JPS5937349A - Vibration preventing support - Google Patents

Vibration preventing support

Info

Publication number
JPS5937349A
JPS5937349A JP57145647A JP14564782A JPS5937349A JP S5937349 A JPS5937349 A JP S5937349A JP 57145647 A JP57145647 A JP 57145647A JP 14564782 A JP14564782 A JP 14564782A JP S5937349 A JPS5937349 A JP S5937349A
Authority
JP
Japan
Prior art keywords
communication
chamber
elastic member
inner cylindrical
fitting
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
Application number
JP57145647A
Other languages
Japanese (ja)
Other versions
JPS6361536B2 (en
Inventor
Yoshiki Funahashi
舟橋 芳樹
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sumitomo Riko Co Ltd
Original Assignee
Sumitomo Riko Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Sumitomo Riko Co Ltd filed Critical Sumitomo Riko Co Ltd
Priority to JP57145647A priority Critical patent/JPS5937349A/en
Publication of JPS5937349A publication Critical patent/JPS5937349A/en
Publication of JPS6361536B2 publication Critical patent/JPS6361536B2/ja
Granted legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16FSPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04Units 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
    • F16F13/06Units 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
    • F16F13/08Units 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
    • F16F13/14Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/16Units of the bushing type, i.e. loaded predominantly radially specially adapted for receiving axial loads

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Body Structure For Vehicles (AREA)
  • Combined Devices Of Dampers And Springs (AREA)

Abstract

PURPOSE:To provide an effective damping effect by elasticity of a first elastic member and flow resistance of fluid between a first chamber and a second chamber and elasticity of a second elastic member and flow resistance of fluid between a plurality of second chambers. CONSTITUTION:When vibration as a load W is applied axially, non-compressive fluid 22 in a first chamber 18 moves into a second chamber 20 through a notch 48, a communicating peripheral groove 52 and a notch 50 so that the vibration in low frequency region is effectively damped by flow resistance in the movement of the fluid. When vibration in the direction perpendicular to the axial direction, i.e., a load W is applied, the second chamber 20 at the side to which the load is applied is deformed and the non-compressive fluid 22 moves into another second chamber 20 so that the low frequency vibration W is satisfactorily damped.

Description

【発明の詳細な説明】 本発明は、防振支持体に係り、特に低周波振動及び高周
波振動に対して同時に有効な減衰特性を発揮し得る一方
、そのような特性がその軸心方向と共に、該軸心方向に
直角な方向においても発揮され得るようにした防振支持
体に関するものである。
DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a vibration-isolating support, which can exhibit effective damping characteristics at the same time, particularly against low-frequency vibrations and high-frequency vibrations; The present invention relates to a vibration isolating support that can also be exerted in a direction perpendicular to the axial direction.

従来から、自動車のボディマウント乃至はキャブマウン
ト、テンションロッド乃至はストラットバーのクッショ
ン(ブツシュ)等の防振支持体として、ゴムブロックを
2個の取付金具の間に介在させた構造のものが用いられ
ているが、高周波域での振動騒音を低減するために動バ
ネ定数の低いゴムを使用すると、ゴムの損失係数が小さ
いため減衰係数が小さくなり、それ故かかる防振支持体
に要請される特性を充分に満たし得なかったのである。
Conventionally, a structure in which a rubber block is interposed between two mounting brackets has been used as a vibration-proof support for automobile body mounts, cab mounts, tension rods, strut bar cushions, etc. However, when rubber with a low dynamic spring constant is used to reduce vibration noise in the high frequency range, the loss coefficient of the rubber is small, so the damping coefficient becomes small, and therefore the characteristics required for such a vibration isolating support are reduced. could not be fully satisfied.

けだし、かかる防振支持体には、低周波域での振動を低
減するための高減衰特性と高周波域での騒音を低減する
ための低動バネ特性を備えるべきことが要求されるから
である。
This is because such a vibration-proof support is required to have high damping characteristics to reduce vibration in the low frequency range and low dynamic spring characteristics to reduce noise in the high frequency range. .

一方、かかる要請に応えるために、ゴムの弾性と流体の
流通抵抗を利用した構造の弾性支持体が、特開昭53−
5376号公報等により提案されている。この流体入り
の弾性支持体は、ゴムの弾性による減衰作用と共に、別
個に形成された二つの空間を連通せしめる小孔部を流体
が通過することにより生じる流通抵抗作用にて、減衰特
性をもたせるようにしたものであり、これによって一応
は低動バネ特性、高減衰特性が達成され得たのであるが
、その構造上から減衰特性が一方向に限定され、それと
は直角な方向における振動に対しては減衰効果が不充分
となる大きな問題があった。このため、かかる流体入り
弾性支持体を用いて直角な二方向における減衰効果を発
揮させるには、その2個を1組として用い、そしてそれ
らを傾斜して配置させる等の工夫が必要となり、これが
その 5− 取付は性を困難ならしめていたのであり、またその減衰
効果も不充分であったのである。加えて、このような流
体入り弾性支持体では、バネ定数比(横方向バネ定数/
上下方向バネ定数)が大きくとれない問題も内在してい
るのである。
On the other hand, in order to meet this demand, an elastic support body with a structure that utilizes the elasticity of rubber and the flow resistance of fluid was developed in Japanese Patent Laid-Open No.
This method has been proposed in Publication No. 5376 and the like. This fluid-filled elastic support has damping properties due to the damping effect due to the elasticity of the rubber as well as the flow resistance effect caused by the fluid passing through the small holes that communicate two separately formed spaces. This made it possible to achieve low dynamic spring characteristics and high damping characteristics, but due to its structure, the damping characteristics were limited to one direction, and the damping characteristics were limited to vibrations in a direction perpendicular to that direction. However, there was a major problem in that the damping effect was insufficient. Therefore, in order to exert a damping effect in two orthogonal directions using such fluid-filled elastic supports, it is necessary to use two of them as a set and arrange them at an angle. 5. Installation was difficult, and its damping effect was insufficient. In addition, in such a fluid-filled elastic support, the spring constant ratio (lateral spring constant/
There is also the inherent problem that the vertical spring constant cannot be made large.

ここにおいて、本発明は、かかる事情に鑑みて為された
ものであって、その主たる目的とするところは、流体媒
体を利用した高減衰特性を有する防振支持体において、
その改良を図ることにある。
The present invention has been made in view of the above circumstances, and its main purpose is to provide a vibration isolation support having high damping characteristics using a fluid medium.
The aim is to improve this.

また、本発明の他の目的は、流体媒体を用いてそれの二
つの空間における流動抵抗を利用して、低動バネ特性並
びに高減衰特性を同時に発揮せしめる一方、そのような
性能を直角な二方向において発揮し得るようにした防振
支持体を提供することにある。
Another object of the present invention is to simultaneously exhibit low dynamic spring characteristics and high damping characteristics by using a fluid medium and utilizing the flow resistance in its two spaces, while also achieving such performance by orthogonally spaced two spaces. It is an object of the present invention to provide a vibration-proof support that can exhibit vibration in various directions.

そして、これらの目的を達成するため、本発明にあって
は、(a)軸心方向の一端部において側方に延ヒルフラ
ンジ部を備え、所定の取付軸が挿通せしめられる内筒金
具と、(1))該内筒金具の外方にあって同心的に配置
され、目、つ該内筒金具のフラン 6− ジ部と同じ側にあって軸心方向に所定の距離を隔てて対
向するフランジ部を有する外筒金具と、(c)該内筒金
具のフランジ部と該外筒金具のフランジ部との間に配置
された円環状の第一の弾性部材と、((り該内筒金具と
該外筒金具の対向する筒状部分間に配置された第二の弾
性部材と、(e)前記第一の弾性部4′、Aの円環形状
の内側に位置し、主として該第−の弾性部材、前記内筒
金具及び前記第二の弾性部Hにて囲まれた第一の室と、
(f)前記第二の弾性部材内にその周方向に形成された
複数の第二の室と、(g)前記第一の室と第二の室とを
相互に連通せしめる連通機構と、()))前記第一の室
及び第二の室に封入された所定の非圧縮性流体とを含む
ように、防振支持体を構成したのである。
In order to achieve these objects, the present invention includes: (a) an inner cylindrical metal fitting having an extended hill flange portion on the side at one end in the axial direction, into which a predetermined mounting shaft is inserted; (1)) Located on the outside of the inner cylindrical metal fitting and arranged concentrically, the eye is located on the same side as the flange part of the inner cylindrical metal fitting and is opposed to it at a predetermined distance in the axial direction. (c) an annular first elastic member disposed between the flange portion of the inner tube fitting and the flange portion of the outer tube fitting; a second elastic member disposed between the cylindrical fitting and the opposing cylindrical portions of the outer cylindrical fitting, and (e) the first elastic member 4', located inside the annular shape of A, and a first chamber surrounded by a second elastic member, the inner cylindrical fitting, and the second elastic part H;
(f) a plurality of second chambers formed in the circumferential direction of the second elastic member; (g) a communication mechanism that allows the first chamber and the second chamber to communicate with each other; ))) The vibration isolating support is configured to include a predetermined incompressible fluid sealed in the first chamber and the second chamber.

従って、かかる構成の防振支持体にあっては、その軸心
方向の振動に対しては、第一の弾性部材の弾性と、第一
の室及び第二の室間の流体の流通抵抗とによって、効果
的な減衰作用が発揮され得ることとなるのであり、また
軸心と直角な方向から加わる振動に対しては、第二の弾
性部材の弾性と、連通機構によって連通せしめられた複
数の第二の室間における流体の流動抵抗によって効果的
な減衰作用が発揮され得ることとなったのである。
Therefore, in the vibration-proof support having such a structure, vibrations in the axial direction can be prevented by the elasticity of the first elastic member and the fluid flow resistance between the first chamber and the second chamber. Therefore, an effective damping effect can be exerted, and the elasticity of the second elastic member and the plurality of elastic members connected by the communication mechanism are effective against vibrations applied from the direction perpendicular to the axis. An effective damping effect can be exerted by the fluid flow resistance between the second chambers.

また、このような直角な2方向における振動に苅する減
衰作用に加えて、それら2方向の複合方向における減衰
効果も当然に達成され得るものである他、第一の弾性部
材と第二の弾性部材の材質を変えて、そのバネ定数をそ
れぞれ異なるものとすることができるところから、その
バネ定数比(llilIl心に直角な方向のバネ定数/
il’1Ill心方向のバネ定数)を従来の流体入り防
振支持体よりも犬とすることが可能となったのである。
Furthermore, in addition to the damping effect of damping vibrations in two orthogonal directions, a damping effect in a composite direction of these two directions can also be naturally achieved. The spring constant ratio (spring constant in the direction perpendicular to the center/
It has become possible to make the spring constant (center direction spring constant) smaller than that of the conventional fluid-filled vibration isolating support.

以下、本発明を更に具体的に明らかにするために、本発
明に係る幾つかの実施例を図面に基づいて詳細に説明す
ることとする。
EMBODIMENT OF THE INVENTION Hereinafter, in order to clarify the present invention more specifically, several embodiments according to the present invention will be described in detail based on the drawings.

先ず、第1図及び第2図には、本発明に係る防振支持体
たるキャブマウントの1例が示されているが、そこにお
いてキャブマウントは、それをボディとフレームとの間
に取り付けるべく、取付ボルトが挿通せしめられる内筒
金具1oと、その外側に所定の距離を隔てて配置された
外筒金具12と、それら内筒金具10と外筒金具12と
の間にそれぞれ配置された、第一の弾性部材としてのゴ
ムリング14及び第二の弾性部材を構成するゴムスリー
ブユニット16と、そして内筒金具10と外筒金具12
との間に、該ゴムリング14とゴムスリーブユニット1
6とによって形成される第−室18及び第二室20内に
充填された所定の非圧縮性流体22とから、実質的に構
成されている。
First, FIG. 1 and FIG. 2 show an example of a cab mount which is a vibration-proof support according to the present invention. , an inner cylindrical metal fitting 1o into which the mounting bolt is inserted, an outer cylindrical metal fitting 12 disposed outside thereof at a predetermined distance, and an inner cylindrical metal fitting 10 disposed between the inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12, respectively. A rubber ring 14 as a first elastic member, a rubber sleeve unit 16 as a second elastic member, an inner cylindrical fitting 10 and an outer cylindrical fitting 12.
between the rubber ring 14 and the rubber sleeve unit 1.
6 and a predetermined incompressible fluid 22 filled in the second chamber 20.

より具体的には、かかるキャブマウントの最内筒を構成
する内筒金具10は、第3図に示されるように、その軸
心方向の一端部において側方に延びるフランジ部24を
備えた筒体であって、その筒状の外周部分において該フ
ランジ部24側に大径部26が所定長さで設けられ、且
つ該大径部26に続いて、フランジ部24が設けられた
端部と反対側の端部に向かって中径部28が延びており
、そしてこの中径部28に前記大径部26かられずかに
離れた位置において所定の長さ:lの小径部30が設け
られている。また、外筒金具12は、9− 第4図及び第5図に示されるように、その軸心方向の一
端部において側方に延びるフランジ部32を備えており
、該フランジ部32がらやや離れた位置においてその外
周面に対して取付用ブラケット34が溶接等によって固
定せしめられている。
More specifically, as shown in FIG. 3, the inner cylinder metal fitting 10 constituting the innermost cylinder of the cab mount is a cylinder equipped with a flange portion 24 extending laterally at one end in the axial direction. A large diameter portion 26 is provided with a predetermined length on the flange portion 24 side in the cylindrical outer peripheral portion thereof, and an end portion following the large diameter portion 26 and provided with the flange portion 24. A medium diameter portion 28 extends toward the opposite end, and a small diameter portion 30 having a predetermined length l is provided in this medium diameter portion 28 at a position slightly apart from the large diameter portion 26. ing. Further, as shown in FIGS. 9-4 and 5, the outer cylindrical fitting 12 is provided with a flange portion 32 extending laterally at one end in the axial direction, and the flange portion 32 is slightly spaced apart from the flange portion 32. At this position, a mounting bracket 34 is fixed to the outer peripheral surface by welding or the like.

なお、かかるブラケット34には適数個の取付用ボルト
孔36が貫設されている。そして、外筒金具12の端部
フランジ部32の外側面に所定厚さのゴムリング14が
同心的に加硫接着等によって固着せしめられており、更
に該ゴムリング14の端面にリング状のカシメ金具38
が加硫接着等によって固着せしめられている。また、ゴ
ムリング14の外周部には、外筒リング4oが埋め込ま
れ、該ゴムリング14の外方への変形が阻止され得るよ
うに構成されている。
Note that a suitable number of mounting bolt holes 36 are provided through the bracket 34. A rubber ring 14 of a predetermined thickness is fixed concentrically to the outer surface of the end flange portion 32 of the outer cylinder fitting 12 by vulcanization adhesive or the like, and a ring-shaped caulking is further attached to the end surface of the rubber ring 14. Metal fittings 38
is fixed by vulcanization adhesive or the like. Further, an outer cylindrical ring 4o is embedded in the outer peripheral portion of the rubber ring 14, and is configured to prevent the rubber ring 14 from deforming outward.

さらに、ゴムスリーブユニット16は、第6図及び第9
図に示されるように、軸方向に2分された二つの分割体
16a、16bからなるものであって、それら分割体は
何れも同径の筒状のゴム半部42a、42bと、その内
側及び外側にそれぞ10− れ加硫接着等によって固着せしめられた内装筒体半部4
4a、4411及び外装筒体半部46a、461)とか
ら構成されている。なお、第6図に示される一方の分割
体16a、即ち内筒金具10のフランジ部24や外筒金
具12のフランジ部32側に位置せしめられるものにお
ける内装筒体半部44aは、第7図及び第8図に示され
るように、その軸方向の両端部にそれぞれ複数個の切欠
き48゜50が設けられている。また、各分割体16a
Furthermore, the rubber sleeve unit 16 is shown in FIGS.
As shown in the figure, it consists of two divided bodies 16a and 16b divided into two in the axial direction, and each of these divided bodies has a cylindrical rubber half part 42a and 42b of the same diameter, and an inner side thereof. and an inner cylindrical body half 4 fixed to the outside by vulcanization adhesive or the like.
4a, 4411 and an exterior cylindrical half portion 46a, 461). Note that the inner cylindrical half portion 44a of one of the divided bodies 16a shown in FIG. 6, that is, the one located on the side of the flange portion 24 of the inner cylindrical fitting 10 and the flange portion 32 of the outer cylindrical fitting 12, is shown in FIG. As shown in FIG. 8, a plurality of notches 48.degree. 50 are provided at both ends in the axial direction. In addition, each divided body 16a
.

16bのゴム半部42a、4211の周方向における対
応する位置にほぼ等しい位相差をもった複数個の第二室
半部20a、201)が設けられており、これら分割体
16a、161)はその軸方向の端面を接して接続され
たときに、第二の弾性部材となるゴム42(42a+4
2b)内には、径方向に内装筒体44と外装筒体46と
によって囲まれた、周方向に別個に複数の密閉された第
二室20が形成されるように構成されている。
A plurality of second chamber halves 20a, 201) having approximately equal phase differences are provided at corresponding positions in the circumferential direction of the rubber halves 42a, 4211 of 16b, and these divided bodies 16a, 161) Rubber 42 (42a+4
2b), a plurality of separately sealed second chambers 20 are formed in the circumferential direction and are surrounded in the radial direction by the inner cylinder 44 and the outer cylinder 46.

このような第3図乃至第10図に示される構成部品を用
いて、第1図及び第2図に示される如き本発明に従うキ
ャブマウントを組み立てるに際しては、先ず第6図乃至
第10図に示される二つの分割体16a、、1G+)が
、水、ポリアルキレングリコール、シリコーン油や低分
子計重合体等の非圧縮性流体22中において、第4図、
第5図に示される構成部品を構成する外筒金具12の筒
状部内に、該分割体16aがフランジ部32側に位置す
るように圧入せしめ、続いて他の一つの分割体1、6 
bを各分割体の開口する第二室半部20a。
When assembling the cab mount according to the present invention as shown in FIGS. 1 and 2 using the components shown in FIGS. 3 to 10, first, assemble the cab mount shown in FIGS. 6 to 10. The two divided bodies 16a, , 1G+), which are separated from each other in FIG.
The divided body 16a is press-fitted into the cylindrical part of the outer cylindrical metal fitting 12 constituting the component shown in FIG.
b is the second chamber half 20a with the opening of each divided body.

201〕を付き合わせるようにして、圧入ぜしぬるので
ある。この圧入操作によって、第二室半部2Qa、2Q
bは結合され、一つの第二室20となり、かかる第二室
20が周方向に所定の位相差をもって形成されることと
なる。なお、この分割体16a、161)の圧入によっ
て形成された3個の第二室20内には、それぞれ非圧縮
性流体22が充填されるようになる。
201] and press them together. By this press-fitting operation, the second chamber halves 2Qa, 2Q
b are combined to form one second chamber 20, and this second chamber 20 is formed with a predetermined phase difference in the circumferential direction. The three second chambers 20 formed by press-fitting the divided bodies 16a, 161) are each filled with an incompressible fluid 22.

次いで、かかる外筒金具12に圧入された分割体16a
、16bに対して、更に第3図に示される内筒金具10
が、そのフランジ24を該外筒金具12のフランジ部3
2側に位置するようにして圧入せしぬられることとなる
。即ち、内筒金具10の中径部28が各分割体16a、
16bの内装筒体半部44a、441)に圧入せしめら
れるのである。かかる内筒金具10の圧入によって、該
内筒金具10の小径部30の外側が分割体16aの内装
筒体半部44aによって囲まれることとなり、そこに連
通周溝52が第1図及び第2図に示される如く形成され
ることとなる。また、内筒金具10のフランジ部24は
、カシメ金具38に当接、収容され、このカシメ金具3
8をカシメ加工してフランジ部24を該カシメ金具38
にて液密に保持せしめることによって、該内筒金具10
とゴムリング14と分割体16aと外筒金具12とによ
って第−室18が内筒金具10の大径部26周りに形成
され、しかも非圧縮性流体中における圧入によって、か
かる第−室18内には、第二室20と同様に非圧縮性流
体22が充填せしめられるのである。また、このように
して形成された第−室18と複数の第二室20とは内筒
金具10の筒状−13= 部の周りに形成された連通周溝52に対して、それぞれ
分割体16aに設けられている両端部の切欠き48.5
0によってそれぞれ連通されている。
Next, the divided body 16a is press-fitted into the outer cylinder fitting 12.
, 16b, the inner cylinder fitting 10 shown in FIG.
However, the flange 24 is connected to the flange portion 3 of the outer cylinder fitting 12.
It will be press-fitted so that it is located on the 2nd side and then it will be wetted. That is, the middle diameter portion 28 of the inner cylinder fitting 10 is divided into each divided body 16a,
It is press-fitted into the inner cylindrical half portions 44a, 441) of 16b. By press-fitting the inner cylindrical fitting 10, the outside of the small diameter portion 30 of the inner cylindrical fitting 10 is surrounded by the inner cylindrical half portion 44a of the divided body 16a, and a communicating circumferential groove 52 is formed therein as shown in FIGS. It will be formed as shown in the figure. Further, the flange portion 24 of the inner cylinder metal fitting 10 is in contact with and accommodated in the caulking metal fitting 38, and this caulking metal fitting 3
8 is caulked and the flange portion 24 is attached to the caulking metal fitting 38.
By holding the inner cylindrical fitting 10 liquid-tightly,
A first chamber 18 is formed around the large diameter portion 26 of the inner tube fitting 10 by the rubber ring 14, the divided body 16a, and the outer tube fitting 12, and the inside of the first chamber 18 is formed by press fitting in an incompressible fluid. Similarly to the second chamber 20, the chamber is filled with an incompressible fluid 22. Moreover, the second chamber 18 and the plurality of second chambers 20 formed in this way are each divided into separate bodies with respect to the communication circumferential groove 52 formed around the cylindrical -13= part of the inner cylindrical fitting 10. Notches 48.5 at both ends provided in 16a
They are connected by 0.

従って、第−室18は連通周溝52を介して、各々の第
二室20にそれぞれ連通せしめられることとなり、また
複数(ここでは3個)の第二室20も相互に連通周溝5
2を介して連通せしめられているのである。
Therefore, the second chamber 18 is communicated with each of the second chambers 20 via the communication circumferential groove 52, and a plurality of (three in this case) second chambers 20 are also communicated with each other through the communication circumferential groove 52.
They are communicated via 2.

従って、かかる構成のキャブマウントにあっては、第1
1図に示される如く、その軸方向に荷重Wとしての振動
が加わると、第−室18内の非圧縮性流体22が内装筒
体半部44aの切欠き48(第1の連通部)、内筒金具
10の外周面に形成された連通周溝52、内装筒体半部
44aの切欠き50(第2の連通部)を通じて第二室2
0内に移動するようになり、そしてこの移動に際しての
流動抵抗によって、かかる振動、即ち低周波域での振動
が効果的に減衰されることとなるのである。
Therefore, in a cab mount having such a configuration, the first
As shown in FIG. 1, when a vibration as a load W is applied in the axial direction, the incompressible fluid 22 in the first chamber 18 moves through the notch 48 (first communication section) of the inner cylinder half 44a, The second chamber 2 is connected to the second chamber 2 through the communication circumferential groove 52 formed on the outer peripheral surface of the inner cylinder fitting 10 and the notch 50 (second communication part) of the inner cylinder half part 44a.
0, and due to the flow resistance during this movement, such vibrations, that is, vibrations in the low frequency range, are effectively damped.

なお、ここでは、ゴムリング14の外周部に外筒リング
40が設けられているところから、ゴムリ14− ング14の外方への変形が効果的に抑制され、その内方
に位置する第−室18の変形が効果的に行なわれ得るよ
うにな′つている。また、軸心方向の高周波振動に対し
ては、ゴムリング14を構成するゴム材料として適宜の
動的バネ定数を有するものを用いることによって、その
領域の振動騒音を効果的に低減させることが可能である
Here, since the outer cylindrical ring 40 is provided on the outer periphery of the rubber ring 14, the outward deformation of the rubber ring 14 is effectively suppressed, and The deformation of the chamber 18 can now be carried out effectively. Furthermore, for high-frequency vibrations in the axial direction, by using a rubber material having an appropriate dynamic spring constant as the rubber material constituting the rubber ring 14, it is possible to effectively reduce vibration noise in that region. It is.

一方、軸心方向に対して直角の方向の振動、即ち第12
図に矢印で示される如き荷重Wが加わったときにあって
は、その荷重が加わる側の第二室20が変形し、そこに
充填されている非圧縮性流体22が分割体16aの内装
筒体半部44aの切欠き50、連通周溝52、そして再
び内装筒体半部44aの切欠き50を通じて、他の第二
室20内に移動し、これによって低周波振動(W)は良
好に減衰せしめられることとなる。また、高周波振動が
加わったときには、内筒10と外筒12との間に介在せ
しめられるゴムスリーブユニット16(分割体16a十
分割体16b)を構成するゴム42(a、I))の弾性
によって減衰させられることとなり、それ故かかる高周
波振動に対してのゴム材料を選択することによって、そ
の振動騒1等の低減を達成することが可能である。
On the other hand, the vibration in the direction perpendicular to the axial direction, that is, the 12th
When a load W as shown by the arrow in the figure is applied, the second chamber 20 on the side to which the load is applied is deformed, and the incompressible fluid 22 filled therein is transferred to the inner cylinder of the divided body 16a. It moves into the other second chamber 20 through the notch 50 of the body half 44a, the communication circumferential groove 52, and again through the notch 50 of the inner cylindrical body half 44a, whereby the low frequency vibration (W) is well suppressed. This results in attenuation. Furthermore, when high-frequency vibration is applied, the elasticity of the rubber 42 (a, I) constituting the rubber sleeve unit 16 (divided body 16a and fully divided body 16b) interposed between the inner cylinder 10 and the outer cylinder 12 Therefore, by selecting a rubber material that is resistant to such high-frequency vibrations, it is possible to reduce the vibration noise.

このように、かかる構成のキャブマウントにあっては、
軸心方向の高周波振動並びに低周波振動が内筒金具10
と外筒金具12の両7ランジ部24.32間に設けられ
たゴムリング14の弾性と共に、第1室18と第2室と
の間の圧縮性流体22の移動が、切欠き48、連通周溝
52、切欠き50を介して所定の流通抵抗を以て行なわ
れ得ることによって効果的に行なわれ得ることとなり、
また軸心に対して直角な方向にあっては、その高周波振
動及び低周波振動はゴムスリーブユニット16における
ゴム42の弾性に加えて、複数の第二室20間における
切欠き50、連通周溝52及び切欠き50を介しての非
圧縮性流体22の流通抵抗によって効果的に減衰せしめ
られ得ることとなる。しかも、かくの如き2方向におけ
る振動減衰作用は、更にそれらの複合方向からの高周波
振動、低周波振動に対しても各ゴム部分並びに各室がそ
れぞれの分力を減衰せしめることによって、全体として
効果的な減衰作用を発揮せしめ得るのである。加えて、
ゴムリング14並びにゴムスリーブユニット16のそれ
ぞれのゴム材料を別個に設けることができるため、それ
らのゴム材料の動的バネ定数を適宜に選定することがで
きるところから、バネ定数比(軸心方向に直角な方向の
バネ定数/軸心方向のバネ定数)を大きくすることも可
能となったのである。
In this way, in a cab mount with such a configuration,
High-frequency vibrations and low-frequency vibrations in the axial direction cause the inner cylinder metal fitting 10 to
Together with the elasticity of the rubber ring 14 provided between the 7 flange portions 24 and 32 of the outer cylinder fitting 12, the movement of the compressible fluid 22 between the first chamber 18 and the second chamber This can be carried out effectively through the circumferential groove 52 and the notch 50 with a predetermined flow resistance.
In addition, in the direction perpendicular to the axis, the high-frequency vibrations and low-frequency vibrations are caused by the elasticity of the rubber 42 in the rubber sleeve unit 16, as well as by the notches 50 between the plurality of second chambers 20 and the communication circumferential grooves. 52 and the notch 50, the flow resistance of the incompressible fluid 22 can be effectively damped. Moreover, the vibration damping effect in these two directions is also effective as a whole, as each rubber part and each chamber attenuate their respective component forces against high-frequency vibrations and low-frequency vibrations from those combined directions. It is possible to exert a damping effect. In addition,
Since the rubber materials of the rubber ring 14 and the rubber sleeve unit 16 can be provided separately, the dynamic spring constants of these rubber materials can be appropriately selected. This also made it possible to increase the spring constant in the perpendicular direction/spring constant in the axial direction.

なお、上側にあっては、ゴムスリーブユニット16に設
けられる第二室20を3個としたのであるが、本発明は
これのみに限定されるものでは決してなく、一般に複数
個設けられるものであるが、例えば第13図及び第14
図に示されるように、単に二つの第二室20を設けるこ
とも可能である。
In addition, on the upper side, the number of second chambers 20 provided in the rubber sleeve unit 16 is three, but the present invention is by no means limited to this, and generally a plurality of second chambers 20 are provided. However, for example, FIGS. 13 and 14
As shown in the figure, it is also possible to provide only two second chambers 20.

なお、第二室20が2個の場合にあっては、前例の如き
3個の場合における軸心に直角なあらゆる方向からの振
動を減衰する場合とは異なり、単に第14図に示される
如く矢印方向の荷重Wとしての振動が加わる場合におい
てのみ有効となるもの17− である。
In addition, in the case where there are two second chambers 20, unlike the case where there are three second chambers 20 as in the previous example, where vibrations from all directions perpendicular to the axis are damped, the vibrations are simply damped as shown in FIG. 17-, which becomes effective only when vibration is applied as a load W in the direction of the arrow.

また、第15図には、前記例示のキャブマウントを実際
に自動車に取り付けた状態を示しており、そこにおいて
本発明に従うキャブマウント60はボディ部材62とフ
レーム部材64との間に組み付けられているのである。
Further, FIG. 15 shows a state in which the above-mentioned exemplary cab mount is actually attached to an automobile, in which a cab mount 60 according to the present invention is assembled between a body member 62 and a frame member 64. It is.

即ち、フレーム部材64に対してキャブマウント60を
構成する外筒金具12の外周面に固着されている数句用
ブラケット34を介して固定せしめられる一方、ボディ
部材62に対しては、該ボディ部材62を貫通する取付
ボルト66がキャブマウント60の内筒金具10内を挿
通せしめられ、そして止め部材68を介してナツト70
で締めつけることによって組み付けられているのである
。なお、図中72は、外筒金具12の端面に対向するよ
うに、止め部材68に固着、形成されたストッパであり
、74はワッシャである。
That is, it is fixed to the frame member 64 via the bracket 34 fixed to the outer peripheral surface of the outer cylindrical metal fitting 12 constituting the cab mount 60, while the body member 62 is fixed to the body member 62. A mounting bolt 66 passing through the hole 62 is inserted into the inner cylindrical metal fitting 10 of the cab mount 60, and then the nut 70 is inserted through the stopper member 68.
It is assembled by tightening it. In addition, in the figure, 72 is a stopper fixed to and formed on the stopper member 68 so as to face the end surface of the outer cylinder fitting 12, and 74 is a washer.

また、第16図、17図には、自動車のサスペンション
のテンションロッドの取付けに際して用いられるクッシ
ョンに本発明を適用した例が示さ18− れており、そこにおいて本発明に従うクッション76は
公知のように1、車体のサイドメンバー若しくはクロス
メンバーに取り付けられたブラケット78にテンション
ロッド80の先端部を取り付けるために、その2個を組
み合わせて1対として用いられている。即ち、第16図
に示されるように、テンションロッド80の先端部がク
ッション76のそれぞれの第二室側端部を付き合わせる
ようにして配置された状態でそれぞれのクッション76
の内筒金具内を挿通せしめられ、ナツト82にて締め付
けることによって取り付けられているのである。なお、
ここに例示のクッション76は、先に示したキャブマウ
ントと同様な構造を有するものであるため、同様な部分
には同一の符号を付して詳細な説明は省略することとす
る。勿論、このような構造のクッション76にあっても
、テンションロッド80から加えられるクッション76
の軸方向の主荷重は、第−室、第二室間の流体の移動に
よって効果的に減衰せしめられ、その減衰特性が著しく
向−卜させられ得る他、かかる軸方向に直角な方向の振
動、更にはそれら二方向の接合方向からの振動に対して
も効果的な減衰性能を発揮することができるのである。
Further, FIGS. 16 and 17 show an example in which the present invention is applied to a cushion used when attaching a tension rod of an automobile suspension, and the cushion 76 according to the present invention is used in a well-known manner. 1. In order to attach the tip of the tension rod 80 to the bracket 78 attached to the side member or cross member of the vehicle body, two of the tension rods 80 are combined and used as a pair. That is, as shown in FIG. 16, each cushion 76 is disposed such that the tip end of the tension rod 80 abuts the second chamber side end of each cushion 76.
It is inserted into the inner cylindrical metal fitting of the cylindrical member and is attached by tightening with a nut 82. In addition,
Since the cushion 76 illustrated here has a similar structure to the cab mount shown above, similar parts will be denoted by the same reference numerals and detailed explanation will be omitted. Of course, even if the cushion 76 has such a structure, the cushion 76 applied from the tension rod 80
The main axial load of the is effectively damped by the movement of fluid between the first and second chambers, and its damping characteristics can be significantly improved, as well as vibrations in the direction perpendicular to the axis. Furthermore, it is possible to exhibit effective damping performance against vibrations from those two joining directions.

以上、本発明にかかる防振支持体について、各種の態様
を説明してきたが、本発明がかかる例示の態様のみに限
定されるものでは決してなく、本発明の趣旨を逸脱しな
い限りにおいて、本発明には種々なる変更、修正を加え
ることができることは、言うまでもないところである。
Although various embodiments of the vibration isolation support according to the present invention have been described above, the present invention is by no means limited to only these illustrative embodiments, and the present invention It goes without saying that various changes and modifications can be made to the.

例えば、前例においては、第−室と第二室並びに複数の
第二室間を連通周溝を介して同時に相互に連通せしめる
構造とされているが、第−室と第二室の連通と第二室間
の連通とをそれぞれ別個に行うことも可能であり、また
連通周溝は内筒金具に設けられる場合のみならず、外筒
金具側に設けることも可能である。また、内筒金具と外
筒金具の7ラング部間に配置される第一の弾性材料とし
てのゴムリング14の外周部に配置された外筒リング4
0は、その設置が望ましいものではあるが、それが設け
られない場合もあり、また帯状バンドとしてゴムリング
14の外周面に接するような構造のものとすることも可
能である。
For example, in the previous example, the structure is such that the first chamber and the second chamber as well as a plurality of second chambers are communicated with each other at the same time via the communication circumferential groove, but the communication between the first chamber and the second chamber and the It is also possible to provide communication between the two chambers separately, and the communication circumferential groove can be provided not only on the inner cylindrical metal fitting but also on the outer cylindrical metal fitting side. Further, an outer cylinder ring 4 is arranged on the outer periphery of a rubber ring 14 as a first elastic material arranged between the seven rungs of the inner cylinder metal fitting and the outer cylinder metal fitting.
Although it is desirable to install the rubber ring 0, there are cases where it is not provided, and it is also possible to have a structure in which it is in contact with the outer peripheral surface of the rubber ring 14 as a belt-like band.

【図面の簡単な説明】[Brief explanation of drawings]

第1図は本発明に従う防振支持体の一例に係るキャブマ
ウントの縦断面図であり、第2図は第1図における■−
■断面図である。第3図乃至第10図はそれぞれ第1図
に示すキャブマウントの構成部品を示すものであって、
第3図はその円筒金具の半切欠き正面図、第4図は外筒
金具、ゴムリング、ブラケット、外筒リングを含む部品
の平面図、第5図はその半切欠き正面図、第6図はゴム
スリーブユニットを形成する一方の分割体の縦断面図、
第7図はその底面図、第8図はそれに用いられる内装筒
体半部の斜視図、第9図はゴムスリー−7”ユニットを
形成する他の一つの分割体の縦断面図、第10図はその
平面図、第11図は軸心方向に振動が加わったときにお
ける非圧縮性流体の流れを説明するための第1図に相当
する断面半回、第12図は軸心方向に対して直角な方向
の振動が加わったときの非圧縮性流体の流れを説明する
た21− めの第2図に対応する図であり、第13図は本発明の別
の実施例に係る第2図に相当する図、第14図は第13
図の実施例における非圧縮性流体の移動を説明するため
の図であり、第15図は第1図に示すキャブマウントの
取付状態を示す断面図であり、第16図は本発明に従う
防振支持体の1例であるテンションロッドのクッション
の取付状態を示す断面図であり、第17図は第16図に
おける■−X■断面図である。 10:内筒金具   12:外筒金具 14:ゴムリング 16:ゴムスリーブユニット 16a、16b :分割体 18:第−室、   20:第二室 2oa、20b : 第二室半! 22:非圧縮性流体 24:フランジ部26:大径部 
   28:中径部 30:小径部    32:フランジ部34:取付用ブ
ラケット 38:カシメ金具  40:外筒リング22− 42(a、b):ゴム(半部) 44(a、b):内装筒体(半部) 46(11,b):外装筒体(半部) 48.50:切欠き   52:連通周溝60:ギャブ
マウント  62:ボデイ部材64:フレーム部材  
 66:取付ボルト76:クッション    78ニブ
ラケット80:テンションロッド 出願人  東海ゴム工業株式会社 23− 第5図 第13図          第14図4a 第15図
FIG. 1 is a longitudinal cross-sectional view of a cab mount according to an example of the vibration-proof support according to the present invention, and FIG.
■It is a sectional view. 3 to 10 each show the components of the cab mount shown in FIG. 1,
Fig. 3 is a half-cut front view of the cylindrical fitting, Fig. 4 is a plan view of parts including the outer cylindrical fitting, rubber ring, bracket, and outer cylindrical ring, Fig. 5 is a half-cut front view thereof, and Fig. 6 is a A longitudinal sectional view of one of the divided bodies forming the rubber sleeve unit,
Fig. 7 is a bottom view thereof, Fig. 8 is a perspective view of a half of the inner cylindrical body used therein, Fig. 9 is a vertical sectional view of another divided body forming the rubber three-7'' unit, and Fig. 10. is a plan view of the same, Fig. 11 is a half-section cross section corresponding to Fig. 1 for explaining the flow of incompressible fluid when vibration is applied in the axial direction, and Fig. 12 is a cross-sectional view in the axial direction. 13 is a diagram corresponding to FIG. 21 for explaining the flow of an incompressible fluid when vibration in a right angle direction is applied, and FIG. 13 is a diagram corresponding to FIG. 2 according to another embodiment of the present invention. Figure 14 corresponds to Figure 13.
FIG. 15 is a cross-sectional view showing how the cab mount shown in FIG. 1 is attached, and FIG. 16 is a vibration-proof 17 is a cross-sectional view showing a state in which a cushion of a tension rod, which is an example of a support body, is attached, and FIG. 17 is a cross-sectional view taken along the line ■-X■ in FIG. 16. 10: Inner cylinder metal fitting 12: Outer cylinder metal fitting 14: Rubber ring 16: Rubber sleeve unit 16a, 16b: Divided body 18: -th chamber, 20: Second chamber 2OA, 20b: Second chamber and a half! 22: Incompressible fluid 24: Flange portion 26: Large diameter portion
28: Medium diameter part 30: Small diameter part 32: Flange part 34: Mounting bracket 38: Caulking metal fittings 40: Outer cylinder ring 22- 42 (a, b): Rubber (half part) 44 (a, b): Inner cylinder Body (half part) 46 (11, b): Exterior cylinder body (half part) 48.50: Notch 52: Communication circumferential groove 60: Gab mount 62: Body member 64: Frame member
66: Mounting bolt 76: Cushion 78 Bracket 80: Tension rod Applicant Tokai Rubber Industries Co., Ltd. 23- Figure 5 Figure 13 Figure 14 Figure 4a Figure 15

Claims (6)

【特許請求の範囲】[Claims] (1)軸心方向の一端部におい・て側方に延びる7ラン
グ部を備え、所定の取付軸が挿通せしめられる内筒金具
と、 該内筒金具の外方にあって同心的に配置され、且つ該内
筒金具の7ラング部と同じ側にあって軸心方向に所定の
距離を隔てて対向する7ラング部を有する外筒金具と、 該内筒金具の7ラング部と該外筒金具の7ラング部との
間に配置された円環状の第一の弾性部材と、 該内筒金具と該外筒金具の対向する筒状部分間に配置さ
れた第二の弾性部材と、 前記第一の弾性部材の円環形状の内側に位置し、主とし
て該第−の弾性部材、前記内筒金具及び前記第二の弾性
部材にて囲まれた第一の室と、 前記第二の弾性部材内に形成され、その周方向に配置さ
れた複数の別個の第二の室と、前記第一の室と第二の室
とを相互に連通ぜしめると共に、該複数の第二の室を相
互に連通せしめる連通機構と、 前記第一の室及び第二の室に封入された所定の非圧縮性
流体とを、 含むことを特徴とする防振支持体。
(1) An inner cylindrical metal fitting having seven rungs extending laterally at one end in the axial direction, into which a predetermined mounting shaft is inserted; , and an outer cylindrical metal fitting having a 7-rung portion on the same side as the 7-rung portion of the inner cylindrical metal fitting and facing each other at a predetermined distance in the axial direction; and the 7-lung portion of the inner cylindrical metal fitting and the outer cylinder. a first annular elastic member disposed between the seven rung portions of the metal fitting; a second elastic member disposed between opposing cylindrical portions of the inner cylindrical fitting and the outer cylindrical fitting; a first chamber located inside the annular shape of the first elastic member and mainly surrounded by the second elastic member, the inner cylindrical fitting, and the second elastic member; A plurality of separate second chambers formed within the member and disposed in the circumferential direction thereof, the first chamber and the second chamber being in communication with each other, and the plurality of second chambers being arranged in the circumferential direction thereof. A vibration isolating support comprising: a communication mechanism that communicates with each other; and a predetermined incompressible fluid sealed in the first chamber and the second chamber.
(2)前記連通機構が、前記内筒金具の外周面に形成さ
れた連通周溝と、該連通周溝と前記第一の室とを連通せ
しめる第一の連通部と、該連通周溝と前記第二の室の各
々とをそれぞれ連通せしめる第二の連通部とを含み、該
連通周溝を介して、第一の室及び複数の第二の室の全て
が相互に同時に連通せしめられる特許請求の範囲第1項
記載の防振支持体。
(2) The communication mechanism includes a communication circumferential groove formed on the outer circumferential surface of the inner cylindrical fitting, a first communication portion that communicates the communication circumferential groove with the first chamber, and a communication circumferential groove. A patent that includes a second communication portion that communicates with each of the second chambers, and allows the first chamber and all of the plurality of second chambers to communicate with each other at the same time via the communication circumferential groove. A vibration-proof support according to claim 1.
(3)前記第二の弾性部材が、その外周面と内周面とに
それぞれ固着された外装筒体と内装筒体を介して、前記
外筒金具と内筒金具との間に圧入せしめられる特許請求
の範囲第1項記載の防振支持体。
(3) The second elastic member is press-fitted between the outer cylindrical metal fitting and the inner cylindrical metal fitting via an outer cylindrical body and an inner cylindrical body fixed to the outer circumferential surface and inner circumferential surface of the second elastic member, respectively. A vibration-proof support according to claim 1.
(4)  前記外装筒体及び内装筒体を有する第二の弾
性部材が軸心方向に2分された構造を有し、それら分割
されたものの接続によって前記複数の第二の室が該第二
の弾性部材内で、径方向に前記外装筒体と内装筒体とで
囲まれて、周方向に別個に形成される特許請求の範囲第
3項記載の防振支持体。
(4) The second elastic member having the outer cylindrical body and the inner cylindrical body has a structure in which it is divided into two in the axial direction, and the plurality of second chambers are connected to the second elastic member by connecting the divided parts. 4. The vibration isolating support according to claim 3, which is surrounded in the radial direction by the outer cylindrical body and the inner cylindrical body and formed separately in the circumferential direction within the elastic member.
(5)  前記第一の室側に圧入、配置せしめられる前
記第二の弾性部材の分割体が位置する前記内筒金具の外
周面部分に、該分割体の内装筒体部分よりも短い軸方向
長さにおいて、小径部を設け、該小径部と前記内装筒体
部分とによって連通周溝を形成せしめる一方、該連通周
溝と前記第一の室とを連通せしめる第一の連通部と、該
連通周溝と前記第二の室の各々とをそれぞれ連通せしめ
る第二の連通部とを設け、これら連通周溝、第−及び第
二の連通部によって前記連通機構を形成せしめたことを
特徴とする特許請求の範囲第4項記載の防振支持体。
(5) On the outer circumferential surface portion of the inner cylindrical fitting where the divided body of the second elastic member that is press-fitted and arranged on the first chamber side is located, an axial direction shorter than the inner cylindrical body portion of the divided body is provided. A first communication portion is provided in the length, and a communication circumferential groove is formed by the small diameter portion and the inner cylindrical body portion, and a first communication portion that communicates the communication circumferential groove with the first chamber; A second communication portion is provided for communicating the communication circumferential groove and each of the second chambers, and the communication mechanism is formed by the communication circumferential groove and the first and second communication portions. The vibration isolating support according to claim 4.
(6)前記第一の弾性部材の外方への変形を阻11−し
得る部材を、該第−の弾性部材の外周部に設けたことを
特徴とする特許請求の範囲第1項乃至第5項の何れかに
記載の防振支持体。
(6) A member capable of preventing outward deformation of the first elastic member is provided on the outer periphery of the second elastic member. The anti-vibration support according to any of Item 5.
JP57145647A 1982-08-23 1982-08-23 Vibration preventing support Granted JPS5937349A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP57145647A JPS5937349A (en) 1982-08-23 1982-08-23 Vibration preventing support

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP57145647A JPS5937349A (en) 1982-08-23 1982-08-23 Vibration preventing support

Publications (2)

Publication Number Publication Date
JPS5937349A true JPS5937349A (en) 1984-02-29
JPS6361536B2 JPS6361536B2 (en) 1988-11-29

Family

ID=15389841

Family Applications (1)

Application Number Title Priority Date Filing Date
JP57145647A Granted JPS5937349A (en) 1982-08-23 1982-08-23 Vibration preventing support

Country Status (1)

Country Link
JP (1) JPS5937349A (en)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6071749U (en) * 1983-10-22 1985-05-21 トヨタ自動車株式会社 Cushion rubber device
JPS60118041U (en) * 1984-01-19 1985-08-09 本田技研工業株式会社 fluid filled bush
JPS60201136A (en) * 1984-03-26 1985-10-11 Toyota Motor Corp Vibro-isolating supporter filled with fluid
JPS61144444A (en) * 1984-12-19 1986-07-02 Tokai Rubber Ind Ltd Bush containing fluid
JPS61166250U (en) * 1985-04-03 1986-10-15
FR2587429A1 (en) * 1985-09-13 1987-03-20 Peugeot Hydro-elastic wedge with at least two directions of damping
FR2587774A1 (en) * 1985-09-26 1987-03-27 Tokai Rubber Ind Ltd ELASTIC SUPPORT WITH FLUID FILLING
US4690389A (en) * 1984-08-07 1987-09-01 Avon Industrial Polymers Limited Hydraulically damped mounting device
US4700934A (en) * 1985-04-19 1987-10-20 Metzeler Kautschuk Gmbh Pretensionable and hydraulically damped mounting element
JPS62202554U (en) * 1987-02-26 1987-12-24
JPS62202553U (en) * 1987-02-26 1987-12-24
FR2605693A1 (en) * 1986-10-27 1988-04-29 Hutchinson Improvements to anti-vibration hydraulic supports
US4871151A (en) * 1986-06-30 1989-10-03 Tokai Rubber Industries, Ltd. Fluid-filled resilient bushing
JPH0226337A (en) * 1988-07-13 1990-01-29 Nissan Motor Co Ltd Inner-outer cylinder type fluid sealed vibration isolator
US4955589A (en) * 1987-12-23 1990-09-11 Avon Industrial Polymers Limited Hydraulically damped mounting device
EP0438559A1 (en) * 1989-07-18 1991-07-31 Lord Corporation Three-axis fluid-filled mount
FR2659712A1 (en) * 1990-03-16 1991-09-20 Hutchinson IMPROVEMENTS TO HYDRAULIC ANTI-VIBRATION SLEEVES.
FR2659713A1 (en) * 1990-03-16 1991-09-20 Hutchinson Improvements to hydraulic anti-vibration sleeves
US5060918A (en) * 1989-03-23 1991-10-29 Tokai Rubber Industries, Ltd. Fluid-filled cylindrical elastic connector having two orifice passages with different cross sectional areas
US5088702A (en) * 1989-07-31 1992-02-18 Hutchinson Hydraulic antivibratory sleeves
US5263815A (en) * 1990-12-24 1993-11-23 Boge Ag Engine mounting for motor vehicles
US5386973A (en) * 1992-05-15 1995-02-07 Boge Ag Elastomeric bearing
FR2726340A1 (en) * 1994-10-31 1996-05-03 Daimler Benz Ag ELASTOMERIC SUPPORT AND HYDRAULIC DAMPING
FR2735833A1 (en) * 1995-06-23 1996-12-27 Tokai Rubber Ind Ltd FLUID-FILLED CUSHIONING DEVICE WITH HIGH ELASTIC RIGIDITY IN TWO MUTUALLY PERPENDICULAR DIRECTIONS
WO2018225289A1 (en) * 2017-06-09 2018-12-13 株式会社ブリヂストン Anti-vibration device

Cited By (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0213789Y2 (en) * 1983-10-22 1990-04-16
JPS6071749U (en) * 1983-10-22 1985-05-21 トヨタ自動車株式会社 Cushion rubber device
JPH0212343Y2 (en) * 1984-01-19 1990-04-06
JPS60118041U (en) * 1984-01-19 1985-08-09 本田技研工業株式会社 fluid filled bush
JPS60201136A (en) * 1984-03-26 1985-10-11 Toyota Motor Corp Vibro-isolating supporter filled with fluid
US4690389A (en) * 1984-08-07 1987-09-01 Avon Industrial Polymers Limited Hydraulically damped mounting device
JPS61144444A (en) * 1984-12-19 1986-07-02 Tokai Rubber Ind Ltd Bush containing fluid
JPH0229899B2 (en) * 1984-12-19 1990-07-03 Tokai Rubber Ind Ltd
JPS61166250U (en) * 1985-04-03 1986-10-15
US4700934A (en) * 1985-04-19 1987-10-20 Metzeler Kautschuk Gmbh Pretensionable and hydraulically damped mounting element
FR2587429A1 (en) * 1985-09-13 1987-03-20 Peugeot Hydro-elastic wedge with at least two directions of damping
US4739979A (en) * 1985-09-26 1988-04-26 Tokai Rubber Industries, Ltd. Fluid-filled resilient support structure
FR2587774A1 (en) * 1985-09-26 1987-03-27 Tokai Rubber Ind Ltd ELASTIC SUPPORT WITH FLUID FILLING
US4871151A (en) * 1986-06-30 1989-10-03 Tokai Rubber Industries, Ltd. Fluid-filled resilient bushing
FR2605693A1 (en) * 1986-10-27 1988-04-29 Hutchinson Improvements to anti-vibration hydraulic supports
JPS62202553U (en) * 1987-02-26 1987-12-24
JPS62202554U (en) * 1987-02-26 1987-12-24
US4955589A (en) * 1987-12-23 1990-09-11 Avon Industrial Polymers Limited Hydraulically damped mounting device
JPH0226337A (en) * 1988-07-13 1990-01-29 Nissan Motor Co Ltd Inner-outer cylinder type fluid sealed vibration isolator
US5060918A (en) * 1989-03-23 1991-10-29 Tokai Rubber Industries, Ltd. Fluid-filled cylindrical elastic connector having two orifice passages with different cross sectional areas
EP0438559A1 (en) * 1989-07-18 1991-07-31 Lord Corporation Three-axis fluid-filled mount
US5088702A (en) * 1989-07-31 1992-02-18 Hutchinson Hydraulic antivibratory sleeves
FR2659712A1 (en) * 1990-03-16 1991-09-20 Hutchinson IMPROVEMENTS TO HYDRAULIC ANTI-VIBRATION SLEEVES.
FR2659713A1 (en) * 1990-03-16 1991-09-20 Hutchinson Improvements to hydraulic anti-vibration sleeves
US5172893A (en) * 1990-03-16 1992-12-22 Hutchison Hydraulic antivibratory sleeves
US5263815A (en) * 1990-12-24 1993-11-23 Boge Ag Engine mounting for motor vehicles
US5386973A (en) * 1992-05-15 1995-02-07 Boge Ag Elastomeric bearing
FR2726340A1 (en) * 1994-10-31 1996-05-03 Daimler Benz Ag ELASTOMERIC SUPPORT AND HYDRAULIC DAMPING
FR2735833A1 (en) * 1995-06-23 1996-12-27 Tokai Rubber Ind Ltd FLUID-FILLED CUSHIONING DEVICE WITH HIGH ELASTIC RIGIDITY IN TWO MUTUALLY PERPENDICULAR DIRECTIONS
US5690320A (en) * 1995-06-23 1997-11-25 Tokai Rubber Industries, Ltd. Fluid-filled damping device having a large spring stiffness values in two mutually perpendicular diametric directions
WO2018225289A1 (en) * 2017-06-09 2018-12-13 株式会社ブリヂストン Anti-vibration device
CN110573764A (en) * 2017-06-09 2019-12-13 株式会社普利司通 Vibration isolation device
EP3636954A4 (en) * 2017-06-09 2021-03-03 Bridgestone Corporation Anti-vibration device
US11231083B2 (en) 2017-06-09 2022-01-25 Bridgestone Corporation Anti-vibration device

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