JPS60166509A - Upper support for car suspension - Google Patents

Upper support for car suspension

Info

Publication number
JPS60166509A
JPS60166509A JP2410584A JP2410584A JPS60166509A JP S60166509 A JPS60166509 A JP S60166509A JP 2410584 A JP2410584 A JP 2410584A JP 2410584 A JP2410584 A JP 2410584A JP S60166509 A JPS60166509 A JP S60166509A
Authority
JP
Japan
Prior art keywords
metal fitting
chamber
inner metal
pressure receiving
receiving chamber
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
JP2410584A
Other languages
Japanese (ja)
Other versions
JPH0434016B2 (en
Inventor
Yasuo Kokuni
小国　康夫
Shigeyuki Funabashi
船橋　茂幸
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
Toyota Motor Corp
Original Assignee
Sumitomo Riko Co Ltd
Toyota Motor Corp
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, Toyota Motor Corp filed Critical Sumitomo Riko Co Ltd
Priority to JP2410584A priority Critical patent/JPS60166509A/en
Publication of JPS60166509A publication Critical patent/JPS60166509A/en
Publication of JPH0434016B2 publication Critical patent/JPH0434016B2/ja
Granted legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
    • F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
    • F16F13/24—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 central part of the unit being supported by one element and both extremities of the unit being supported by a single other element, i.e. double acting mounting
    • 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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/54—Arrangements for attachment

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

PURPOSE:To improve the cutting-off force for the vibration in high frequency and small displacement and the damping force for the vibration in low frequency and large displacement by sealing a pressure receiving chamber whose capacity is reduced by the relative displacement of the inside and outside metal fittings and an equillibrium chamber constituted of flexible thin films, with incompressible fluid and allowing the both chambers to communicate each other through an orifice. CONSTITUTION:The vibration in high frequency and small displacement is cut-off by the elastic deformation in the direction of shear or rubber elastomers 30 and 52. While, for the vibration in low frequency and large displacement, the relative displacement in the axial direction between a piston rod 22 and the outside and inside metal fittings 26 and 28 becomes large, and when the both come close to each other, a pressure receiving chamber 58 contracts, and the liquid in the pressure receiving chamber 58 flows into the side of an equillibrium chamber 68 through an orifice 72, expanding a diaphragm rubber 62. Therefore, a damping force is generated for the vibration in large displacement. When the both metal fittings 26 and 28 are separated, liquid flows reversely, and a damping force is generated similarly. With such constitution, the cutting-off force for the vibration in high frequency and small displacement and the damping force for the vibration in low frequency and large displacement can be improved.

Description

【発明の詳細な説明】 技術分野 本発明は、車両懸架装置において、緩衝器のピストンロ
ソ］“を車体に対して弾性的に連結するためのアッパサ
ポートに係り、特に小変位の振動を有効にｘａ　ｌ析す
ることができるとともに、大変位の振動を効果的に減衰
することか可能なアッパサポートに関するものである。Detailed Description of the Invention Technical Field The present invention relates to an upper support for elastically connecting a shock absorber piston rotor to a vehicle body in a vehicle suspension system, and particularly relates to an upper support for elastically connecting a shock absorber piston rotor to a vehicle body. The present invention relates to an upper support that can be analyzed and effectively damp vibrations caused by large displacements.

従来技術 車両懸架装置の一種に、緩衝器（シヨ・ノクアフソーハ
）を懸架リンクに利用したストラットタイプおいては、
緩ｉｈ器の一端部か車輪側に連結される一方、緩衝器の
ビスＩ・ンロソトがアッパサポートを介して車体側に弾
性的に連結されるのが普通であって、例えば緩ｉｈ器の
外側にコイルスプリングか配置されて、車両前輪用の懸
架装置としてよく用いられている、いわゆるマンクファ
ーソンストラソトタイプのものを、その代表例として挙
げることができる。A type of prior art vehicle suspension system is a strut type that uses a shock absorber as a suspension link.
While one end of the induction heater is connected to the wheel side, the screws of the shock absorber are usually elastically connected to the vehicle body via an upper support, for example, the outside of the induction heater. A typical example is the so-called Munkferson Strasotho type suspension system, which is often used as a suspension system for the front wheels of a vehicle and has a coil spring disposed in the front wheel.

そして、上記アッパサポートは、車輪側に取り付けられ
る外側金具と、緩衝器のピストンロンドが取り付けられ
る内側金具と、それら外側金具と内１１ｔ，＋ｌ金具と
の間に介在せしめられたゴム弾性体とを含んで構成され
るのが普通であり、緩衝器およびコイルスプリングでは
吸収しきれない車輪側からの振動や、コイルスプリング
の自動振動等が車体側に伝達されることを抑制する役割
を果たす。The upper support has an outer metal fitting attached to the wheel side, an inner metal fitting to which the shock absorber piston rond is attached, and a rubber elastic body interposed between these outer metal fittings and the inner 11t, +l metal fittings. It plays a role in suppressing vibrations from the wheel side that cannot be absorbed by the shock absorber and coil springs, automatic vibrations of the coil springs, etc. from being transmitted to the vehicle body.

ところで、このようなアッパサポートにおいては、小変
位で高周波の振動入力に対しては、柔らかいばね特性（
低い動ばね定数）を保ちつつ、そのような振動を有効に
遮断する遮断特性と、大変位で低周波の振動入力に対し
ては、それを速やかに減衰して上記外側金具と内側金具
との大きな変位を抑制する減衰特性とが要求されるので
あるか、従来のアソパサポ−１・では、ゴム弾性体の防
振作用のみによってそのような二つの防振特性を果たさ
せようとするものであったため、自ずと限界が生じ、要
求される二つの特性を共に満足することが困難であった
。By the way, in such an upper support, soft spring characteristics (
It has an isolation characteristic that effectively isolates such vibrations while maintaining a low dynamic spring constant (dynamic spring constant), and a structure that quickly damps large displacement and low-frequency vibration inputs and protects the outer and inner fittings from each other. Perhaps because damping characteristics that suppress large displacements are required, the conventional ASOPAS support 1 attempts to achieve these two vibration damping characteristics only by the vibration damping action of the rubber elastic body. As a result, limitations naturally arose, and it was difficult to satisfy both of the required characteristics.

発明の目的 ここにおいて、本発明は、そのような事情に鑑がみてな
されたものであり、その目的とするところは、小変位で
高周波の振動に対する高い遮断能力を発１ルしつつ、大
変位で低周波の振動にり」する大きな減衰力を得ること
かできるアソパザボ−１・を提供することにある。Purpose of the Invention The present invention has been made in view of the above circumstances, and its purpose is to provide high isolation capability against high-frequency vibrations with small displacements, while also achieving large displacements. An object of the present invention is to provide an asopaza board 1 which can obtain a large damping force against low-frequency vibrations.

発明の構成 そのような目的を達成するために、本発明にあっては、
前述のような外側金具，内側金具，ゴム弾性体を含むア
ッパサポートにおいて、該内側金具と該外側金具との間
に画成されて、それら内側金具と外側金具との相対的な
変位によって容積が縮小せしめられ得る受圧室を設ける
と共に、前記内側金具を挟んで該受圧室とは反対側に、
少なくとも一部が可撓性薄膜からなる囲いにて平衡室を
形成し、それら受圧室と平衡室とをオリフィスを介して
連ｊｍせしめる一方、かかる受圧室及び平衡室内に所定
の非圧縮性流体をそれぞれ封入したのである。Structure of the Invention In order to achieve such an object, the present invention includes the following:
In the upper support including the outer metal fitting, the inner metal fitting, and the rubber elastic body as described above, the space is defined between the inner metal fitting and the outer metal fitting, and the volume is increased by the relative displacement between the inner metal fitting and the outer metal fitting. A pressure receiving chamber that can be reduced is provided, and on the opposite side of the pressure receiving chamber with the inner metal fitting in between,
An equilibrium chamber is formed by an enclosure at least partially made of a flexible thin film, and the pressure receiving chamber and the equilibrium chamber are connected through an orifice, while a predetermined incompressible fluid is supplied into the pressure receiving chamber and the equilibrium chamber. Each was enclosed.

発明の効果 このようにすれば、小変位で高周波の振動入力時には、
主にゴム弾性体の弾性変形作用による柔らかいばね特性
、言い換えれば低い動ばね定数が得られて、そのような
振動が車体側に伝達されることを有効に遮断することが
できる。一方、大変位で低周波の振動入力時には、内側
金具と外側金具との相対変位が大きくなることによって
、受圧室の容積が縮小せしめられ、それに伴い受圧室内
の非圧縮性流体かオリフィスを介して平衡室内に流入し
、その非圧縮性流体かオリフィスを流通する際に牛しる
粘性抵抗によって、そのような大変位で低周波の振動が
速やかに減衰せし７められ、−一つのアソパザボー１〜
でありながら、振動遮断能力および振動減衰能力のいず
れにも優れた防振特性を発揮する複合的なアソパザボ−
１を提供することが可能となったのである。Effects of the invention By doing this, when high frequency vibration is input with small displacement,
A soft spring characteristic, in other words a low dynamic spring constant, is obtained mainly due to the elastic deformation of the rubber elastic body, and transmission of such vibrations to the vehicle body can be effectively blocked. On the other hand, when a large displacement and low frequency vibration is input, the volume of the pressure receiving chamber is reduced due to the large relative displacement between the inner and outer fittings, and as a result, the incompressible fluid in the pressure receiving chamber is Due to the viscous resistance of the incompressible fluid flowing into the equilibrium chamber and flowing through the orifice, low frequency vibrations with such large displacements are rapidly damped. ~
However, it is a composite atopaza board that exhibits excellent vibration isolation properties in both vibration isolation and vibration damping capabilities.
It became possible to provide 1.

実施例 以１″、本発明の一１二の実施例を図面に基づいて詳細
に説明する。Embodiments 1'' From now on, 112 embodiments of the present invention will be described in detail with reference to the drawings.

なお、この実施例は車両前輪用の、いわゆるマソクファ
ーソンストラノトタイプの懸架装置におけるアソパサボ
−１・に本発明を適用した場合の一例である。This embodiment is an example in which the present invention is applied to an Asopasabo-1 in a so-called Masochfersonstranoto type suspension system for the front wheels of a vehicle.

第１図には、−１−記タイブの懸架装置が簡略に示され
ている。かかる図において、１０は緩衝器であり、この
緩衝器１０の外周にはコイルスプリング１２が配設され
ている。そして、緩衝器１０のシリンダ１４の下端部が
、車輪１６を回転可能に支持するステアリングナックル
に連結されるとともに、アーム機構１８を介して車体２
０に支承されている。一方、緩衝器１０のピストンロッ
ド２２の上端部か、アッパサポート（いわゆるストラソ
トマウン１−）２４を介して車体２０に弾性的に連結さ
れているのである。In FIG. 1, a suspension system of type -1- is simply shown. In this figure, 10 is a shock absorber, and a coil spring 12 is arranged around the outer periphery of this shock absorber 10. The lower end of the cylinder 14 of the shock absorber 10 is connected to a steering knuckle that rotatably supports the wheel 16, and is connected to the vehicle body via an arm mechanism 18.
Supported by 0. On the other hand, the upper end of the piston rod 22 of the shock absorber 10 is elastically connected to the vehicle body 20 via an upper support (so-called stratomount 1-) 24.

このアッパサポート２４の拡大断面図が第２図に示され
ている。An enlarged sectional view of this upper support 24 is shown in FIG.

この図から明らかなように、かかるアッパサポート２４
は、円環状の外側金具２６と、その内側に同心的に配置
された円環状の内側金具２８と、これら外側金具２６と
内側金具２８との間に介在させられたゴム弾性体３０と
を備えており、このゴム弾性体３０の内周側に内側金具
２８が、また外周側に外側金具２６がそれぞれ公知の加
硫接着により固着されている。外側金具２６は円筒状部
３２を備え、この円筒状部３２の前記緩（Ｆ器１０側の
端部が半径方向外向きに円環状に延出せしめられて、フ
ランジ部３４が一体に形成されており、このフランジ部
３４に立設された複数のホルト３６において前記車体２
０に取り付けられる。一方、内側金具２８は中心部に円
筒状部３８を備え、その中間部に円環皿状の部材が嵌合
、固定されることによって、前記緩衝器ｌＯ側において
半径方向外向きに延びる円環状のフランジ部４０が一体
的に形成されている。また、円筒状部３８の内側には、
ベアリング４２がカシメ付けられており、このヘアリン
グ４２を介して前記ｆｆｌ衝器１０のピストンロッド２
２の上端部が、ナ７１４４によって内側金具２８と相対
回転可能な状態で取り付けられる。As is clear from this figure, the upper support 24
comprises an annular outer fitting 26, an annular inner fitting 28 disposed concentrically inside the annular outer fitting 26, and a rubber elastic body 30 interposed between the outer fitting 26 and the inner fitting 28. An inner metal fitting 28 and an outer metal fitting 26 are fixed to the inner circumferential side and the outer circumferential side of the rubber elastic body 30, respectively, by known vulcanization adhesive. The outer metal fitting 26 includes a cylindrical portion 32, and the end portion of the cylindrical portion 32 on the loose (F) side 10 extends outward in the radial direction in an annular shape, and a flange portion 34 is integrally formed. The vehicle body 2 is connected to a plurality of bolts 36 erected on this flange portion 34.
Attached to 0. On the other hand, the inner metal fitting 28 has a cylindrical part 38 in the center, and a circular plate-shaped member is fitted and fixed in the middle part of the cylindrical part 38, so that a circular plate-like member is fitted and fixed to the central part, so that a circular plate-shaped member extends radially outward on the buffer lO side. A flange portion 40 is integrally formed. Moreover, inside the cylindrical part 38,
A bearing 42 is caulked, and the piston rod 2 of the ffl shocker 10 is inserted through this hair ring 42.
2 is attached to the inner metal fitting 28 by a nut 7144 so as to be rotatable relative to the inner metal fitting 28.

外側金具２６のフランジ部３４と内側金具２８のフラン
ジ部４０とは、ピストンロッド２２の軸方向において、
フランジ部３４の内周側にフランジ部４０の外周側が所
定距離隔てて対向させられており、またそれらフランジ
部３４．４０の外周縁部には、いずれも前記緩衝器１０
側に円筒状に延出せしめられた円筒縁部４６，４８がそ
れぞれ同心的に設けられている。そして、前記ゴム弾性
体３０の外周部には、それらフランジ部３４．４０の間
に位置して、前記緩衝器１０側に開口する円環状の凹所
５０が形成されている。この凹所５０は両フランジ部３
４．４０の双方の円筒縁部４６．４８において開口させ
られており、この凹所５０の開口部が、円環状の比較的
薄いゴム弾性体５０によって閉塞されることにより、受
圧室５８が形成されている。The flange portion 34 of the outer metal fitting 26 and the flange portion 40 of the inner metal fitting 28 are arranged in the axial direction of the piston rod 22.
The outer circumferential side of the flange portion 40 is opposed to the inner circumferential side of the flange portion 34 at a predetermined distance, and the shock absorber 10 is located on the outer circumferential edge of the flange portions 34 and 40.
Concentric cylindrical edges 46, 48 are provided which extend cylindrically to the sides. An annular recess 50 is formed in the outer peripheral portion of the rubber elastic body 30, located between the flange portions 34 and 40, and opening toward the shock absorber 10 side. This recess 50 is located at both flange portions 3.
4.40 are opened at both cylindrical edges 46.48, and the opening of this recess 50 is closed by a relatively thin annular rubber elastic body 50, thereby forming a pressure receiving chamber 58. has been done.

このゴム弾性体５２ば、Ｌ字型の横断面形状を有し、そ
の上端外周部に円環状の固着リング５４が、また下端内
周部に同じく円環状の固着リング５６が、それぞれ同心
的に公知の加硫接着により固着されている。そして外側
の固着リング５４が円筒縁部４６の内周面に、また内側
の固着リング５６が円筒縁部４８の外周面にそれぞれ圧
入され０ ることにより、前記凹所５０が液密に閉塞されて受圧室
５８が形成されているのであり、それら両リング５４．
５６およびゴム弾性体５２が閉塞部材を構成しζいるの
である。This rubber elastic body 52 has an L-shaped cross-sectional shape, and has an annular fixing ring 54 on the outer periphery of the upper end and a similarly annular fixing ring 56 on the inner periphery of the lower end, concentrically. It is fixed by known vulcanization adhesive. Then, the outer fixing ring 54 is press-fitted into the inner circumferential surface of the cylindrical edge 46, and the inner fixing ring 56 is press-fitted into the outer circumferential surface of the cylindrical edge 48, so that the recess 50 is fluid-tightly closed. A pressure receiving chamber 58 is formed between the two rings 54.
56 and the rubber elastic body 52 constitute a closing member.

なお、このゴム弾性体５２は、前記ゴム弾性体３０とと
もに、外側金具２６と内側金具２８とを弾性的に連結す
る役割を果たして、双方のフランジ部３４．４０がピス
トンロッド 相対移動することを許容するものであり、このゴム弾性
体５２と−に記凹所５０とによって画成された受圧室５
８は、外側金具２６と内側金具２８とがピストンロッド
２２の軸方向に相対的に接近させられたときに、その容
積が減少せしめられるようになっている。Note that this rubber elastic body 52, together with the rubber elastic body 30, plays a role of elastically connecting the outer metal fitting 26 and the inner metal fitting 28, and allows the flange portions 34 and 40 of both to move relative to the piston rod. The pressure receiving chamber 5 is defined by the rubber elastic body 52 and the recess 50.
8 is configured such that when the outer metal fitting 26 and the inner metal fitting 28 are brought relatively close to each other in the axial direction of the piston rod 22, the volume thereof is reduced.

一方、内側金具２８のフランジ部４０　（円筒縁部４８
を含む）と前記円筒状部３８の下側部分とによって、円
環状の凹所６０が形成されている。On the other hand, the flange portion 40 (cylindrical edge 48
) and the lower portion of the cylindrical portion 38 form an annular recess 60.

この凹所６０は前記受圧室５８の内周側において、前記
緩衝器１０側に開口させられており、この凹所６０の開
口部は円環状のダイヤフラムゴム６２１ によって覆われている。このダイードフラムコム６２の
外周部と内周部とには、ともに円環状をなす固着リング
６４．６６がそれぞれ同心的に加硫接着により固着され
ていて、外側のリンク６４かフランジ部４０の円筒縁部
４８に、または内側のリング６６が円筒状部３８の下側
部分にそれぞれ圧入されることにより、凹所６０の開口
部が液密に閉塞されて、フランジ部４０を挟んで前記受
圧室５８とは反対側に平衡室６８が画成されているので
ある。This recess 60 is opened toward the shock absorber 10 on the inner peripheral side of the pressure receiving chamber 58, and the opening of this recess 60 is covered with an annular diaphragm rubber 621. Fixing rings 64 and 66, each having an annular shape, are fixed concentrically to the outer and inner circumferential parts of the diade flam comb 62 by vulcanization adhesive, and the outer link 64 or the flange part 40 By press-fitting the inner ring 66 into the cylindrical edge 48 or into the lower part of the cylindrical part 38, the opening of the recess 60 is liquid-tightly closed, and the pressure is received across the flange part 40. An equilibrium chamber 68 is defined on the opposite side of the chamber 58.

ここでは、両リング６４．６６とダイヤフラムゴム６２
とが閉塞部利を構成し、その閉塞部材と上記凹所とが共
同して囲いを、またタイヤフラムゴム６２が可撓性薄膜
をそれぞれ構成しているのである。」１記ダイヤフラム
ゴム６２は、主にその厚さ方向に弾性変形（膨出変形）
させられることにより、この平衡室６８の容積が増大す
ることを許容する役割を担っており、固着リング６４お
よび６６の間隔に比べて断面寸法が長く、言い換えれば
弛みを有していることにより、その膨出変形２ が容易となるようにされている。Here, both rings 64, 66 and diaphragm rubber 62
The closing member and the recess together constitute an enclosure, and the tire flamm rubber 62 constitutes a flexible thin film. 1. The diaphragm rubber 62 undergoes elastic deformation (bulging deformation) mainly in its thickness direction.
It plays the role of allowing the volume of this equilibrium chamber 68 to increase as a result of this, and its cross-sectional dimension is longer than the interval between the fixing rings 64 and 66, in other words, it has slack. The bulging deformation 2 is made easy.

そして、フランジ部４０の円筒縁部４８を貫通して、短
いブツシュ７０が圧入により固定され、このブツシュ７
０のブツシュ孔が受圧室５８と平衡室６８とを相互に連
通せしめるオリフィス７２を形成している。Then, a short bushing 70 is fixed by press fitting through the cylindrical edge 48 of the flange part 40.
The bushing hole 0 forms an orifice 72 that allows the pressure receiving chamber 58 and the equilibrium chamber 68 to communicate with each other.

また、上記のよ・うにそれぞれ画成され、互いに連通−
υ゛しめられた受圧室５８と平衡室６８とには、例えば
、水、ポリアルキレングリコールあるいはシリコーン浦
等の所定の非圧縮性流体がそれぞれ封入せしめられてい
るのである。In addition, each is defined as described above and communicates with each other.
A predetermined incompressible fluid such as water, polyalkylene glycol, or silicone fluid is sealed in the closed pressure chamber 58 and equilibrium chamber 68, respectively.

ところで、このようなアメパザボート２４を製作するに
際しては、まず、外側金具２６と内側金具２８とを所定
の金型内に同心的にセソｌ〜して、それらの間にゴム伺
料を注入して、ゴム弾性体３０を加硫成形するとともに
、凹所５０を形成する。By the way, when manufacturing such an American boat 24, first, the outer metal fitting 26 and the inner metal fitting 28 are placed concentrically in a predetermined mold, and a rubber filling material is injected between them. , the rubber elastic body 30 is vulcanized and molded, and the recess 50 is formed.

一方、それとは別に、リング５４．５６の間にゴム弾性
体５２を加硫成形した閉塞部材を用意する。On the other hand, separately, a closing member is prepared in which a rubber elastic body 52 is vulcanized and molded between the rings 54 and 56.

また、リング６４と６６との間にダイヤフラムゴム６２
を加硫成形した別の閉塞部材を用意する。Also, a diaphragm rubber 62 is provided between the rings 64 and 66.
Prepare another closing member which is vulcanized and molded.

３ そして、上述のように内側金具２８と外側金具２６との
間にゴム弾性体３０を備えた加硫成形品を、前記非圧縮
性流体が収容された流体槽内に浸積した状態で、凹所５
０の開口部にゴム弾性体５２に固着されたリング５４．
５６を圧入するとともに、凹所６０の開口部にダイヤフ
ラムゴム６２に固着されたリング６４．６６を圧入する
ことにより、受圧室５８および平衡室６日が画成される
と同時に、それらの内部にそれぞれ前記非圧縮性流体が
容易封入される。なお、ヘアリング４２はゴム弾性体３
０の加硫成形に先立って、あるいはそれより後において
、リング６６の圧入前に内側金具２８の円筒状部３８の
内側にカシメ付ければよく、またオリフィス７２を構成
するブツシュ７０は、内側金具２８の単品の状態で圧入
しておくことが好適である。3 Then, as described above, the vulcanized molded product provided with the rubber elastic body 30 between the inner metal fitting 28 and the outer metal fitting 26 is immersed in a fluid tank containing the incompressible fluid, recess 5
A ring 54 is fixed to the rubber elastic body 52 at the opening of the ring 54.
56 and press-fit the rings 64 and 66 fixed to the diaphragm rubber 62 into the opening of the recess 60, thereby defining the pressure receiving chamber 58 and the equilibrium chamber 6, and at the same time, forming a pressure receiving chamber 58 and an equilibrium chamber 6. In each case, the incompressible fluid is easily encapsulated. Note that the hair ring 42 is made of rubber elastic body 3.
The bushing 70 constituting the orifice 72 may be caulked to the inside of the cylindrical portion 38 of the inner fitting 28 before the ring 66 is press-fitted, prior to or after the vulcanization of the inner fitting 28. It is preferable to press-fit it as a single item.

このように、凹所５０および６０に、それぞれゴム弾性
体５２およびダイヤフラムゴム６２をリングを介して圧
入し、受圧室５８と平衡室６８と４ を形成するために、当該アッパサポート２４の成形並び
に組立てが容易であり、かつそれら受圧室５８および平
衡室６８を有しながら、構造的にもそれほど複雑になら
ない利点がある。In this way, the rubber elastic body 52 and the diaphragm rubber 62 are press-fitted into the recesses 50 and 60 through the rings, respectively, and in order to form the pressure receiving chamber 58 and the equilibrium chambers 68 and 4, the upper support 24 is formed and It has the advantage of being easy to assemble, and having the pressure receiving chamber 58 and the equilibrium chamber 68, but not having a very complicated structure.

以上のような具体例によって製造され、構成されたアノ
パサボ−１・２４ば、第１図に示されるように、緩ｆＪ
ｉ器１０のビス］・ンロノド２２を車体２０に対して弾
性的に連結すべく、内側金具２８にピストンロソｔ・２
２が取り伺けられる一方、外側金具２６が車体２０に取
りイ」けられた状態で使用される。The Anopa sabot 1/24 manufactured and configured according to the above-described specific example has a low fJ as shown in FIG.
The piston rotor t2 is attached to the inner metal fitting 28 in order to elastically connect the rotor 22 to the vehicle body 20.
2 can be removed, while the outer metal fitting 26 is used in a state where it is removed from the vehicle body 20.

そして、小変位で高周波域の振動入力に対しては、ゴム
弾性体３０並びに５２の主に剪断方向の弾性変形作用に
より、そのような振動を有効に遮断する機能が得られ、
言い換えれば動ばね定数が低くて柔らかいばね特性が（
■られるのである。In response to vibration input in a high frequency range with a small displacement, the elastic deformation action of the rubber elastic bodies 30 and 52 mainly in the shear direction provides a function to effectively block such vibrations.
In other words, the dynamic spring constant is low and the spring characteristics are soft (
■It will be done.

一方、大変位で低周波の振動入力が作用した場合には、
外側金具２６と内側金具２８とのピストンロソド２２の
軸方向における相対変位が大きくなり、両者の接近時に
受圧室５８の容積が縮小せ５ しめられる。それに伴って、受圧室５８内の流体がオリ
フィス７２を介して平衡室６８の側にダイヤフラムゴム
６２を膨出させつつ流入し、そのオリフィス７２を流通
せしめられる際に、大変位の振動に幻する減衰力が発生
する。逆に、外側金具２６と内側金具２８とが離間する
方向に大きく変位する過程では、受圧室５８の容積が増
大することにより、一旦は平衡室６８に流入した流体が
、オリフィス７２を介して再び受圧室５８側に流入する
際にも上記同様の減衰力が生じ、その結果、大変位で低
周波の振動を速やかに抑制し、ゴム弾性体３０等の過大
変形を防１１−シてその耐久性を高め得るとともに、車
輪１６等ばね下部相の大きなバウンド、リバウンドを抑
制し得て、走行安定性。On the other hand, when a large displacement and low frequency vibration input is applied,
The relative displacement between the outer metal fitting 26 and the inner metal fitting 28 in the axial direction of the piston rod 22 increases, and the volume of the pressure receiving chamber 58 is reduced when the two approach each other. Accordingly, the fluid in the pressure receiving chamber 58 flows into the equilibrium chamber 68 side through the orifice 72 while causing the diaphragm rubber 62 to bulge, and when the fluid is allowed to flow through the orifice 72, a large displacement vibration appears. A damping force is generated. Conversely, in the process where the outer metal fitting 26 and the inner metal fitting 28 are largely displaced in the direction of separation, the volume of the pressure receiving chamber 58 increases, so that the fluid that once entered the equilibrium chamber 68 flows through the orifice 72 again. A damping force similar to the above is generated when flowing into the pressure receiving chamber 58 side, and as a result, low frequency vibrations due to large displacement are quickly suppressed, preventing excessive deformation of the rubber elastic body 30, etc., and improving its durability. It is possible to improve running stability by suppressing large bounces and rebounds of the unsprung parts of the wheels 16, etc.

乗心地等を同士させることが可能となったのである。This made it possible to match the riding comfort.

次に、第３図に基づいて本発明の別の実施例を説明する
。Next, another embodiment of the present invention will be described based on FIG.

この実施例におけるアソパサボ−１・７４が前記実施例
のアンパザボート２４と異なる点は、ダイ６ ヤフラムゴム６２を挟んで前記平衡室６８とは反対側に
空気室７６が画成されて、ダイードフラムゴム６２の膨
出方向の過大変形が抑制され得るようになっている点で
ある。すなわち、内側金具２８に形成された円環状の凹
所６０の開口部が金属剛体層の囲い７８によって塞がれ
ており、この囲い７８はドーナツ状の基板８０の外周部
および内周部にそれぞれ垂直に立ち上かる円筒部８２お
よび８４をそれぞれ備え、これら円筒部８２および８４
において上記凹所６０の開口部に圧入される一方、この
囲い８０の双方の円筒部８２．８４にまたがって、基板
８０との間に空間を隔てた状態でダイヤフラムゴム６２
が加硫成形されることにより、かかるダイヤフラムゴム
６２をはさんでその両側に、前記平衡室６８と空気室７
６とがそれぞれ画成せしめられ、その空気室７６に空気
が閉じ込められているのである。The difference between the asopa sabot 1 and 74 in this embodiment from the ampaza boat 24 of the previous embodiment is that an air chamber 76 is defined on the opposite side of the equilibrium chamber 68 across the die 6 diaphragm rubber 62, and The point is that excessive deformation of 62 in the direction of expansion can be suppressed. That is, the opening of the annular recess 60 formed in the inner metal fitting 28 is closed by an enclosure 78 made of a rigid metal layer, and this enclosure 78 is provided at the outer and inner peripheries of the donut-shaped substrate 80, respectively. Vertically rising cylindrical portions 82 and 84 are provided, and these cylindrical portions 82 and 84
The diaphragm rubber 62 is press-fitted into the opening of the recess 60, while straddling both cylindrical parts 82, 84 of this enclosure 80, with a space between it and the substrate 80.
By vulcanization molding, the equilibrium chamber 68 and the air chamber 7 are formed on both sides of the diaphragm rubber 62.
6 are respectively defined, and air is confined in the air chambers 76.

その他の部分については、前記実施例と同様の構成であ
るため説明は省略するが、このようなアソパサボ−１−
７４においては、平衡室６８に流入］７ する流体によってダイヤフラムゴム６２が膨出変形させ
られる時に、空気室７６に存在する空気が圧縮せしめら
れることにより、その圧力が増大するため、その空気の
圧力によってダイヤフラムゴム６２の膨出方向の過大な
変形が抑制される。そのため、ダイヤフラムゴム６２を
かなり薄くすることができ、また、その耐久性を高める
ことができる。The other parts have the same structure as the previous embodiment, so the explanation will be omitted.
74, it flows into the equilibrium chamber 68] 7 When the diaphragm rubber 62 is expanded and deformed by the flowing fluid, the air existing in the air chamber 76 is compressed and its pressure increases. This suppresses excessive deformation of the diaphragm rubber 62 in the direction of expansion. Therefore, the diaphragm rubber 62 can be made considerably thinner, and its durability can be increased.

なお、これまで説明した実施例において、オリフィス７
２の孔径を適宜に変えること、あるいはそのオリフィス
７２を構成するブ・７シユ７０の数を増減することなど
によって、当該アソパザポートの減衰力を最適に調整す
ることができ、またブツシュ７０等オリフィス管の長さ
を長くして減衰力を大きくすることもできる。例えば、
長いオリフィス管をフランジ部４０の円筒縁部４８に沿
って円弧状に延びるように配設し、その一端部を円筒縁
部４８に圧入して受圧室５８側に開口させ、他端部を平
衡室６８側に開口させるようにして、オリフィス７２を
長く設定することも可能なので８ ある。逆に、そのようなオリフィス管を用いることなく
、単にフランジ部に孔をあけて、オリフィスを形成する
ことも可能である。Note that in the embodiments described so far, the orifice 7
By appropriately changing the hole diameter of the orifice 72 or increasing or decreasing the number of bushes 70 constituting the orifice 72, the damping force of the asopaza port can be optimally adjusted. It is also possible to increase the damping force by increasing the length. for example,
A long orifice pipe is arranged to extend in an arc shape along the cylindrical edge 48 of the flange portion 40, one end of which is press-fitted into the cylindrical edge 48 to open toward the pressure receiving chamber 58, and the other end is balanced. It is also possible to make the orifice 72 long by opening it toward the chamber 68, so there are 8 orifices. Conversely, it is also possible to form an orifice by simply drilling a hole in the flange portion without using such an orifice tube.

また、本発明は、前述のように緩衝器の外側にコイルス
プリングを備えたものだけに限らず、そのようなコイル
スプリングを有しないストラットタイプの懸架装置用ア
ソバサボ−１・とじても有効に適用することができる。Furthermore, the present invention is not limited to shock absorbers equipped with coil springs on the outside as described above, but can also be effectively applied to strut-type suspension systems that do not have such coil springs. can do.

その他、具体的な説明は割愛するが、本発明の趣旨を逸
脱することなく、当業者の知識に基づき、種々の変更、
改良等を施した態様で本発明を実施し得ることは、改め
て言うまでもないところである。In addition, although specific explanations are omitted, various modifications and changes may be made based on the knowledge of those skilled in the art without departing from the spirit of the present invention.
It goes without saying that the present invention can be implemented in modified forms.

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

第１図は本発明の−・実施例であるアッパサポートを含
む懸架装置の具体例を示す概略図である。 第２図はそのアソパサボ−１・の拡大断面図であり、第
３図は本発明の別の実施例を示す拡大断面図であって、
第２図に対応する図である。 １０；緩ｉｈ器　２０：車体 ９ ２２ｚピストンロフト ２４．１４：アソパサボ−１・ ２６；外側金具　２８；内側金具 ３０；ゴム弾性体　３２，３８：円筒状部３４．４０：
フランジ部　ｓｏ、ｓｏ：凹所５２：ゴム弾性体　５４
．５６：固着リング５８；受圧室　６２：ダイヤフラム
コム６４．６６：固着リング　６８：平衡室７０；ブツ
シュ　７２ニオリフイス ７６：空気室　７８；囲い 出願人　トヨタ自動車株式会社 同　東海ゴム工業株式会社 ０FIG. 1 is a schematic diagram showing a specific example of a suspension system including an upper support according to an embodiment of the present invention. FIG. 2 is an enlarged sectional view of the Asopa Sabo-1, and FIG. 3 is an enlarged sectional view showing another embodiment of the present invention,
FIG. 2 is a diagram corresponding to FIG. 2; 10; Loose induction heater 20: Vehicle body 9 22z Piston loft 24.14: Asopa sabo-1, 26; Outer metal fitting 28; Inner metal fitting 30; Rubber elastic body 32, 38: Cylindrical part 34.40:
Flange part so, so: recess 52: rubber elastic body 54
．． 56: Fixing ring 58; Pressure receiving chamber 62: Diaphragm comb 64. 66: Fixing ring 68: Equilibrium chamber 70; Bush 72 Niorifice 76: Air chamber 78; Enclosure Applicant Toyota Motor Corporation Tokai Rubber Industries Co., Ltd. 0

Claims (1)

【特許請求の範囲】 （１）　車体側に取り付けられる外側金具と、緩衝器の
ピストンロソ１−が取り付けられる内側金具と、それら
外側金具と内側金具との間に介在せしめられたゴム弾性
体とを含むアッパサポートにおいて、前記内側金具と外
側金具との間に画成されて該内側金具と外側金具との相
対的な変位によって容積が縮小せしめられる受圧室を設
けると共に、前記内側金具を挟んで該受圧室とは反対側
に少なくとも一部が可撓性薄膜からなる囲いにて平衡室
を形成し、それら受圧室と平衡室とをオリフィスを介し
て連通せしめる一方、該受圧室及び平衡室内に所定の非
圧縮性流体をそれぞれ封入したことを特徴とする車両懸
架装置用アソバサボ−１゜（２）前記内側金具と外側金
具とが、前記緩衝器側において該緩衝器ピストンロンド
のほぼ半径方向外向きに延出されたフランジ部をそれぞ
れ有する一方、それらフランジ部の間に前記受圧室が形
成されており、かつ、該内側金具のフランジ部を挾んで
前記緩衝器側に前記平衡室が画成され、そして該内側金
具のフランジ部を貫通して前記オリフィスが設けられて
いる特許請求の範囲第１項記載のアッパサポート。 （３）前記ゴム弾性体が、前記内側金具と外側金具との
双方のフランジ部の端部において前記緩衝器側に開口す
る環状の凹所を有する一方、該凹所開口部に、前記双方
のフランジ部の相対移動を許容する、少な（とも一部が
ゴム弾性体から成る閉塞部材を圧入せしめて若しくはカ
シメ付けて該開口部を塞ぐことによって、前記受圧室が
画成せしめられている特許請求の範囲第２項記載のアソ
パサボーｌ−０ （４）前記内側金具に、該内側金具の前記フランジ部を
主体として前記緩衝器側に開口する環状の凹所が形成さ
れ、該凹所の開口部に、弾性的に膨出変形可能なダイヤ
フラムゴムを含む環状の閉塞部材を圧入せしめて若しく
はカシメイ」げて該開口部を寒くことによって、前記平
衡室が画成せしめられており、前記凹所と閉塞部祠とが
前記囲いを、また前記ダイヤフラムゴムが前記可撓性薄
膜を、それぞれ構成している特許請求の範囲第２項また
は第３項記載のアソパサボ−１・。 （５）前記囲いを挟んで前記平衡室とは反対側に、前記
ダイヤフラノ・ゴムの過大変形を抑制する空気室が剛体
製の囲いによって画成されている特許請求の範囲第１項
ないし第４項の何れかに記載のアッパサポート。 （６）前記Ｖｉｌ１体製の囲いに前記ダイヤフラムゴム
が一体的に取りイー１けられ、該囲いが前記内側金す、
の凹所の開［１部に圧入若しくはカシメイ」けられるご
とによって、該ダイヤフラムを挟んでその両側に前記平
衡室と前記空気室とがそれぞれ画成せしめられている特
許請求の範囲第５項記載のアソパサボ−１・。[Scope of Claims] (1) An outer metal fitting attached to the vehicle body side, an inner metal fitting to which the shock absorber piston rotor 1- is attached, and a rubber elastic body interposed between these outer metal fittings and the inner metal fitting. The upper support includes a pressure receiving chamber that is defined between the inner metal fitting and the outer metal fitting and whose volume is reduced by relative displacement between the inner metal fitting and the outer metal fitting, and a An equilibrium chamber is formed by an enclosure at least partially made of a flexible thin film on the opposite side of the pressure receiving chamber, and the pressure receiving chamber and the equilibrium chamber are communicated with each other through an orifice. An assemblage sabot for a vehicle suspension system, characterized in that each of the incompressible fluids is sealed therein. The pressure receiving chamber is formed between the flange portions, and the equilibrium chamber is defined on the shock absorber side by sandwiching the flange portion of the inner metal fitting. 2. The upper support according to claim 1, wherein the orifice is provided passing through a flange portion of the inner metal fitting. (3) The rubber elastic body has an annular recess that opens toward the shock absorber at the end of the flange portion of both the inner metal fitting and the outer metal fitting, while the recess opening has an annular recess that opens toward the buffer side. A patent claim in which the pressure-receiving chamber is defined by closing the opening by press-fitting or caulking a small closing member (partially made of a rubber elastic body) that allows relative movement of the flange portion. Asopasabo l-0 according to item 2 (4) An annular recess is formed in the inner metal fitting, the flange portion of the inner metal fitting being the main body, and an annular recess that opens toward the shock absorber side, and the opening of the recess The equilibrium chamber is defined by press-fitting or crimping an annular closing member containing a diaphragm rubber that can be elastically expanded and deformed to cool the opening. Asopa sabo-1 according to claim 2 or 3, wherein the closing portion shrine constitutes the enclosure, and the diaphragm rubber constitutes the flexible thin film. (5) The enclosure constitutes the enclosure. According to any one of claims 1 to 4, an air chamber for suppressing excessive deformation of the diaphragm rubber is defined by a rigid enclosure on the opposite side of the balance chamber. The upper support according to the description.
Claim 5, wherein the equilibrium chamber and the air chamber are respectively defined on both sides of the diaphragm by opening (press-fitting or crimping) the recess of the diaphragm. Asopa Sabo-1.
JP2410584A 1984-02-10 1984-02-10 Upper support for car suspension Granted JPS60166509A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2410584A JPS60166509A (en) 1984-02-10 1984-02-10 Upper support for car suspension

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2410584A JPS60166509A (en) 1984-02-10 1984-02-10 Upper support for car suspension

Publications (2)

Publication Number Publication Date
JPS60166509A true JPS60166509A (en) 1985-08-29
JPH0434016B2 JPH0434016B2 (en) 1992-06-04

Family

ID=12129064

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2410584A Granted JPS60166509A (en) 1984-02-10 1984-02-10 Upper support for car suspension

Country Status (1)

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JP (1) JPS60166509A (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2609766A1 (en) * 1987-01-20 1988-07-22 Peugeot ELASTIC SUPPORT, IN PARTICULAR FOR THE SUSPENSION OF A VEHICLE ENGINE
DE3710629A1 (en) * 1987-03-31 1988-10-20 Audi Ag Body-side support bearing of a spring strut
US4856750A (en) * 1987-04-13 1989-08-15 Automobiles Peugeot Hydroelastic support, in particular for the suspension of a vehicle engine
US5687959A (en) * 1995-04-29 1997-11-18 Firma Carl Freudenberg Hydraulically damping rubber bearing
FR2756341A1 (en) * 1996-11-26 1998-05-29 Peugeot HYDROELASTIC SUPPORT, PARTICULARLY FOR THE SUSPENSION OF A DRIVE UNIT IN THE BODY OF A MOTOR VEHICLE
DE19620835B4 (en) * 1995-05-23 2007-06-14 Trelleborg Automotive Technical Centre Gmbh hydraulic structure

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2609766A1 (en) * 1987-01-20 1988-07-22 Peugeot ELASTIC SUPPORT, IN PARTICULAR FOR THE SUSPENSION OF A VEHICLE ENGINE
US4871150A (en) * 1987-01-20 1989-10-03 Automobiles Peugeot Elastically yieldable support in particular for the suspension of a vehicle engine
DE3710629A1 (en) * 1987-03-31 1988-10-20 Audi Ag Body-side support bearing of a spring strut
US4856750A (en) * 1987-04-13 1989-08-15 Automobiles Peugeot Hydroelastic support, in particular for the suspension of a vehicle engine
US5687959A (en) * 1995-04-29 1997-11-18 Firma Carl Freudenberg Hydraulically damping rubber bearing
DE19620835B4 (en) * 1995-05-23 2007-06-14 Trelleborg Automotive Technical Centre Gmbh hydraulic structure
FR2756341A1 (en) * 1996-11-26 1998-05-29 Peugeot HYDROELASTIC SUPPORT, PARTICULARLY FOR THE SUSPENSION OF A DRIVE UNIT IN THE BODY OF A MOTOR VEHICLE
EP0849494A1 (en) * 1996-11-26 1998-06-24 Automobiles Peugeot Elastic hydraulic support in particular for the mounting of an engine in an automotive vehicle

Also Published As

Publication number Publication date
JPH0434016B2 (en) 1992-06-04

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