JPS6361536B2 - - Google Patents
Info
- Publication number
- JPS6361536B2 JPS6361536B2 JP57145647A JP14564782A JPS6361536B2 JP S6361536 B2 JPS6361536 B2 JP S6361536B2 JP 57145647 A JP57145647 A JP 57145647A JP 14564782 A JP14564782 A JP 14564782A JP S6361536 B2 JPS6361536 B2 JP S6361536B2
- Authority
- JP
- Japan
- Prior art keywords
- communication
- chamber
- elastic member
- inner cylindrical
- metal 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.)
- Expired
Links
- 239000002184 metal Substances 0.000 claims description 39
- 239000012530 fluid Substances 0.000 claims description 26
- 230000004323 axial length Effects 0.000 claims 1
- 238000013016 damping Methods 0.000 description 20
- 230000000694 effects Effects 0.000 description 11
- 239000000463 material Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 230000002093 peripheral effect Effects 0.000 description 5
- 239000000853 adhesive Substances 0.000 description 3
- 230000001070 adhesive effect Effects 0.000 description 3
- 238000002955 isolation Methods 0.000 description 3
- 238000004073 vulcanization Methods 0.000 description 3
- 230000002238 attenuated effect Effects 0.000 description 2
- 239000002131 composite material Substances 0.000 description 1
- 239000013013 elastic material Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 229920001515 polyalkylene glycol Polymers 0.000 description 1
- 229920000642 polymer Polymers 0.000 description 1
- 229920002545 silicone oil Polymers 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
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
- F16F13/16—Units 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)
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、自動車のボデイマウント乃至はキヤ
ブマウント、テンシヨンロツド乃至はストラツト
バーのクツシヨン（ブツシユ）等の防振支持体と
して、ゴムブロツクを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つたので
ある。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
できことが要求されるからである。 Conventionally, structures in which a rubber block is interposed between two mounting brackets have been used as vibration-proof supports for automobile body mounts, cab mounts, tension rods, strut bar cushions, etc. 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 can be sufficiently achieved. I couldn't satisfy it. 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、これによつて一応は低
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つた。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
取付け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つたのである。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 such demands, an elastic support body having a structure that utilizes the elasticity of rubber and the flow resistance of fluid has been proposed in Japanese Patent Application Laid-open No. 5376/1983. 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. With this, it was 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 vibrations in the direction perpendicular to that were limited. 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. This made its installation difficult, and its damping effect was also insufficient. In addition,
Such a fluid-filled elastic support body also has the problem that the spring constant ratio (lateral spring constant/vertical spring constant) cannot be kept large.
ここにおいて、本発明は、かかる事情に鑑みて
為されたものであつて、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 improve a vibration isolation support that uses a fluid medium and has high damping characteristics. It is in.
また、本発明の他の目的は、流体媒体を用いて
それの二つの室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 utilize a fluid medium and its flow resistance between two chambers to
The object of the present invention is to provide a vibration-proof support that simultaneously exhibits low dynamic spring characteristics and high damping characteristics, while also being able to exhibit such performance in two orthogonal directions.
そして、これらの目的を達成するため、本発明
にあつては、(a)軸心方向の一端部において側方に
延びるフランジ部を備え、所定の取付軸が挿通せ
しめられる内筒金具と、(b)該内筒金具の外方にあ
つて同心的に配置され、且つ該内筒金具のフラン
ジ部と同じ側にあつ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、(d)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
の弾性部材の円環形状の内側に位置し、主として
該第一の弾性部材、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、(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、(h)前記一の室及び第二の
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 a flange portion extending laterally at one end in the axial direction, into which a predetermined mounting shaft is inserted; b) An outer cylinder having a flange portion which is arranged concentrically outside the inner cylinder metal fitting, and which is on the same side as the flange portion of the inner cylinder metal fitting and faces a predetermined distance in the axial direction. metal fittings and (c)
(d) an annular first elastic member disposed between the flange portion of the inner tube fitting and the flange portion of the outer tube fitting; and (d) opposing cylindrical portions of the inner tube fitting and the outer tube fitting. (e) a second elastic member disposed in between; and (e) located inside the annular shape of the first elastic member, mainly the first elastic member, the inner cylinder fitting, and the second elastic member. (f) a plurality of second chambers formed in the circumferential direction within the second elastic member; (g) the first chamber and the second chamber; and (h) a predetermined incompressible fluid sealed in the first chamber and the second chamber.
従つて、かかる構成の防振支持体にあつては、
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空間の流体の流通
抵抗とによつて、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、連通機構によつ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つて効果的
な減衰作用が発揮され得ることとなつたのであ
る。また、このような直角な２方向における振動
に対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
（軸心に直角な方向のバネ定数／軸心方向のバネ
定数）を従来の流体入り防振支持体よりも大とす
ることが可能となつたのである。 Therefore, in the case of a vibration-proof support with such a structure,
An effective damping effect can be exerted against the vibration in the axial direction by the elasticity of the first elastic member and the flow resistance of the fluid in the first chamber and the second space. In addition, vibrations applied from a direction perpendicular to the axis are handled by the elasticity of the second elastic member and the resistance to fluid flow between the plurality of second chambers communicated by the communication mechanism. As a result, an effective damping effect can be exerted. Furthermore, in addition to the damping effect on vibrations in two orthogonal directions, a damping effect in a composite direction of these two directions can also be naturally achieved. Since the spring constant can be made different by changing the material, the spring constant ratio (spring constant in the direction perpendicular to the axis/spring constant in the axis direction) is different from that of conventional fluid-filled vibration isolation supports. It became possible to make it larger than the body.
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
振支持体たるキヤブマウントの１例が示されてい
るが、そこにおいてキヤブマウントは、それをボ
デイ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１０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
スリーブユニツト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
スリーブユニツト１６とによつて形成される第一
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, FIGS. 1 and 2 show an example of a cab mount which is a vibration-proof support according to the present invention. An inner cylindrical metal fitting 10 into which a bolt is inserted, and an outer cylindrical metal fitting 12 arranged outside the inner cylindrical metal fitting 10 at a predetermined distance apart.
, a rubber ring 14 as a first elastic member and a rubber sleeve unit 16 constituting a second elastic member, which are respectively arranged between the inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12, and the inner cylindrical metal fitting. 10 and the outer cylindrical fitting 12, from a predetermined incompressible fluid 22 filled in a first chamber 18 and a second chamber 20 formed by the rubber ring 14 and the rubber sleeve unit 16. , substantially consisting of.
より具体的には、かかるキヤブマウントの最内
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を備えた筒体であつて、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２
６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つて中径部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
わ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、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からやや離
れた位置においてその外周面に対して取付用ブラ
ケツト３４が溶接等によつて固定せしめられてい
る。なお、かかるブラケツト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
つて固着せしめられており、更に該ゴムリング１
４の端面にリング状のカシメ金具３８が加硫接着
等によつ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４０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。 More specifically, as shown in FIG. 3, the inner cylinder metal fitting 10 constituting the innermost cylinder of the cab mount is a cylinder body provided 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, and the large diameter portion 2
6, a medium diameter portion 28 extends toward the end opposite to the end where the flange portion 24 is provided, and a position slightly away from the large diameter portion 26 is provided in this medium diameter portion 28. A small diameter portion 30 having a predetermined length: 1 is provided at. In addition, the outer cylinder fitting 12
As shown in FIGS. 4 and 5, the is provided with a flange portion 32 extending laterally at one end in the axial direction thereof, and at a position slightly away from the flange portion 32, the outer circumferential surface of the A mounting bracket 34 is fixed by welding or the like. 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.
A ring-shaped caulking metal fitting 38 is fixed to the end surface of 4 by vulcanization adhesive or the like. Further, an outer cylindrical ring 40 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、ゴムスリーブユニツト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
つて、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
れ加硫接着等によつて固着せしめられた内装筒体
半部４４ａ，４４ｂ及び外装筒体半部４６ａ，４
６ｂ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４
４ａ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４
８，５０が設けられている。また、各分割体１６
ａ，１６ｂのゴム半部４２ａ，４２ｂ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つた
複数個の第二室半部２０ａ，２０ｂが設けられて
おり、これら分割体１６ａ，１６ｂ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＋４２ｂ）内には、径
方向に内装筒体４４と外装筒体４６とによつて囲
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。 Furthermore, as shown in FIGS. 6 and 9, the rubber sleeve unit 16 consists of two divided bodies 16a and 16b that are axially divided into two parts, and both of these divided bodies have the same diameter. cylindrical rubber half parts 42a, 42b, inner cylinder half parts 44a, 44b and outer cylinder half parts 46a, 4 fixed to the inside and outside thereof by vulcanization adhesive or the like, respectively.
6b. Note that the inner cylindrical half portion 4 of one of the divided bodies 16a shown in FIG.
4a has a plurality of notches 4 at both ends in the axial direction, as shown in FIGS. 7 and 8.
8,50 are provided. In addition, each divided body 16
A plurality of second chamber halves 20a, 20b having approximately the same phase difference are provided at corresponding positions in the circumferential direction of the rubber halves 42a, 42b of the rubber halves 42a, 16b. Inside the rubber 42 (42a+42b) which becomes the second elastic member when the end faces in the axial direction are connected and are connected, there is a circumference surrounded in the radial direction by the inner cylinder 44 and the outer cylinder 46. A plurality of sealed second chambers 20 are formed separately in the direction.
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
本発明に従うキヤ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，１６ｂが、水、ポリアルキレング
リコール、シリコーン油や低分子量重合体等の非
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
１６ｂを各分割体の開口する第二室半部２０ａ，
２０ｂを付き合わせるようにして、圧入せしめる
のである。この圧入操作によつて、第二室半部２
０ａ，２０ｂ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
もつて形成されることとなる。なお、この分割体
１６ａ，１６ｂの圧入によつて形成された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。 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 the components shown in FIGS. 6 to 10 are assembled. The two divided bodies 16a and 16b form an outer cylindrical metal fitting that constitutes the component shown in FIGS. 4 and 5 in an incompressible fluid 22 such as water, polyalkylene glycol, silicone oil, or a low molecular weight polymer. The divided body 16a is press-fitted into the 12 cylindrical portions so that it is located on the flange portion 32 side, and then the other divided body 16b is inserted into the second chamber half portion 20a, which has an opening in each divided body.
20b are brought together and press-fitted. By this press-fitting operation, the second chamber half 2
0a and 20b 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 and 16b 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３２側に位置するようにして
圧入せしめられることとなる。即ち、内筒金具１
０の中径部２８が各分割体１６ａ，１６ｂの内装
筒体半部４４ａ，４４ｂに圧入せしめられるので
ある。かかる内筒金具１０の圧入によつて、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によつ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３８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つて、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
によつて第一室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
圧入によつて、かかる第一室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
一室１８と複数の第二室２０とは内筒金具１０の
筒状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４８，５０によつてそれぞれ連通され
ている。従つて、第一室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５２を介して連通せし
められているのである。 Next, with respect to the divided bodies 16a and 16b press-fitted into the outer cylindrical fitting 12, the inner cylindrical fitting 10 shown in FIG. In this way, it is press-fitted. That is, the inner cylinder fitting 1
The middle diameter portion 28 of 0 is press-fitted into the inner cylindrical half portions 44a, 44b of each divided body 16a, 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 the communicating circumferential groove 52 is formed therein by the first inner cylindrical half 44a. It will be formed as shown in the figure and FIG. Further, the flange portion 24 of the inner cylinder metal fitting 10 is abutted on and accommodated in a caulking metal fitting 38, and the flange portion 24 is held liquid-tight by the caulking metal fitting 38 by caulking the caulking metal fitting 38. , the first chamber 18 is connected to the large diameter portion 26 of the inner cylindrical fitting 10 by the inner cylindrical fitting 10, the rubber ring 14, the divided body 16a, and the outer cylindrical fitting 12.
The first chamber 18, like the second chamber 20, is filled with an incompressible fluid 22 by being press-fitted in an incompressible fluid formed around the first chamber 18. Further, the first chamber 18 and the plurality of second chambers 20 formed in this way are provided in the divided body 16a, respectively, with respect to the communication circumferential groove 52 formed around the cylindrical part of the inner cylinder fitting 10. They are communicated by cutouts 48 and 50 at both ends. Therefore, the first 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.
従つて、かかる構成のキヤブマウントにあつて
は、第１１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、第一室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２０内に移
動するようになり、そしてこの移動に際しての流
動抵抗によつて、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。
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
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一室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つて、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。 Therefore, in the case of the cab mount having such a structure, when vibration as a load W is applied in the axial direction, the incompressible fluid 22 in the first chamber 18 is moved to the inner cylinder half as shown in FIG. Notch 48 of 44a
(first communication part), a communication circumferential groove 52 formed on the outer peripheral surface of the inner cylinder fitting 10, and a notch 50 (second communication part) in the inner cylinder half part 44a to move into the second chamber 20. The flow resistance during this movement effectively damps such vibrations, that is, vibrations in the low frequency range.
Here, since the outer cylindrical ring 40 is provided on the outer periphery of the rubber ring 14, outward deformation of the rubber ring 14 is effectively suppressed, and the first chamber 18 located inside thereof is effectively suppressed. It is now possible to effectively transform the Furthermore, with respect to 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, vibration noise in that region can be effectively reduced. is possible.
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が加わつ
たときにあつては、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、これによつて低周波振動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
が加わつたときには、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ツト１６
（分割体１６ａ＋分割体１６ｂ）を構成するゴム
４２，ａ，ｂの弾性によつ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つて、その振動騒音の低
減を達成することが可能である。 On the other hand, when vibration is applied in a direction perpendicular to the axial direction, that is, when a load W as shown by the arrow in FIG. 12 is applied, the second chamber 20 on the side to which the load is applied is deformed. The incompressible fluid 22 filled in the inner cylinder half 44a of the divided body 16a passes through the notch 50 of the inner cylinder half 44a, the communication circumferential groove 52, and again through the notch 50 of the inner cylinder half 44a to the other second chamber. 20
As a result, the low frequency vibrations W are effectively attenuated. Furthermore, when high frequency vibration is applied, the rubber sleeve unit 16 interposed between the inner cylinder 10 and the outer cylinder 12
(divided body 16a + divided body 16b) is damped by the elasticity of the rubber 42, a, b, and therefore, by selecting a rubber material that can withstand such high frequency vibration, the vibration noise can be reduced. It is possible to achieve a reduction in
このように、かかる構成のキヤブマウントにあ
つては、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の両フランジ部２
４，３２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２
２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
ことによつ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つては、その高
周波振動及び低周波振動はゴムスリーブユニツト
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
抵抗によつ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つて、
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
ーブユニツト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
可能となつたのである。 In the cab mount having such a configuration, high-frequency vibrations and low-frequency vibrations in the axial direction are transmitted to both the flange portions 2 of the inner cylindrical metal fitting 10 and the outer cylindrical metal fitting 12.
4, 32, as well as the elasticity of the rubber ring 14 provided between the first chamber 18 and the second chamber 2.
2 can be moved effectively through the notch 48, the communication 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. Furthermore, the vibration damping effect in two directions is further enhanced by the fact that each rubber part and each chamber attenuate the component forces of high-frequency vibrations and low-frequency vibrations from these combined directions.
As a whole, an effective damping effect can be exerted. 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. It has also become possible to increase the spring constant in the direction perpendicular to the center direction/spring constant in the axial direction.
なお、上例にあつては、ゴムスリーブユニツト
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。なお、第二室２０が２個の場合にあつて
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
なるものである。 In the above example, 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 may be provided. However, it is also possible to simply provide two second chambers 20, as shown in FIGS. 13 and 14, for example. 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. This becomes effective only when vibration is applied as a load W in the direction of the arrow.
また、第１５図には、前記例示のキヤブマウン
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ヤブマウント６
０はボデイ部材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。即ち、フレーム部
材６４に対してキヤブマウント６０を構成する外
筒金具１２の外周面に固着されている取付用ブラ
ケツト３４を介して固定せしめられる一方、ボデ
イ部材６２に対しては、該ボデイ部材６２を貫通
する取付ボルト６６がキヤブマウント６０の内筒
金具１０内を挿通せしめられ、そして止め部材６
８を介してナツト７０で締めつけることによつて
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、形成されたストツパであり、７
４はワツシヤである。 Further, FIG. 15 shows a state in which the above-mentioned cab mount is actually attached to an automobile, in which a cab mount 6 according to the present invention is shown.
0 is assembled between the body member 62 and the frame member 64. That is, it is fixed to the frame member 64 via the mounting bracket 34 fixed to the outer peripheral surface of the outer cylinder metal fitting 12 constituting the cab mount 60, while the body member 62 is fixed to the body member 62. A penetrating mounting bolt 66 is inserted into the inner cylinder fitting 10 of the cab mount 60, and the stop member 6
It is assembled by tightening with a nut 70 via the screw 8. In addition, 72 in the figure
7 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;
4 is Watsusha.
また、第１６図，第１７図には、自動車のサス
ペンシヨンのテンシヨンロツドの取付けに際して
用いられるクツシヨンに本発明を適用した例が示
されており、そこにおいて本発明に従うクツシヨ
ン７６は公知のように、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ツ
ト７８にテンシヨンロツド８０の先端部を取り付
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、テンシヨンロツド８０の先端部がクツシヨン
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ツシヨン
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つて取り付けられている
のである。なお、ここに例示のクツシヨン７６
は、先に示したキヤ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を省略することとする。勿
論、このような構造のクツシヨン７６にあつて
も、テンシヨンロツド８０から加えられるクツシ
ヨン７６の軸方向の主荷重は、第一室、第二室間
の流体の移動によつて効果的に減衰せしめられ、
その減衰特性が著しく向上させられ得る他、かか
る軸方向に直角な方向の振動、更にはそれら二方
向の複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 for attaching a tension rod to a suspension of an automobile, in which the cushion 76 according to the present invention is, as is known, In order to attach the tip of the tension rod 80 to a bracket 78 attached to a side member or cross member of the vehicle body, the two tension rods are combined and used as a pair. That is, as shown in FIG. 16, the tension rod 80 is inserted into the inner cylindrical fitting of each cushion 76 with its distal end portion touching the second chamber side end of each cushion 76. Natsuto 82
It is attached by tightening it. In addition, the cushion 76 illustrated here
Since this has the same structure as the cab mount shown earlier, similar parts will be given the same reference numerals and detailed explanation will be omitted. Of course, even with the cushion 76 having such a structure, the main load in the axial direction of the cushion 76 applied from the tension rod 80 can be effectively attenuated by the movement of fluid between the first chamber and the second chamber. ,
In addition to being able to significantly improve its damping characteristics, it is also possible to exhibit effective damping performance against vibrations in a direction perpendicular to the axial direction, as well as vibrations in a combination of these two 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。例えば、前例
においては、第一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、第一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フランジ部間
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４０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。更に、例示の具体例にあつ
ては、フランジ部２４が内筒金具１０の一端に固
設されて、一体的に形成された構造が採用されて
いるが、これに代えて、フランジ部２４が内筒金
具１０とは別体とされた構造、例えばフランジ部
形成部材を内筒金具の一端部にカシメ固定や嵌合
等によつて取り付けてなる構造も、適宜に採用さ
れ得るものであ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. 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 communicate 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, although it is desirable to install the outer cylindrical ring 40 disposed on the outer periphery of the rubber ring 14 as the first elastic material disposed between the flange portions of the inner cylindrical metal fitting and the outer cylindrical metal fitting, In some cases, the rubber ring 14 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. Furthermore, in the specific example illustrated, the flange portion 24 is fixed to one end of the inner cylinder fitting 10, and an integrally formed structure is adopted, but instead of this, the flange portion 24 is A structure that is separate from the inner cylindrical fitting 10, for example, a structure in which a flange forming member is attached to one end of the inner cylindrical fitting by caulking, fitting, etc., may also be adopted as appropriate. Needless to say.
第１図は本発明に従う防振支持体の一例に係る
キヤ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１
０図はそれぞれ第１図に示すキヤブマウントの構
成部品を示すものであつて、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、ブラケツト、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
スリーブユニツ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
ーブユニツトを形成する他の一つの分割体の縦断
面、第１０図はその平面図、第１１図は軸心方向
に振動が加わつ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図、
第１２図は軸心方向に対して直角な方向の振動が
加わつたときの非圧縮性流体の流れを説明するた
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１
４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
図に示すキヤ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
例であるテンシヨンロツドのクツシヨンの取付状
態を示す断面図であり、第１７図は第１６図にお
ける―断面図である。
１０：内筒金具、１２：外筒金具、１４：ゴム
リング、１６：ゴムスリーブユニツト、１６ａ，
１６ｂ：分割体、１８：第一室、２０：第二室、
２０ａ，２０ｂ：第二室半部、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：
取付用ブラケツト、３８：カシメ金具、４０：外
筒リング、４２，ａ，ｂ：ゴム（半部）、４４，
ａ，ｂ：内装筒体（半部）、４６，ａ，ｂ：外装
筒体（半部）、４８，５０：切欠き、５２：連通
周溝、６０：キヤブマウント、６２：ボデイ部
材、６４：フレーム部材、６６：取付ボルト、７
６：クツシヨン、７８：ブラケツト、８０：テン
シヨンロツド。
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 in the figure. Figures 3 to 1
Figure 0 shows the components of the cab mount shown in Figure 1, Figure 3 is a half-cut front view of the cylindrical metal fitting, and Figure 4 shows the outer cylinder metal fitting, rubber ring, bracket, and outer cylinder ring. A plan view of the included parts, FIG. 5 is a half-cut front view thereof, FIG. 6 is a longitudinal cross-sectional view of one of the divided bodies forming the rubber sleeve unit, FIG. 7 is a bottom view thereof, and FIG. 8 is used therein. A perspective view of a half of the inner cylindrical body, FIG. 9 is a longitudinal section of another divided body forming the rubber sleeve unit, FIG. 10 is a plan view thereof, and FIG. 11 is a diagram when vibration is applied in the axial direction. A cross-sectional half view corresponding to FIG. 1 for explaining the flow of incompressible fluid in
FIG. 12 is a diagram corresponding to FIG. 2 for explaining the flow of incompressible fluid when vibration is applied in a direction perpendicular to the axial direction, and FIG. 13 is a diagram corresponding to another embodiment of the present invention. Figure 1 corresponding to Figure 2 according to the embodiment
4 is a diagram for explaining the movement of the incompressible fluid in the embodiment of FIG. 13, and FIG. 15 is a diagram for explaining the movement of the incompressible fluid in the embodiment of FIG.
FIG. 16 is a cross-sectional view showing the mounted state of the cab mount shown in the figure, and FIG.
FIG. 17 is a cross-sectional view showing the attachment state of the cushion of the tension rod as an example, and FIG. 17 is a cross-sectional view taken 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: first chamber, 20: second chamber,
20a, 20b: second chamber half part, 22: incompressible fluid, 24: flange part, 26: large diameter part, 28: medium diameter part, 30: small diameter part, 32: flange part, 34:
Mounting bracket, 38: Caulking metal fittings, 40: Outer cylinder ring, 42, a, b: Rubber (half part), 44,
a, b: Interior cylinder (half part), 46, a, b: Exterior cylinder (half part), 48, 50: Notch, 52: Communication circumferential groove, 60: Cab mount, 62: Body member, 64: Frame member, 66: Mounting bolt, 7
6: Cushion, 78: Bracket, 80: Tension rod.
Claims (1)
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、 該内筒金具の外方にあつて同心的に配置され、
且つ該内筒金具のフランジ部と同じ側にあつて軸
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、 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、 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、主として該第一の弾性部材、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せしめ
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。 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。 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。 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つて前記複数の第二
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。 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つて連通周溝を形
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、第一及び第二
の連通部によつ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。 ６ 前記第一の弾性部材の外方への変形を阻止し
得る部材を、該第一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。[Scope of Claims] 1. An inner cylindrical metal fitting having a flange portion extending laterally at one end in the axial direction, into which a predetermined mounting shaft is inserted, and concentrically arranged on the outside of the inner cylindrical metal fitting. is,
and an outer cylindrical metal fitting having a flange part on the same side as the flange part of the inner cylindrical metal fitting and facing each other at a predetermined distance in the axial direction; a flange part of the inner cylindrical metal fitting and a flange part of the outer cylinder metal fitting; a second elastic member disposed between opposing cylindrical portions of the inner cylindrical fitting and the outer cylindrical fitting; and the first elastic member. a first chamber located inside the annular shape of and mainly surrounded by the first elastic member, the inner cylindrical fitting, and the second elastic member; and a first chamber formed within the second elastic member. , a plurality of separate second chambers arranged in the circumferential direction thereof, and a communication mechanism that allows the first chamber and the second chamber to communicate with each other, and allows the plurality of second chambers to communicate with each other. and a predetermined incompressible fluid sealed in the first chamber and the second chamber. 2. The communication mechanism includes a communication circumferential groove formed on the outer circumferential surface of the inner cylindrical metal fitting, a first communication portion that allows communication between the communication circumferential groove and the first chamber, and a communication circumferential groove and the first chamber. and a second communication portion that communicates with each of the second chambers, and the first chamber and all of the plurality of second chambers are simultaneously communicated with each other via the communication circumferential groove. The anti-vibration support according to scope 1. 3. A patent claim in which 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 that are respectively fixed to the outer circumferential surface and inner circumferential surface of the second elastic member. The anti-vibration support according to item 1. 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. An axial length that is shorter than an inner cylindrical body portion of the divided body is provided on the outer circumferential surface portion of the inner cylindrical metal fitting where the divided body of the second elastic member that is press-fitted and placed on the first chamber side is located. wherein a small diameter portion is provided, a communication circumferential groove is formed by the small diameter portion and the inner cylinder portion, and a first communication portion that communicates the communication circumferential groove with the first chamber; A second communication portion is provided that communicates the communication circumferential groove with each of the second chambers, and the communication mechanism is formed by the communication circumferential groove and the first and second communication portions. A vibration-proof support according to claim 4, characterized in that: 6. Claims 1 to 5, characterized in that a member capable of preventing outward deformation of the first elastic member is provided on the outer periphery of the first elastic member.
The anti-vibration support described in any of paragraphs.
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 JPS5937349A (en) | 1984-02-29 |
| JPS6361536B2 true 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) |
Families Citing this family (25)
| 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 |
| DE3566023D1 (en) * | 1984-08-07 | 1988-12-08 | Avon Ind Polymers | Hydraulically damped mounting device |
| JPS61144444A (en) * | 1984-12-19 | 1986-07-02 | Tokai Rubber Ind Ltd | Bush containing fluid |
| JPS61166250U (en) * | 1985-04-03 | 1986-10-15 | ||
| DE3514268A1 (en) * | 1985-04-19 | 1986-10-23 | Metzeler Kautschuk GmbH, 8000 München | PRELVETABLE AND HYDRAULIC DAMPED BEARING ELEMENT |
| FR2587429B1 (en) * | 1985-09-13 | 1989-12-01 | Peugeot | HYDROELASTIC SHIM WITH AT LEAST TWO DAMPING DIRECTIONS |
| JPH0225947Y2 (en) * | 1985-09-26 | 1990-07-16 | ||
| JPS636248U (en) * | 1986-06-30 | 1988-01-16 | ||
| FR2605693B1 (en) * | 1986-10-27 | 1989-04-28 | Hutchinson | IMPROVEMENTS ON ANTI-VIBRATION HYDRAULIC SUPPORTS |
| JPS62202554U (en) * | 1987-02-26 | 1987-12-24 | ||
| JPS62202553U (en) * | 1987-02-26 | 1987-12-24 | ||
| GB8730005D0 (en) * | 1987-12-23 | 1988-02-03 | Avon Ind Polymers | Hydraulically damped mounting device |
| JP2848399B2 (en) * | 1988-07-13 | 1999-01-20 | 日産自動車株式会社 | Inner / outer cylinder type fluid-filled vibration isolator |
| JPH02124338U (en) * | 1989-03-23 | 1990-10-12 | ||
| US4962915A (en) * | 1989-07-18 | 1990-10-16 | Lord Corporation | Three-axis fluid-filled mount |
| FR2650356B1 (en) * | 1989-07-31 | 1994-05-27 | Hutchinson | IMPROVEMENTS MADE TO MAN CHONS HYDRAULIC ANTI-VIBRATOR |
| FR2659712B1 (en) * | 1990-03-16 | 1992-07-17 | Hutchinson | IMPROVEMENTS TO HYDRAULIC ANTI-VIBRATION SLEEVES. |
| FR2659713B1 (en) * | 1990-03-16 | 1994-07-22 | Hutchinson | IMPROVEMENTS IN HYDRAULIC ANTI-VIBRATION SLEEVES. |
| DE4041837C1 (en) * | 1990-12-24 | 1992-04-30 | Boge Ag, 5208 Eitorf, De | |
| DE4216185C2 (en) * | 1992-05-15 | 1994-12-08 | Boge Gmbh | Elastic rubber bearing |
| DE4438932C2 (en) * | 1994-10-31 | 1998-07-02 | Daimler Benz Ag | Hydro bearing |
| JP3477920B2 (en) * | 1995-06-23 | 2003-12-10 | 東海ゴム工業株式会社 | Fluid-filled anti-vibration support |
| JP2018204774A (en) * | 2017-06-09 | 2018-12-27 | 株式会社ブリヂストン | Vibration controller |
-
1982
- 1982-08-23 JP JP57145647A patent/JPS5937349A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5937349A (en) | 1984-02-29 |
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