JPS63266240A - Fluid-filled bush - Google Patents
Fluid-filled bushInfo
- Publication number
- JPS63266240A JPS63266240A JP10048287A JP10048287A JPS63266240A JP S63266240 A JPS63266240 A JP S63266240A JP 10048287 A JP10048287 A JP 10048287A JP 10048287 A JP10048287 A JP 10048287A JP S63266240 A JPS63266240 A JP S63266240A
- Authority
- JP
- Japan
- Prior art keywords
- fluid
- cylinder part
- inner cylinder
- fluid chambers
- axial direction
- 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.)
- Pending
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 138
- 238000013016 damping Methods 0.000 abstract description 19
- 239000012858 resilient material Substances 0.000 abstract 3
- 230000035807 sensation Effects 0.000 abstract 1
- 239000000725 suspension Substances 0.000 description 28
- 230000006835 compression Effects 0.000 description 11
- 238000007906 compression Methods 0.000 description 11
- 238000005192 partition Methods 0.000 description 6
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 239000003381 stabilizer Substances 0.000 description 2
- 239000000470 constituent Substances 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000000644 propagated effect Effects 0.000 description 1
- 230000003014 reinforcing effect Effects 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)
- Vehicle Body Suspensions (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、外筒部、外筒部の内側に同軸的に配された内
筒部、及び、外筒部と内筒部との間に介在せしめられた
弾性体等を備え、弾性体の内部に流体室が形成されて成
る流体入りブツシュに関する。Detailed Description of the Invention (Industrial Application Field) The present invention relates to an outer cylinder part, an inner cylinder part disposed coaxially inside the outer cylinder part, and a structure between the outer cylinder part and the inner cylinder part. The present invention relates to a fluid-filled bushing comprising an elastic body interposed between the body and the like, with a fluid chamber formed inside the elastic body.
（従来の技術）
車両のサスペンション装置を構成するサスペンションア
ームが車体に取り付けられる部分等には、−ｍに、車両
の走行時において車輪及びサスペンションアーム等を介
して車体に伝播する振動を低減させるためのブツシュが
配される。斯かるブツシュは、通常、サスペンションア
ームが挿通される内筒部と車体に固定される外筒部との
間にラバー等の弾性体が介在せしめられて成り、外筒部
と内筒部との間に作用する荷重が弾性体の変形によって
吸収されるようになされている。さらに、ブツシュを構
成する外筒部と内筒部との間に作用する。荷重に対する
減衰力を発生させるべく、弾性体の内部に形成された流
体室内にオイル等の流体が封入された流体入りブツシュ
も知られている。(Prior Art) In the parts where the suspension arms constituting the suspension system of the vehicle are attached to the vehicle body, -m is installed to reduce vibrations propagated to the vehicle body through the wheels and suspension arms, etc. when the vehicle is running. Bushes are arranged. Such a bushing usually consists of an elastic body such as rubber interposed between an inner cylinder part into which the suspension arm is inserted and an outer cylinder part which is fixed to the vehicle body. The load acting between them is absorbed by the deformation of the elastic body. Furthermore, it acts between the outer cylinder part and the inner cylinder part that constitute the bush. A fluid-filled bushing is also known in which a fluid such as oil is sealed in a fluid chamber formed inside an elastic body in order to generate a damping force against a load.
このような流体入りブツシュとして、例えば、実開昭６
１−１０８５４６号公報には、内筒部と外筒部との間に
介在せしめられた弾性体に形成された流体室内に、それ
を内筒部の軸方向に沿って複数に仕切る仕切部材が配置
され、斯かる仕切部材に、それによって仕切られる複数
の流体室を相互に連通させる連通部（上記公報ではオリ
フィスと称されている）が設けられたものが提案されて
いる。斯かる流体入りブツシュにおいては、仕切部材に
よって仕切られた複数の流体室の夫々の間で、連通部を
通じての流体の給排が行われることにより、内筒部の軸
方向に作用する荷重に対して減衰力が発生する。As such a fluid-filled bushing, for example,
1-108546 discloses a fluid chamber formed in an elastic body interposed between an inner cylinder part and an outer cylinder part, and a partition member that partitions the fluid chamber into a plurality of parts along the axial direction of the inner cylinder part. It has been proposed that such a partition member is provided with a communication portion (referred to as an orifice in the above publication) that allows a plurality of fluid chambers partitioned by the partition member to communicate with each other. In such a fluid-filled bushing, fluid is supplied and discharged through the communication portion between each of the plurality of fluid chambers partitioned by the partition member, thereby resisting the load acting in the axial direction of the inner cylinder portion. damping force is generated.
また、上述の如くにして内筒部の軸方向に作用する荷重
に対して減衰力を発生するのではな（、内筒部の軸方向
に直交する方向に作用する荷重に対して減衰力を発生す
るようにされた流体入りブツシュも知られている。In addition, instead of generating a damping force against a load acting in the axial direction of the inner cylinder as described above, Fluid-filled bushings adapted to generate electricity are also known.
（発明が解決しようとする問題点）
しかしながら、車両のサスペンション装置におけるサス
ペンションアームが車体に取り付けられる部分等の如く
の、車体前後方向及び車幅方向に沿う互いに直交する二
方向に荷重が作用するような位置に、上述の如くの流体
入りブツシュが配される場合には、直交する二方向に作
用する荷重のうちの一方に対しては減衰力が生じないた
め、良好な乗心地が得られないことになってしまう。そ
こで、このような問題に対処するためには、サスペンシ
ョンアームが車体に取り付けられる部分等に、内筒部の
軸方向に作用する荷重、及び、内筒部の軸方向に直交す
る方向に作用する荷重の夫々に対して減衰力を生じさせ
ることができるものとされた流体入りブツシュを配すこ
とが望まれるが、斯かる用途に供されるべき流体入りブ
ツシュは見当たらない。(Problem to be Solved by the Invention) However, when a load acts in two directions perpendicular to each other along the longitudinal direction and the width direction of the vehicle body, such as the part where the suspension arm of a vehicle suspension device is attached to the vehicle body, etc. If a fluid-filled bushing such as the one described above is placed in a position where the bushing is placed in a position where the fluid-filled bushing is placed, a good riding comfort cannot be obtained because no damping force is generated for one of the loads acting in two orthogonal directions. It turns out to be a problem. Therefore, in order to deal with such problems, it is necessary to reduce the load that acts in the axial direction of the inner cylinder part and the load that acts in the direction orthogonal to the axial direction of the inner cylinder part, etc., at the part where the suspension arm is attached to the vehicle body. Although it would be desirable to have a fluid-filled bushing capable of producing a damping force for each load, no fluid-filled bushings have been found for this purpose.
斯かる点に鑑み、本発明は、同軸的に配された外筒部と
内筒部との間に設けられた流体室を備え、内筒部の軸方
向に作用する荷重、及び、内筒部の軸方向に直交する方
向に作用する荷重の夫々に対し、減衰力を発生させるこ
とができるようにされた流体入りブツシュを提供するこ
とを目的とする。In view of these points, the present invention includes a fluid chamber provided between an outer cylinder part and an inner cylinder part coaxially arranged, and a load acting in the axial direction of the inner cylinder part and a fluid chamber provided between an outer cylinder part and an inner cylinder part arranged coaxially. An object of the present invention is to provide a fluid-filled bushing capable of generating a damping force for each load acting in a direction perpendicular to the axial direction of the bushing.
（問題点を解決するための手段）
上述の目的を達成すべく、本発明に係る流体入りブツシ
ュは、外筒部と、外筒部の内側に同軸的に配された内筒
部と、外筒部と内筒部との間に介在せしめられて、外筒
部と内筒部との間に両者の軸方向に並置された少なくと
も２個の流体室を形成する弾性体と、外筒部もしくは内
筒部に設けられ、２個の流体室を連通させる連通路と、
外筒部もしくは内筒部から２個の流体室の間に突出せし
められ、弾性体より大なる硬度を有するス）７バ部とを
備え、弾性体によって形成される２個の流体室は、その
一方の側壁部を形成する部分の厚みと他方の側壁部を形
成する部分の厚みとが異なるものとされて構成される。(Means for Solving the Problems) In order to achieve the above-mentioned object, a fluid-filled bushing according to the present invention includes an outer cylinder part, an inner cylinder part coaxially disposed inside the outer cylinder part, and an outer cylinder part. an elastic body interposed between the cylindrical portion and the inner cylindrical portion to form at least two fluid chambers arranged in parallel in the axial direction between the outer cylindrical portion and the inner cylindrical portion; or a communication passage provided in the inner cylinder portion and communicating the two fluid chambers;
The two fluid chambers formed by the elastic body are provided with a bar part that protrudes between the two fluid chambers from the outer cylinder part or the inner cylinder part and has a hardness greater than that of the elastic body. The thickness of the portion forming one side wall portion is different from the thickness of the portion forming the other side wall portion.
（作 用）
上述の如くの構成とされる本発明に係る流体入りブツシ
ュにおいては、内筒部の軸方向に荷重が作用する場合に
は、外筒部と内筒部との間に介在せしめられた弾性体に
より、内筒部の軸方向に並置されて形成された２個の流
体室の夫々の容積が、両者を仕切る弾性体の変位に劣っ
て変化せしめられ、２個の流体室内に封入された流体が
、連通路を通じて容積が小とされた流体室から容積が大
とされた流体室へ流入せしめられて、減衰力が発生する
ものとされる。また、内筒部の軸方向に直交する方向に
荷重が作用する場合には、弾性体によって形成された２
個の流体室における厚みが小とされた側壁部の変形量が
大とされて、２個の流体室の容積が変化せしめられ、２
個の流体室内に封入された流体が、連通路を通じて容積
が小とされた流体室から容積が大とされた流体室へ流入
せしめられて、減衰力が発生するものとされる。(Function) In the fluid-filled bushing according to the present invention configured as described above, when a load is applied in the axial direction of the inner cylinder part, the bushing is inserted between the outer cylinder part and the inner cylinder part. Due to the elastic body, the volume of each of the two fluid chambers formed side by side in the axial direction of the inner cylinder portion is changed less than the displacement of the elastic body that partitions the two fluid chambers. The sealed fluid is caused to flow from the fluid chamber with a small volume to the fluid chamber with a large volume through the communication path, thereby generating a damping force. In addition, when a load is applied in a direction perpendicular to the axial direction of the inner cylinder, the
The amount of deformation of the side wall portion with a small thickness in the two fluid chambers is increased, and the volume of the two fluid chambers is changed.
The fluid sealed in each fluid chamber is caused to flow from a fluid chamber with a small volume to a fluid chamber with a large volume through a communication path, thereby generating a damping force.
このようにされることにより、内筒部の軸方向に作用す
る荷重、及び、内筒部の軸方向に直交する方向に作用す
る荷重の夫々に対して、減衰力を発生させることができ
ることになる。By doing so, it is possible to generate a damping force for each of the load acting in the axial direction of the inner cylinder part and the load acting in a direction orthogonal to the axial direction of the inner cylinder part. Become.
（実施例）
以下、本発明の実施例について図面を参照して説明する
。(Example) Hereinafter, an example of the present invention will be described with reference to the drawings.
第１図は、本発明に係る流体入りブツシュの一例を示し
、第２図は第１図に示される例が、車両の右側フロント
サスペンション装置に適用された状態を示す。なお、車
両には、左側フロントサスペンション装置が右側フロン
トサスペンション装置と同様の構成をもって設けられて
いる。FIG. 1 shows an example of a fluid-filled bushing according to the present invention, and FIG. 2 shows the example shown in FIG. 1 applied to a right front suspension device of a vehicle. Note that the vehicle is provided with a left front suspension device having the same configuration as the right front suspension device.
第２図において、右前輪８の車体に対する独立懸架を行
う右側フロントサスペンション装置を支持するサスペン
ション支持部材２は、車幅方向に伸びる横支持部２ａ及
びその両端部から車体前後方向に伸びる一対の縦支持部
２ｂ（第１図においては一対の縦支持部２ｂのうちの右
方のもののみが示されている）を有している。サスペン
ション支持部材２は、その縦支持部２ｂの上面部が一点
鎖線で示される車体フレーム４に、複数のラバーマウン
ト６が介在せしめられて取り付けられている。また、サ
スペンション支持部材２における横支持部２ａ及び縦支
持部２ｂの夫々の所定位置には、サスペンション支持部
材２の補強を行うブラケット７の両端部が固定されてい
る。In FIG. 2, the suspension support member 2 that supports the right front suspension device that independently suspends the right front wheel 8 with respect to the vehicle body includes a lateral support portion 2a extending in the vehicle width direction and a pair of vertical support portions 2a extending in the longitudinal direction of the vehicle body from both ends of the lateral support portion 2a. It has a support portion 2b (only the right one of the pair of vertical support portions 2b is shown in FIG. 1). The suspension support member 2 has an upper surface portion of the vertical support portion 2b attached to the vehicle body frame 4, which is indicated by a dashed line, with a plurality of rubber mounts 6 interposed therebetween. Further, both ends of a bracket 7 for reinforcing the suspension support member 2 are fixed to predetermined positions of each of the horizontal support portion 2a and the vertical support portion 2b of the suspension support member 2.
右前輪８は、ナックル部材１０の車輪支持部ｌＯａに回
転可能に取り付けられ、ナックル部材１０は、サスペン
ションロアアーム１２の一端部に、ジヨイント部１４を
介して回動可能に支持されている。ナックル部材１０に
おけるナックルアーム１０ｂの先端部には、タイロッド
１６の一端部が軸着されており、タイロッド１６の他端
部は、ラックギアハウジング１８に収納されて車幅方向
に伸びる、ステアリングギア機構を構成するラックギア
２０の一端部に、ボールジヨイント２２を介して連結さ
れている。従って、図示されていないステアリングホイ
ールからの操舵力は、ラックギア２０及びタイロッド１
６を介してナックルアーム１０ｂに伝達され、ナックル
部材１０がジヨイント部１４を中心として回動せしめら
れる。それにより、右前輪８が転舵され、同時に図示さ
れていない左前輪も転舵される。The right front wheel 8 is rotatably attached to a wheel support portion lOa of a knuckle member 10, and the knuckle member 10 is rotatably supported at one end of a suspension lower arm 12 via a joint portion 14. One end of a tie rod 16 is pivotally attached to the tip of the knuckle arm 10b of the knuckle member 10, and the other end of the tie rod 16 has a steering gear mechanism that is housed in a rack gear housing 18 and extends in the vehicle width direction. It is connected to one end of the constituent rack gear 20 via a ball joint 22. Therefore, the steering force from the steering wheel (not shown) is applied to the rack gear 20 and the tie rod 1.
6 to the knuckle arm 10b, and the knuckle member 10 is rotated about the joint portion 14. As a result, the right front wheel 8 is steered, and at the same time, the left front wheel (not shown) is also steered.
サスペンションロアアーム１２の他端ｔＪ １２ ａは
、サスペンション支持部材２における縦支持部２ｂの下
面側に配されたブラケット２４に、ボルト２７を介して
取り付けられ、それにより、サスペンションロアアーム
１２が車体上下方向に揺動可能とされている。The other end tJ 12 a of the suspension lower arm 12 is attached via a bolt 27 to a bracket 24 arranged on the lower surface side of the vertical support portion 2b of the suspension support member 2, so that the suspension lower arm 12 is moved in the vertical direction of the vehicle body. It is said to be swingable.
また、サスペンションロアアーム１２の中間部には、ス
タビライザ２８の一端部が固定されており、スタビライ
ザ２日の他端部は、車幅方向に伸びて図示されていない
左側フロントサスペンシラン装置に連結されている。さ
らに、サスペンションロアアーム１２の中間部には、コ
ンプレッションロッド３０の一端部が固定されている。Further, one end of a stabilizer 28 is fixed to the middle part of the suspension lower arm 12, and the other end of the stabilizer 28 extends in the vehicle width direction and is connected to a left front suspension device (not shown). There is. Further, one end portion of a compression rod 30 is fixed to the intermediate portion of the suspension lower arm 12.
コンプレッションロッド３０の他端部３０ａは、本発明
の一例をなす流体入りブツシュ３６の内筒部３８に挿通
され、流体入りブツシュ３６の外筒部４０は、サスペン
ション支持部材２における縦支持部２ｂの下面側に、そ
こに配されたブラケット３２によって固定されており、
それにより、コンプレッションロッド３０が車体上下方
向に揺動可能とされている。なお、流体入りブツシュ３
６における内筒部３８の両端部には、車体前後方向にお
けるコンプレッションロッド３０の移動量を規制する係
止片４１が固定されている。The other end 30a of the compression rod 30 is inserted into an inner cylindrical portion 38 of a fluid-filled bushing 36, which is an example of the present invention, and an outer cylindrical portion 40 of the fluid-filled bushing 36 is inserted into the vertical support portion 2b of the suspension support member 2. It is fixed on the lower surface side by a bracket 32 arranged there,
This allows the compression rod 30 to swing in the vertical direction of the vehicle body. In addition, fluid-filled bushing 3
Locking pieces 41 are fixed to both ends of the inner cylindrical portion 38 at 6 for regulating the amount of movement of the compression rod 30 in the longitudinal direction of the vehicle body.
流体入りブツシュ３６は、第１図に拡大されて示される
如く、内筒部３８と外筒部４ｏとの間に介在せしめられ
たラバー等の弾性体４２によって形成され、内筒部３８
の軸方向に沿って並置された流体室４４ａ及び４４ｂ、
及び、流体室４５ａ及び４５ｂを有しており、これら流
体室４４ａ。As shown in an enlarged view in FIG. 1, the fluid-filled bushing 36 is formed of an elastic body 42 such as rubber, which is interposed between the inner cylinder part 38 and the outer cylinder part 4o.
fluid chambers 44a and 44b juxtaposed along the axial direction;
The fluid chamber 44a has fluid chambers 45a and 45b.
４４ｂ、４５ａ及び４５ｂ内には、オイル等が封入され
ている。流体室４４ａと流体室４５ａ、及び、流体室４
４ｂと流体室４５ｂとは、第１図における■−■線に沿
う断面を表す第３図に示される如く、内筒部３８を挾ん
で対向配置されている。Oil etc. are sealed in 44b, 45a and 45b. Fluid chamber 44a, fluid chamber 45a, and fluid chamber 4
4b and the fluid chamber 45b are arranged to face each other with the inner cylinder portion 38 in between, as shown in FIG.
流体室４４ａ及び４４ｂは、内筒部３８に形成された連
通路４６を通じて連通せしめられており、また、流体室
４５ａ及び４５ｂは、内筒部３８に形成された連通路４
７を通じて連通せしめられている。流体室４４ａと流体
室４４ｂとの間における弾性体４２の内部、及び、流体
室４５ａと流体室４５ｂとの間における弾性体４２の内
部には、夫゛々、内筒部３８からストッパ４８及び４９
が突出しており、ストッパ４８及び４９は、弾性体４２
に比して大なる硬度を有するものとされている。The fluid chambers 44a and 44b communicate with each other through a communication passage 46 formed in the inner cylinder part 38, and the fluid chambers 45a and 45b communicate with each other through a communication passage 46 formed in the inner cylinder part 38.
It is communicated through 7. The inside of the elastic body 42 between the fluid chamber 44a and the fluid chamber 44b and the inside of the elastic body 42 between the fluid chamber 45a and the fluid chamber 45b are provided with a stopper 48 and a stopper 48 from the inner cylinder part 38, respectively. 49
protrudes, and the stoppers 48 and 49 are connected to the elastic body 42.
It is said to have greater hardness than that of
そして、弾性体４２によって形成された流体室４４ａ及
び４４ｂ、及び、流体室４５ａ及び４５ｂの夫々におけ
る外筒部４０の両端部に位置する側壁部の厚みは、流体
室４４ｂ側に比して流体室４４ａ側において大とされて
おり、また、流体室４５ａ側に比して流体室４５ｂ側に
おいて大とされている。The thickness of the side wall portions located at both ends of the outer cylindrical portion 40 in each of the fluid chambers 44a and 44b and the fluid chambers 45a and 45b, which are formed by the elastic body 42, is greater than that on the fluid chamber 44b side. The chamber 44a side is larger, and the fluid chamber 45b side is larger than the fluid chamber 45a side.
上述の如くの構成とされた流体入りブツシュ３６におい
て、その内筒部３８に挿通せしめられたコンプレッショ
ンロッド３０の他端部３０ａに、例えば、第４図に矢印
Ｘで示される如くの車体後方側への荷重が作用する場合
には、外筒部４０に対して内筒部３８が矢印Ｘで示され
る方向に移動せしめられる。このとき、内筒部３８より
突出するストッパ４８及び４９が弾性体４２を伴って内
筒部３８とともに車体後方側に移動し、斯かるストッパ
４８及び４９の移動によって、流体室４４ｂ及び４５ｂ
が圧縮されて、流体室４４ａ及び４５ａの容積が流体室
４４ｂ及び４５ｂの容積に比して大とされる。それによ
り、流体室４４ｂ及び４５ｂ内の流体が、第４図におい
て白抜矢印で示される如く、夫々、連通路４６及び４７
を通じて流体室４４ａ及び４５ａ内に流入せしめられて
、内筒部３８の軸方向に作用する荷重に対する減衰力が
発生する。In the fluid-filled bushing 36 configured as described above, the other end 30a of the compression rod 30 inserted into the inner cylindrical portion 38 is attached to the rear side of the vehicle body as shown by the arrow X in FIG. When a load is applied to the inner cylinder part 38, the inner cylinder part 38 is moved in the direction indicated by the arrow X with respect to the outer cylinder part 40. At this time, the stoppers 48 and 49 protruding from the inner cylinder part 38 move toward the rear of the vehicle body together with the inner cylinder part 38 accompanied by the elastic body 42, and the movement of the stoppers 48 and 49 closes the fluid chambers 44b and 45b.
is compressed, and the volumes of the fluid chambers 44a and 45a are made larger than the volumes of the fluid chambers 44b and 45b. As a result, the fluid in the fluid chambers 44b and 45b flows through the communication passages 46 and 47, respectively, as shown by the white arrows in FIG.
The fluid flows into the fluid chambers 44a and 45a through the fluid chambers 44a and 45a, thereby generating a damping force against the load acting in the axial direction of the inner cylinder portion 38.
また、コンプレッションロッド３０の他端部３０ａに、
例えば、第４図に矢印Ｘで示される方向とは逆に、車体
前方側への荷重が作用する場合には、外筒部４０に対し
て内筒部３８が矢印Ｘで示される方向とは逆方向に変位
せしめられる。斯かる状態においては、ストッパ４８及
び４９が弾性体４２を伴って内筒部３８とともに車体前
方側に移動し、斯かるストッパ部４８及び４９の移動に
よって流体室４４ａ及び４５ａが圧縮されて、流体室４
４ｂ及び４５ｂの容積が流体室４４ａ及び４５ａの容積
に比して大とされる。それにより、流体室４４ａ及び４
５ａ内の流体が、第４図において白抜矢印で示される方
向とは逆に、夫々、連通！４６及び４７を通じて流体室
４４ｂ及び４５ｂ内に流入せしめられて、内筒部３８の
軸方向に作用する荷重に対する減衰力が発生する。Moreover, at the other end 30a of the compression rod 30,
For example, when a load is applied to the front side of the vehicle body in the opposite direction to the direction indicated by arrow X in FIG. It is displaced in the opposite direction. In such a state, the stoppers 48 and 49 move toward the front side of the vehicle body together with the inner cylindrical portion 38 accompanied by the elastic body 42, and the movement of the stoppers 48 and 49 compresses the fluid chambers 44a and 45a, causing the fluid to flow out. room 4
The volumes of fluid chambers 4b and 45b are larger than those of fluid chambers 44a and 45a. Thereby, the fluid chambers 44a and 4
The fluids in 5a communicate in the opposite direction to the direction indicated by the white arrow in FIG. 4! The fluid flows into the fluid chambers 44b and 45b through 46 and 47, and a damping force against the load acting in the axial direction of the inner cylinder portion 38 is generated.
なお、コンプレッションロッド３０の他端部３０ａに、
内筒部３８の軸方向に過大な荷重が作用する場合には、
内筒部３８の両端部に固定された係止片４１が、外筒部
４０の端面部に当接せしめられることにより、流体入り
ブツシュ３６の破損が防止される。In addition, at the other end 30a of the compression rod 30,
If an excessive load is applied in the axial direction of the inner cylinder part 38,
The locking pieces 41 fixed to both ends of the inner cylindrical portion 38 are brought into contact with the end surfaces of the outer cylindrical portion 40, thereby preventing the fluid-filled bushing 36 from being damaged.
一方、コンプレッションロッド３０の他端部３０ａに、
例えば、第５図に矢印Ｙで示される如くの、車幅方向に
沿う荷重が作用する場合には、外筒部４０に対して内筒
部３８が矢印Ｙで示される方向に移動せしめられる。斯
かる状態においては、流体室４５ａ及び４５ｂが圧縮さ
れて、流体室４５ａにおける厚みが小とされた側壁部が
流体室４５ｂにおける厚みが大とされた側壁部に比して
大きく外方に変形し、それにより、流体室４５ａの容積
が流体室４５ｂの容積に比して大とされる。On the other hand, at the other end 30a of the compression rod 30,
For example, when a load along the vehicle width direction as shown by arrow Y in FIG. 5 is applied, the inner cylinder part 38 is moved in the direction shown by arrow Y with respect to the outer cylinder part 40. In such a state, the fluid chambers 45a and 45b are compressed, and the thinner side wall portion of the fluid chamber 45a deforms outward to a greater extent than the thicker side wall portion of the fluid chamber 45b. However, as a result, the volume of the fluid chamber 45a is made larger than the volume of the fluid chamber 45b.
また、流体室４４ａ及び４４ｂが伸長して流体室４４ｂ
における厚みが少とされた側壁部が流体室４４ａにおけ
る厚みが大とされた側壁部に比して大きく内方に変形し
、それにより、流体室４４ａの容積が流体室４４ｂの容
積に比して大とされる。Further, the fluid chambers 44a and 44b are expanded, and the fluid chamber 44b
The thinner side wall portion of the fluid chamber 44a deforms inward to a greater extent than the thicker side wall portion of the fluid chamber 44a, so that the volume of the fluid chamber 44a becomes smaller than the volume of the fluid chamber 44b. It is said to be large.
このため、流体室４５ｂ及び４４ｂ内の流体が、第５図
において白抜き矢印で示される如く、連通路４６及び４
７を通じて、夫々流体室４５ａ及び４４ａ内に流入せし
められて、内筒部３８の軸方向に直交する方向に作用す
る荷重に対する減衰力が発生する。Therefore, the fluid in the fluid chambers 45b and 44b flows through the communication paths 46 and 44, as shown by the white arrows in FIG.
7 into the fluid chambers 45a and 44a, respectively, to generate a damping force against a load acting in a direction perpendicular to the axial direction of the inner cylinder portion 38.
また、コンプレッションロッド３０の他端部３０ａに、
例えば、第５図に矢印Ｙで示される方向とは逆の、車幅
方向に沿う荷重が作用する場合には、外筒部４０に対し
て内筒部３８が矢印Ｙで示される方向とは逆方向に移動
せしめられる。斯かる状態においては、流体室４５ａ及
び４５ｂが伸長して流体室４５ａにおける厚みが小とさ
れた側壁部が流体室４５ｂにおける厚みが大とされた側
壁部に比して大きく内方に変形し、それにより、流体室
４５ｂの容積が流体室４５ａの容積に比して大とされる
。また、流体室４４ａ及び４４ｂが圧縮されて流体室４
４ｂにおける厚みが少とされた側壁部が流体室４４ａの
厚みが大とされた側壁部に比して大きく外方に変形して
、それにより、流体室４４ｂの容積が流体室４４ａの容
積に比して大とされる。このため、流体室４５ａ及び４
４ａ内の流体が、第５図において白抜き矢印で示される
方向とは逆に、連通路４６及び４７を通じて、夫々流体
室４５ｂ及び４４ｂ内に流入せしめられて、内筒部３８
の軸方向に、直交する方向に作用する荷重に対する減衰
力が発生する。Moreover, at the other end 30a of the compression rod 30,
For example, when a load is applied along the vehicle width direction, which is opposite to the direction shown by arrow Y in FIG. forced to move in the opposite direction. In such a state, the fluid chambers 45a and 45b are expanded, and the thinner side wall of the fluid chamber 45a deforms inward to a greater extent than the thicker side wall of the fluid chamber 45b. Therefore, the volume of the fluid chamber 45b is made larger than the volume of the fluid chamber 45a. Further, the fluid chambers 44a and 44b are compressed, and the fluid chamber 4
The thinner side wall portion of the fluid chamber 4b deforms outward to a greater extent than the thicker side wall portion of the fluid chamber 44a, so that the volume of the fluid chamber 44b becomes equal to the volume of the fluid chamber 44a. It is said to be large in comparison. For this reason, the fluid chambers 45a and 4
The fluid in 4a is caused to flow into fluid chambers 45b and 44b through communication passages 46 and 47, respectively, in the opposite direction to the direction indicated by the white arrow in FIG.
A damping force is generated against a load acting in a direction perpendicular to the axial direction.
なお、コンプレッションロッド３０の他端部３０ａに、
内筒部３８の軸方向に直交する方向に過大な荷重が作用
する場合には、外筒部４０に対する内筒部３８の変位量
が内筒部３８より突出するストッパ４８及び４９によっ
て規制されるので、流体入りブツシュ３６の破損が防止
される。In addition, at the other end 30a of the compression rod 30,
When an excessive load is applied in a direction perpendicular to the axial direction of the inner cylinder part 38, the amount of displacement of the inner cylinder part 38 with respect to the outer cylinder part 40 is regulated by stoppers 48 and 49 that protrude from the inner cylinder part 38. Therefore, damage to the fluid-filled bushing 36 is prevented.
このように、コンブレッションロ゛ソド３０の他端部３
０ａに嵌合せしめられ、サスペンション支持部材２にお
ける縦支持部２ｂの下面側に取り付けられたプラケツト
３２に固定された外筒部４０を有する流体入りブツシュ
３６が、その内筒部３８の軸方向に作用する荷重、及び
、内筒部３８の軸方向に直交する方向に作用する荷重の
夫々に対して減衰力を発生させるものとされているので
、斯かる流体入りブツシュ３６が配されたフロントサス
ペンション装置を備えた車両においては、その走行時に
おける車体前後方向及び車幅方向における振動が効果的
に吸収され、乗心地が著しく向上せしめられることにな
る。In this way, the other end 3 of the compression rod 30
A fluid-filled bushing 36 having an outer cylindrical portion 40 that is fitted into the inner cylindrical portion 0a and fixed to a bracket 32 attached to the lower surface side of the vertical support portion 2b of the suspension support member 2 extends in the axial direction of the inner cylindrical portion 38. Since a damping force is generated for each of the applied load and the load applied in a direction perpendicular to the axial direction of the inner cylinder portion 38, the front suspension equipped with such a fluid-filled bushing 36 In a vehicle equipped with the device, vibrations in the longitudinal and longitudinal directions of the vehicle body and in the vehicle width direction when the vehicle is running are effectively absorbed, and ride comfort is significantly improved.
なお、上述の例においては、ストッパ４８及び４９が夫
々内筒部３８より突出するものとされているが、例えば
、ストッパ４８及び４９は、外筒部４０より突出するも
のとされてもよい。In the above example, the stoppers 48 and 49 each protrude from the inner cylinder part 38, but for example, the stoppers 48 and 49 may protrude from the outer cylinder part 40.
（発明の効果）
以上の説明から明らかな如く、本発明に係る流体入りブ
ツシュによれば、内筒部の軸方向に荷重が作用する場合
には、内筒部の軸方向に沿って並置された２個、の流体
室の容積が弾性体の変形によって変化せしめられるので
、容積が小とされた流体室から容積が大とされた流体室
への流体の流入に基づいて減衰力を発生させることがで
き（また、内筒部の軸方向に直交する方向に荷重が作用
する場合には、弾性体によって形成された２個の流体室
のうちの一方における、厚みが小とされる側壁部の変形
量が大とされて、２個の流体室の容積が変化せしめられ
るので、容積が小とされた流体室から容積が大とされた
流体室への流体の流入に基づいて減衰力を発生させるこ
とができる。(Effects of the Invention) As is clear from the above description, according to the fluid-filled bushing of the present invention, when a load is applied in the axial direction of the inner cylinder, the inner cylinder is juxtaposed along the axial direction. Since the volumes of the two fluid chambers are changed by the deformation of the elastic body, a damping force is generated based on the flow of fluid from the fluid chamber with a smaller volume to the fluid chamber with a larger volume. (Also, when a load is applied in a direction perpendicular to the axial direction of the inner cylinder, the thinner side wall of one of the two fluid chambers formed by the elastic body Since the amount of deformation is large and the volumes of the two fluid chambers are changed, the damping force is generated based on the inflow of fluid from the fluid chamber with a small volume to the fluid chamber with a large volume. can be generated.
従って、例えば、斯かる流体入りブツシュが車両のサス
ペンション装置におけるサスペンションアームが車体に
取り付けられる部分等に配される場合には、サスペンシ
ョンアームに作用する車体前後方向及び車幅方向に沿う
荷重の夫々に対する減衰力が得られ、乗心地の著しい向
上が図られることになる。Therefore, for example, when such a fluid-filled bushing is placed in a part of a vehicle suspension system where a suspension arm is attached to the vehicle body, it is difficult to handle the loads acting on the suspension arm in the vehicle longitudinal direction and the vehicle width direction. A damping force is obtained, and riding comfort is significantly improved.
【図面の簡単な説明】
第・１図は本発明に係る流体入りブツシュの一例を示す
拡大断面図、第２図は第１図に示される例を、それが適
用された車両の右側フロントサスペンション装置ととも
に示す図、第３図は第１図におけるｍ−ｍ線に沿う断面
図、第４図及び第５図は第１図に示される例の動作説明
に供される図である。
図中、３６は流体入りブツシュ、３８は内筒部、４０は
外筒部、４２は弾性体、４４ａ、４４ｂ。
４５ａ及び４５ｂは流体室、４６及び４７は連通路、４
８及び４９はストッパである。[Brief Description of the Drawings] Fig. 1 is an enlarged sectional view showing an example of a fluid-filled bushing according to the present invention, and Fig. 2 is an enlarged sectional view showing an example of a fluid-filled bushing according to the present invention. FIG. 3 is a sectional view taken along line mm in FIG. 1, and FIGS. 4 and 5 are diagrams for explaining the operation of the example shown in FIG. 1. In the figure, 36 is a fluid-filled bushing, 38 is an inner cylindrical portion, 40 is an outer cylindrical portion, 42 is an elastic body, and 44a, 44b. 45a and 45b are fluid chambers, 46 and 47 are communicating passages, 4
8 and 49 are stoppers.
Claims (1)
、上記外筒部と内筒部との間に介在せしめられて、上記
外筒部と内筒部との間に両者の軸方向に並置された少な
くとも２個の流体室を形成し、該２個の流体室の一方の
側壁部を形成する部分の厚みと他方の側壁部を形成する
部分の厚みとが異なるものとされた弾性体と、上記外筒
部もしくは上記内筒部に設けられ、上記２個の流体室を
連通させる連通路と、上記外筒部もしくは上記内筒部か
ら上記２個の流体室の間に突出せしめられ、上記弾性体
より大なる硬度を有するストッパ部と、を備えて構成さ
れた流体入りブッシュ。an outer cylindrical portion, an inner cylindrical portion coaxially disposed inside the outer cylindrical portion, and an inner cylindrical portion interposed between the outer cylindrical portion and the inner cylindrical portion; At least two fluid chambers arranged in parallel in the axial direction of the two fluid chambers are formed between the two fluid chambers, and the thickness of the portion forming one side wall portion of the two fluid chambers is equal to the thickness of the portion forming the other side wall portion. different elastic bodies, a communication passage provided in the outer cylinder part or the inner cylinder part to communicate the two fluid chambers, and a communication passage for communicating the two fluid chambers from the outer cylinder part or the inner cylinder part. A fluid-filled bush comprising: a stopper portion that protrudes between the chambers and has a harder hardness than the elastic body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10048287A JPS63266240A (en) | 1987-04-23 | 1987-04-23 | Fluid-filled bush |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10048287A JPS63266240A (en) | 1987-04-23 | 1987-04-23 | Fluid-filled bush |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63266240A true JPS63266240A (en) | 1988-11-02 |
Family
ID=14275142
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10048287A Pending JPS63266240A (en) | 1987-04-23 | 1987-04-23 | Fluid-filled bush |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63266240A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5172893A (en) * | 1990-03-16 | 1992-12-22 | Hutchison | Hydraulic antivibratory sleeves |
| US5178376A (en) * | 1989-10-05 | 1993-01-12 | Firma Carl Freudenberg | Hydraulically damped rubber cartridge spring |
| US5322266A (en) * | 1992-02-20 | 1994-06-21 | Firma Carl Freudenberg | Hydraulic damper elastomeric body having alternating rigid and deformable wall sections |
| GB2360344A (en) * | 1999-06-14 | 2001-09-19 | Avon Vibration Man Syst Ltd | Mounting device for hydraulically damping both axial and radial vibrations |
| WO2004042250A1 (en) * | 2002-11-07 | 2004-05-21 | Trelleborg Automotive Technical Centre Gmbh | Hydraulically-damped mounting, in particular for supporting the engine in a motor vehicle |
| EP3636954A4 (en) * | 2017-06-09 | 2021-03-03 | Bridgestone Corporation | Anti-vibration device |
| US20220290733A1 (en) * | 2021-03-09 | 2022-09-15 | Hyundai Motor Company | Hydraulic mount for vehicle |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60139942A (en) * | 1983-12-27 | 1985-07-24 | Nissan Motor Co Ltd | Tubular bush |
| JPS60159436A (en) * | 1984-01-30 | 1985-08-20 | Tokai Rubber Ind Ltd | Fluid enclosed suspension bush |
| JPS60179540A (en) * | 1984-02-23 | 1985-09-13 | Nissan Motor Co Ltd | Liquid charged damper device |
-
1987
- 1987-04-23 JP JP10048287A patent/JPS63266240A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60139942A (en) * | 1983-12-27 | 1985-07-24 | Nissan Motor Co Ltd | Tubular bush |
| JPS60159436A (en) * | 1984-01-30 | 1985-08-20 | Tokai Rubber Ind Ltd | Fluid enclosed suspension bush |
| JPS60179540A (en) * | 1984-02-23 | 1985-09-13 | Nissan Motor Co Ltd | Liquid charged damper device |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5178376A (en) * | 1989-10-05 | 1993-01-12 | Firma Carl Freudenberg | Hydraulically damped rubber cartridge spring |
| US5172893A (en) * | 1990-03-16 | 1992-12-22 | Hutchison | Hydraulic antivibratory sleeves |
| US5322266A (en) * | 1992-02-20 | 1994-06-21 | Firma Carl Freudenberg | Hydraulic damper elastomeric body having alternating rigid and deformable wall sections |
| GB2360345B (en) * | 1999-06-14 | 2002-02-27 | Avon Vibration Man Syst Ltd | Hydraulically damped mounting device |
| GB2360345A (en) * | 1999-06-14 | 2001-09-19 | Avon Vibration Man Syst Ltd | Mounting device for hydraulically damping both axial and radial vibrations |
| GB2360344B (en) * | 1999-06-14 | 2002-02-27 | Avon Vibration Man Syst Ltd | Hydraulically damped mounting device |
| GB2360344A (en) * | 1999-06-14 | 2001-09-19 | Avon Vibration Man Syst Ltd | Mounting device for hydraulically damping both axial and radial vibrations |
| WO2004042250A1 (en) * | 2002-11-07 | 2004-05-21 | Trelleborg Automotive Technical Centre Gmbh | Hydraulically-damped mounting, in particular for supporting the engine in a motor vehicle |
| US7207552B2 (en) | 2002-11-07 | 2007-04-24 | Trelleborg Automotive Technical Centre Gmbh | Hydraulic damping mount, particularly for mounting an automotive engine |
| CN100387862C (en) * | 2002-11-07 | 2008-05-14 | 特雷里博格汽车技术中心有限责任公司 | Hydraulic damping mount, particularly for mounting an automotive engine |
| 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 |
| US20220290733A1 (en) * | 2021-03-09 | 2022-09-15 | Hyundai Motor Company | Hydraulic mount for vehicle |
| US11906012B2 (en) * | 2021-03-09 | 2024-02-20 | Hyundai Motor Company | Hydraulic mount for vehicle |
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