３４が固着され、このゴム層３４に外筒金具１４のゴム
層２４が当接・ｕしめられるため、より一層緩衝効果が
高められ、かつ、金属同士の当接が回避される利点があ
る。Moreover, when a large impact load is applied, a large vibration damping force is generated due to the fluid flowing through the orifice grooves 42 in a double series, and the inner wall surface of the outer cylindrical fitting 14 is eventually The rubber sleeve 1 due to such a large load is brought into contact with the strike collar portion 30.
Excessive deformation of the rubber sleeve 16 can be reliably prevented.
can increase the durability of In particular, since the outer cylindrical metal fitting 14 is brought into contact with the stopper portion 30 after the vibration of large displacement has been sufficiently damped, the impact of the contact is small and the stopper action is smooth on the uneven surface. is obtained. Further, a rubber layer 34 is fixed to the stopper surface of the stopper part 30, and the rubber layer 24 of the outer cylinder fitting 14 is brought into contact with this rubber layer 34, so that the cushioning effect is further enhanced. , and there is an advantage that contact between metals can be avoided.
なお、上記可動体３８をゴム製のものに換えて第５図お
よび第６図に示されるように、二つの金属製のブロック
片４４．．４６を連通孔３６の両側から挿入し、突き合
わせ部において圧入することにより一体化した金属製の
可動体３８を採用することも可能である。このような金
属製の可動体３８を採用する場合には、連通孔３６の開
口周縁部にゴム層を固着して密着性を高めることが望ま
しい。In addition, the movable body 38 is replaced with a rubber one, and as shown in FIGS. 5 and 6, two metal block pieces 44. ．． It is also possible to adopt a metal movable body 38 that is integrated by inserting the movable body 46 from both sides of the communication hole 36 and press-fitting it at the abutting portion. When such a metal movable body 38 is employed, it is desirable to fix a rubber layer to the opening periphery of the communication hole 36 to improve adhesion.
また、ゴム製あるいは金属製のいずれにしても、可動片
３８の側部にオリフィス溝４２を形成するのに換えて、
°その中心部に軸方向に貫通するオリフィス孔を形成し
て、それをオリフィス手段として機能させることも可能
である。さらに、第７図に示されるように、可動部材と
して板状の可動板４８を用い、この可動板４８を連通孔
３６の途上に設けられた環状溝５０内に収容して、その
溝幅方向において連通孔３６を遮断する位置と遮断しな
い位置との間で移動、可能なものとし、かつ、その可動
板４８にオリフィス孔５２を形成した態様も採り（ｑる
。 ・
一方、前記オリフィス溝４２やオリフィス孔５２等のオ
リフィス手段は、可動体３８や可動板４８自体に設ける
のに限らず、別の部位に設けることも可能である。その
具体例が第８図および第９図に示されている。Also, instead of forming the orifice groove 42 on the side of the movable piece 38, whether made of rubber or metal,
° It is also possible to form an orifice hole penetrating in the axial direction in the center thereof and to function it as an orifice means. Further, as shown in FIG. 7, a plate-shaped movable plate 48 is used as a movable member, and this movable plate 48 is accommodated in an annular groove 50 provided in the middle of the communication hole 36, and the movable plate 48 is accommodated in the groove width direction. An embodiment is also adopted in which the movable plate 48 is movable between a position where the communicating hole 36 is blocked and a position where it is not blocked, and an orifice hole 52 is formed in the movable plate 48. The orifice means, such as the orifice hole 52, are not limited to being provided in the movable body 38 or the movable plate 48 itself, but can also be provided in other parts.Specific examples thereof are shown in FIGS. 8 and 9. ing.
この実施例では、内筒金具１２の外壁面とブロック体２
８の各突出部３２との合わせ面に、バイパス通路５４．
５４が設＆ノられて、双方の流体室２６、．２６を連通
孔３６．３６とは並列に連通せしめており、これらバイ
パス通路５４．５４がオリフィス手段とし“ζ機能する
ようにされている。In this embodiment, the outer wall surface of the inner cylinder fitting 12 and the block body 2
Bypass passages 54 .
54 are provided for both fluid chambers 26, . 26 are communicated in parallel with the communicating holes 36, 36, and these bypass passages 54, 54 function as orifice means.
すなわち、第１０図および第１１図から明らかなように
、可動体３８には前記実施例のようなオリフィス溝４２
が設けられておらず、そのフランジ４０が連通孔３６の
開口周縁部に着座して、そこを遮断した状態においては
、双方の流体室２６の流体が、かかるバイパス通路５４
．５４のみを経て相互に流通せしめられることにより、
実質的には前記実施例と同様に、低周波で大変位の振動
に対する有効な減衰力が発生ずるのである。なお、第９
図において、各バイパス通路５４が可動体３８のフラン
ジ４０によって塞がれるかの如く示されているが、それ
らバイパス通路５４は各可動体３８を挟んで、その両側
に２本ずつ、都合４本形成されており、常時両流体室２
６を連通させた状態となっている。That is, as is clear from FIGS. 10 and 11, the movable body 38 has an orifice groove 42 as in the above embodiment.
is not provided and the flange 40 is seated on the opening periphery of the communication hole 36 to block it, the fluid in both fluid chambers 26 flows through the bypass passage 54.
．． By being allowed to mutually circulate through only 54,
Substantially the same as in the previous embodiment, an effective damping force against low frequency, large displacement vibrations is generated. In addition, the 9th
In the figure, each bypass passage 54 is shown as being blocked by the flange 40 of the movable body 38, but there are four bypass passages 54 in total, two on each side of each movable body 38. Both fluid chambers 2 are formed at all times.
6 are in communication.
そし”（、この例においても、ゴム製の可動体３８に換
えて、第１２図および第１３図に示されるような金属製
の可動体３８を採用し得ることを始めとして、その他の
部分については、第１図および第２図に示される実施例
と同様であるため、対応した符号を附して説明は省略す
る。(In this example as well, a metal movable body 38 as shown in FIGS. 12 and 13 can be used instead of the rubber movable body 38, and other parts Since these are similar to the embodiments shown in FIGS. 1 and 2, corresponding reference numerals are given and explanations thereof will be omitted.
また、可動体３８等の可動部材とは別にオリフィス手段
を設ける場合であっても、第１４図に示されるように、
板状の可動板５６を可動部材として機能させ、かつ、そ
れとは別のところにバイパス通路５８を設けて、これに
オリフィス手段としての役割を果たさせることも可能で
ある。Furthermore, even if the orifice means is provided separately from the movable member such as the movable body 38, as shown in FIG.
It is also possible to make the plate-shaped movable plate 56 function as a movable member, and to provide a bypass passage 58 separately from it to serve as an orifice means.
その他、本発明をエンジンマウント等、他の防振支持体
に適用することを始めとして、本発明には、当業者の知
識に基づいて種々の変更、改良等を施した態様が存在し
得ることは、改めて言うまでもないところである。In addition, the present invention may be modified in various ways based on the knowledge of those skilled in the art, including applying the present invention to other vibration-proof supports such as engine mounts. Needless to say again.
第１図は、本発明の一実施であるサスペンションブツシ
ュの縦断面図であって、かつ第２図におけるＩ−１断面
図である。第２図は、第１図における■−■断面図であ
り、第３図および第４図は、そこにおける可動体をそれ
ぞれ示す平面図および正面図である。また、第５図およ
び第６図゛は、可動体の別の態様を示す平面図および正
面図であり、第７図は本発明の別の実施例の要部を簡略
に示す概念的な断面図である。第８図は、本発明の別の
実施例であるサスペンションブツシュの縦断面図であっ
て、かつ第９図における■−■断面図である。第９図は
、第８図におけるＩＸ −ＩＸ断面図であり、第１０図
および第１１図は、そこにおける可動体を示すそれぞれ
平面図および正面図である。
また第１２図および第１３図は、そのような可動体の別
の態様をそれぞれ示す平面図および正面図であり、更に
第１４図は、本発明の別の実施例の要部を簡略に示す概
念的な断面図である。
１０：サスペンションブツシュ
（流体入りブツシュ）
１２：内筒金具 １４：外筒金具
１６：ゴムスリーブ（ゴム弾性体）
２６：流体室 ２８；ブロソ体
３０：ストソパ部（ストッパ手段）
３２：突出部 ３６：連通孔（連通路）３８：可動体（
可動部材）
４０：フランジ
４２ニオリフイス溝（オリフィス手段）４Ｂ、り６：可
動板（可動部材）
５２ニオリフイス孔（オリフィス手段）５４．５８：ハ
・イバス通路（オリフィス手段）出願人 東海ゴム工業
株式会社FIG. 1 is a longitudinal sectional view of a suspension bushing that is an embodiment of the present invention, and is a sectional view taken along line I-1 in FIG. 2. FIG. 2 is a cross-sectional view taken along the line ■-■ in FIG. 1, and FIGS. 3 and 4 are a plan view and a front view, respectively, showing the movable body there. 5 and 6 are a plan view and a front view showing another aspect of the movable body, and FIG. 7 is a conceptual cross-sectional view schematically showing the main parts of another embodiment of the present invention. It is a diagram. FIG. 8 is a longitudinal cross-sectional view of a suspension bushing according to another embodiment of the present invention, and is a cross-sectional view taken along the line -■ in FIG. 9. FIG. 9 is a sectional view taken along line IX-IX in FIG. 8, and FIGS. 10 and 11 are a plan view and a front view, respectively, showing the movable body there. Further, FIG. 12 and FIG. 13 are a plan view and a front view, respectively, showing another aspect of such a movable body, and FIG. 14 is a simplified diagram showing the main part of another embodiment of the present invention. It is a conceptual cross-sectional view. 10: Suspension bushing (fluid-filled bushing) 12: Inner cylinder metal fitting 14: Outer cylinder metal fitting 16: Rubber sleeve (rubber elastic body) 26: Fluid chamber 28; Bloso body 30: Stroke part (stopper means) 32: Projecting part 36 : Communication hole (communication path) 38: Movable body (
Movable member) 40: Flange 42 Niorifice groove (orifice means) 4B, Ri 6: Movable plate (movable member) 52 Niorifice hole (orifice means) 54.58: H bus passage (orifice means) Applicant Tokai Rubber Industries Co., Ltd.
Claims (3)
の間にゴム弾性体が介在せしめられると共に、該ゴム弾
性体に、所定の非圧縮性流体がそれぞれ封入される１組
の流体室が形成され、且つそれら流体室間を相互に連通
せしめる連通路が設けられた構造の流体入りブツシュに
おいて、前記流体室内に、前記内筒金具に固定され且つ
該円筒金具から前記外筒金具に延びる所定高さのストッ
パ手段を設けて、該ストッパ手段に前記外筒金具が当接
し得るようにすると共に、前記連通路に、該連通路を遮
断する位置と遮断しない位置とに移動可能であって、前
記流体の流通に伴う押圧力によって前記連通路を遮断す
る位置に移動せしめられる可動部材を設け、更に、該可
動部材によって前記連通路が遮断された状態においても
、前記双方の流体室同士を相互に、且つ前記流体の流通
に対して該連通路より大きな流通抵抗を与える状態で連
通せしめるオリフィス手段を設けたことを特徴とする流
体入りブツシュ。(1) A pair of rubber elastic bodies are interposed between an inner cylindrical metal fitting and an outer cylindrical metal fitting that are arranged concentrically with each other, and a predetermined incompressible fluid is sealed in each of the rubber elastic bodies. In a fluid-filled bushing having a structure in which a fluid chamber is formed and a communication path is provided for communicating between the fluid chambers, the bushing is fixed to the inner cylindrical metal fitting within the fluid chamber, and is connected from the cylindrical metal fitting to the outer cylindrical metal fitting. A stopper means extending to a predetermined height is provided so that the outer cylindrical fitting can come into contact with the stopper means, and the stopper means is movable in the communication path between a position where the communication path is blocked and a position where the communication path is not blocked. A movable member is provided that can be moved to a position where the communication path is blocked by a pressing force accompanying the flow of the fluid, and further, even when the communication path is blocked by the movable member, both of the fluid chambers are A fluid-filled bushing, characterized in that it is provided with orifice means for allowing the fluid to communicate with each other in a state that provides greater flow resistance than the communication path to the flow of the fluid.
°ζいる特許請求の範囲第１項記載の流体入りブツシュ
。(2) The fluid-filled bushing according to claim 1, wherein the orifice means is provided on the movable member.
に形成されたバイパス通路によって構成されている特許
請求の範囲第１項記載の流体入りブツシュ。(3) The fluid-filled bushing according to claim 1, wherein the orifice means is constituted by a bypass passage formed in parallel with the communication passage.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3476284A JPS60179542A (en) | 1984-02-24 | 1984-02-24 | Liquid containing bushing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3476284A JPS60179542A (en) | 1984-02-24 | 1984-02-24 | Liquid containing bushing |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP32680889A Division JPH02209646A (en) | 1989-12-16 | 1989-12-16 | Mount having fluid therein |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60179542A true JPS60179542A (en) | 1985-09-13 |
| JPH0231255B2 JPH0231255B2 (en) | 1990-07-12 |
Family
ID=12423321
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3476284A Granted JPS60179542A (en) | 1984-02-24 | 1984-02-24 | Liquid containing bushing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60179542A (en) |
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62288742A (en) * | 1986-06-06 | 1987-12-15 | Tokai Rubber Ind Ltd | Highly viscous fluid sealing mount device |
| US4728086A (en) * | 1986-01-20 | 1988-03-01 | Bridgestone Corporation | Vibration isolating apparatus |
| US4763884A (en) * | 1985-11-28 | 1988-08-16 | Nissan Motor Company, Limited | Apparatus for supporting a vibrating object |
| US4793600A (en) * | 1986-03-14 | 1988-12-27 | Bridgestone Corporation | Vibration isolating apparatus |
| JPS64741U (en) * | 1987-06-19 | 1989-01-05 | ||
| US4838529A (en) * | 1985-11-18 | 1989-06-13 | Bridgestone Corporation | Liquid-filled vibration isolating devices |
| FR2626640A1 (en) * | 1988-01-28 | 1989-08-04 | Hutchinson | IMPROVEMENTS ON HYDRAULIC ANTI-VIBRATION SUPPORT SLEEVES |
| US4858899A (en) * | 1985-10-28 | 1989-08-22 | Nissan Motor Co., Ltd. | Bushing type vibration insulator |
| US4861006A (en) * | 1986-09-16 | 1989-08-29 | Bridgestone Corporation | Anti-vibration apparatus |
| US4883260A (en) * | 1987-09-16 | 1989-11-28 | Tokai Rubber Industries, Ltd. | Elastic bushing having fluid chamber filled with highly viscous fluid |
| US5037073A (en) * | 1988-11-10 | 1991-08-06 | Tokai Rubber Industries Ltd. | Fluid-filled cylindrical elastic mount having moveable block and spiral orifice |
| DE4026370A1 (en) * | 1990-08-21 | 1992-03-05 | Freudenberg Carl Fa | Tubular rubber spring with two supports - has rubber piece containing two fluid-filled compartments, with hole and stop pad containing release pocket |
| US5118068A (en) * | 1987-10-28 | 1992-06-02 | Bridgestone Corporation | Vibration isolator |
| JPH0510840U (en) * | 1991-07-23 | 1993-02-12 | 三菱自動車工業株式会社 | Liquid-filled mount structure |
| US5280885A (en) * | 1988-04-07 | 1994-01-25 | Bridgestone Corporation | Vibration isolating apparatus |
| JPH06255327A (en) * | 1993-03-02 | 1994-09-13 | Onodani Kiko Kk | Removal of flat tire and device therefor |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5784220A (en) * | 1980-11-14 | 1982-05-26 | Aisin Seiki Co Ltd | Composite engine mount for vehicle engine |
| JPS5794145A (en) * | 1980-11-28 | 1982-06-11 | Kinugawa Rubber Ind Co Ltd | Anti-vibration supporting device |
-
1984
- 1984-02-24 JP JP3476284A patent/JPS60179542A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5784220A (en) * | 1980-11-14 | 1982-05-26 | Aisin Seiki Co Ltd | Composite engine mount for vehicle engine |
| JPS5794145A (en) * | 1980-11-28 | 1982-06-11 | Kinugawa Rubber Ind Co Ltd | Anti-vibration supporting device |
Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4858899A (en) * | 1985-10-28 | 1989-08-22 | Nissan Motor Co., Ltd. | Bushing type vibration insulator |
| US4838529A (en) * | 1985-11-18 | 1989-06-13 | Bridgestone Corporation | Liquid-filled vibration isolating devices |
| US4763884A (en) * | 1985-11-28 | 1988-08-16 | Nissan Motor Company, Limited | Apparatus for supporting a vibrating object |
| US4728086A (en) * | 1986-01-20 | 1988-03-01 | Bridgestone Corporation | Vibration isolating apparatus |
| US4793600A (en) * | 1986-03-14 | 1988-12-27 | Bridgestone Corporation | Vibration isolating apparatus |
| JPS62288742A (en) * | 1986-06-06 | 1987-12-15 | Tokai Rubber Ind Ltd | Highly viscous fluid sealing mount device |
| US4861006A (en) * | 1986-09-16 | 1989-08-29 | Bridgestone Corporation | Anti-vibration apparatus |
| US4973031A (en) * | 1986-09-16 | 1990-11-27 | Bridgestone Corporation | Anti-vibration apparatus |
| JPS64741U (en) * | 1987-06-19 | 1989-01-05 | ||
| US4883260A (en) * | 1987-09-16 | 1989-11-28 | Tokai Rubber Industries, Ltd. | Elastic bushing having fluid chamber filled with highly viscous fluid |
| US5118068A (en) * | 1987-10-28 | 1992-06-02 | Bridgestone Corporation | Vibration isolator |
| FR2626640A1 (en) * | 1988-01-28 | 1989-08-04 | Hutchinson | IMPROVEMENTS ON HYDRAULIC ANTI-VIBRATION SUPPORT SLEEVES |
| US5280885A (en) * | 1988-04-07 | 1994-01-25 | Bridgestone Corporation | Vibration isolating apparatus |
| US5037073A (en) * | 1988-11-10 | 1991-08-06 | Tokai Rubber Industries Ltd. | Fluid-filled cylindrical elastic mount having moveable block and spiral orifice |
| DE4026370A1 (en) * | 1990-08-21 | 1992-03-05 | Freudenberg Carl Fa | Tubular rubber spring with two supports - has rubber piece containing two fluid-filled compartments, with hole and stop pad containing release pocket |
| JPH0510840U (en) * | 1991-07-23 | 1993-02-12 | 三菱自動車工業株式会社 | Liquid-filled mount structure |
| JPH06255327A (en) * | 1993-03-02 | 1994-09-13 | Onodani Kiko Kk | Removal of flat tire and device therefor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0231255B2 (en) | 1990-07-12 |
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