JP4215221B2 - Hydraulic insulator - Google Patents

Hydraulic insulator Download PDF

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Publication number
JP4215221B2
JP4215221B2 JP07668198A JP7668198A JP4215221B2 JP 4215221 B2 JP4215221 B2 JP 4215221B2 JP 07668198 A JP07668198 A JP 07668198A JP 7668198 A JP7668198 A JP 7668198A JP 4215221 B2 JP4215221 B2 JP 4215221B2
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axis direction
side wall
axis
rigidity
inner cylinder
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JP07668198A
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JPH11257415A (en
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守 田辺
道生 和気
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Marugo Rubber Industries Ltd
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Marugo Rubber Industries Ltd
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Priority to JP07668198A priority Critical patent/JP4215221B2/en
Priority to KR1019990003768A priority patent/KR19990077402A/en
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    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K5/00—Arrangement or mounting of internal-combustion or jet-propulsion units
    • B60K5/12—Arrangement of engine supports
    • B60K5/1208—Resilient supports
    • B60K5/1216—Resilient supports characterised by the location of the supports relative to the motor or to each other
    • 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
    • F16F13/10—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 the wall being at least in part formed by a flexible membrane or the like
    • F16F13/102—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 the wall being at least in part formed by a flexible membrane or the like characterised by features of flexible walls of equilibration chambers; decoupling or self-tuning means
    • 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
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
    • F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
    • F16F15/08—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with rubber springs ; with springs made of rubber and metal
    • 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
    • F16F2228/00—Functional characteristics, e.g. variability, frequency-dependence
    • F16F2228/06—Stiffness
    • F16F2228/066—Variable stiffness

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、エンジン等の振動体を車体に防振支持する自動車用のハイドロリックインシュレータに関するものである。
【０００２】
【従来の技術】
エンジンを車体に支持する支持部材として、内外筒間に張装したゴム弾性体中にオリフィスで連絡する液封液室を隔成したブッシュタイプのハイドロリックインシュレータがある。エンジンを車体に取り付けるに際し、減衰しようとする振動の振動数に共振振動数を設定したハイドロリックインシュレータ（以下、単にインシュレータという）を使用すると、殊に低周波のシェイク振動が発生したときに液室間に大きな液の移動が起こり、車体に伝わる振動が減衰されて乗り心地が向上する。
【０００３】
エンジンの振動は、インシュレータの筒軸であるＺ軸と、Ｚ軸に直交して互いに直交するＸ軸とＹ軸の三方向に発生するが、このうち、重量がかかるＸ軸方向の振動を主方向とし、この振動荷重に最大に反応すべく、この方向に液室を対向させ、且つ、一般的には、この方向の剛性（ばね強度）を最大に設定している。ところが、車種等によってはインシュレータの取付け方式が異なり、他の方向の剛性の方を高くしなければならないことがある。
【０００４】
剛性に関与する最大の要因は、液室を構成する室壁の肉厚であるが、他の方向の剛性を上げるためには、Ｘ軸方向の剛性を相対的に下げなければならない。しかし、液室の室壁は液に接面しているものであるから、この肉厚を無闇に薄くすると、振動に基づく圧縮荷重がかかったときに室壁のみが外方へ変形してしまい、液移動を起こさず、減衰性能の低下につながる。
【０００５】
このため、室壁を内側に湾曲させたりして、外方膨出を防ぐ試みもなされているが、耐久性を低下させずにＸ軸方向の剛性を下げて他の方向の剛性を相対的に上げるには、室壁を内外筒間に架橋する限り、限界がある。
本発明は、このような課題を解決するものであり、Ｘ軸方向の液室の室壁の外方膨出を防止しながら、剛性の低下も可能にしたものである。
【０００６】
【課題を解決するための手段】
以上の課題の下、本発明は、平行配置された内筒と外筒との間に、筒軸であるＺ軸と直角なＹ軸方向に内筒を含んで外筒間に架橋されるゴム弾性体の隔壁と、隔壁のＺ軸方向両端に連続して内外筒間に架橋される同じくゴム弾性体の側壁とで、内筒を挟む対向位置でＹ軸とＺ軸とに直角な、主荷重方向であって最大の剛性に設定されたＸ軸方向に、液が封入され、且つ、オリフィスで連絡された受圧室と平衡室を対設したハイドロリックインシュレータにおいて、受圧室の側壁を、内筒からＸ軸方向に延びる縦側壁と、縦側壁の終端から外筒にかけてＺ軸方向に延びる横側壁とで構成するとともに、両横側壁の外面に、中央に支柱部を残してＺ軸方向に凹ませた凹陥部を形成し、この凹陥部を縦側壁の内面から縦側壁の肉厚を超えてＺ軸方向内側まで入り込ませ、Ｘ軸方向の剛性を下げてＹ軸方向の剛性を上げたことを特徴とするハイドロリックインシュレータを提供する。
【０００７】
以上の手段をとることにより、即ち、受圧室の側壁を内筒からＸ軸方向に延びる縦側壁と、縦側壁の終端から外筒にかけてＺ軸方向に延びる横側壁とで構成したものであるから、受圧室の縦側壁は、徒に長くならず、外方膨出を防止できて減衰性能を低下させない。加えて、横側壁に形成した凹陥部は、Ｘ軸方向の剛性を下げ、他の方向の剛性を相対的に上げることに寄与する。この点で、凹陥部は、Ｘ軸とＹ軸との剛性比を調整する調整要素ともなり得る。
【０００８】
又、本発明は、以上の構成のインシュレータにおいて、内筒の外周に外套部材を嵌着した手段を提供する。これは、Ｘ軸方向の剛性を上げずに他の方向の剛性を上げるためのより優れた手段といえる。
【０００９】
【発明の実施の形態】
以下、本発明の実施の形態を図面を参照して説明する。図１は本発明の一例を示すインシュレータの横断面図、図２は縦断面図、図３は正面図であるが、このインシュレータは、平行配置された内筒１０と外筒１２との間に、筒軸であるＺ軸と直角なＹ軸方向に内筒１０を含んで外筒１２間に架橋されるゴム弾性体の隔壁１４と、隔壁１４のＺ軸方向両端に連続して内外筒１０、１２間に架橋される同じくゴム弾性体の側壁１６とで、内筒１０を挟む対向位置でＹ軸とＺ軸とに直角なＸ軸方向に二つの空室１８、２０を対設したものである。尚、主荷重はＸ軸方向にかかり、内筒１０を外筒１２に対して反荷重側に偏心させてある。
【００１０】
この場合、内筒１０を含む側壁１６の外周に外筒１２を嵌合し、外筒１２のＺ軸方向両端を抜けないように絞ってインシュレータに構成するが、この操作を液中で行うことで、空室１８、２０は液が封入されて液室１８、２０を構成する。このとき、隔壁１４のＹ軸方向両端に溝２２を形成しておけば、液室１８、２０間を連絡するオリフィス２２となる。以上の液室１８、２０のうちの一方（図１等で下方側）を受圧室１８、他方（図１等で上方側）を平衡室２０と呼ぶ。
【００１１】
加えて、本例のものは、隔壁１４は平衡室２０側に入り込んでおり、その端近くに、Ｘ軸を中心にＹ軸両方向に細長く展開してＺ軸方向に貫通する貫通孔２４を形成している。これにより、平衡室２０に面する隔壁１４は薄肉の第二隔壁２６を形成し、耐久性が増すとともに、ダイヤフラム作用が期待できる。この他、内筒１０の外周のＺ軸方向中央部には外套部材２８を嵌着している。Ｘ軸方向の剛性を上げずにＹ軸方向の剛性を上げるためである。尚、この外套部材２８は、金属や樹脂によるものが一般的であり、内外周形状も円筒に限らず、種々の形状が考えられる。又、内筒１４と一体的に成形してもよい。更に、側壁１６の外周側には、受圧室１８、平衡室２０部分を窓状に切り欠いた補強リング３０を埋設して強度を高めている。
【００１２】
次に、本発明は、受圧室１８の側壁１６を、内筒１０からＸ軸方向に延びる縦側壁３２と、縦側壁３２の終端から外筒１２にかけてＺ軸方向に延びる横側壁３４とで構成するとともに、横側壁３４の外面に、Ｚ軸方向に凹ませた凹陥部３６を形成する。従って、横側壁３４のＺ軸方向中央には支柱部３７が残ることになる。更に、本例のものは、横側壁３４の中央Ｘ軸線上には、受圧室１８の容積を増すとともに、凹陥部３６に面する肉厚を一定にするためのＶ字形の溝３８を形成している。
【００１３】
以上の内筒１０と外筒１２とを振動体と支持体との間に介在させると、振動体の振動に伴って受圧室１８と平衡室２０とが変形し、両室１８、２０に封入された液はオリフィス２２を通って移動する。これにより、振動の減衰が図られるのであるが、このとき、受圧室１８の縦側壁３２は、受圧室１８の範囲のみに設けられ、且つ、両縦側壁３２は横側壁３４によって互いが連結されているから、圧縮時における外方膨出が防がれる。従って、十分な容積変化を来して液を移動させ、大いなる減衰性能を発揮する。この点で、縦側壁３２の肉厚はある程度厚い方が好ましい。
【００１４】
一方、以上の凹陥部３６は横側壁３４の肉厚を薄くしてＸ軸方向の剛性を下げるのに貢献している。しかし、この凹陥部３６を設けたとしても、Ｙ軸方向の剛性はあまり下がらない。何故なら、横側壁３４は、Ｙ軸方向全長に亘って外筒１２に連結しているから、Ｘ軸方向の剛性の低下の割合に比べてＹ軸方向の剛性の低下が緩やかであるからである。
【００１５】
この場合、凹陥部３６を縦側壁３２の内面よりＺ軸方向に深く入り込ませると、受圧室１８のＺ軸方向の両端に面する横側壁３４は比較的薄い肉厚になり、Ｘ軸方向の剛性を一層引き下げる。しかし、この部分の両縦側壁３２を連結する機能は変わらず、圧縮時の外方膨出は防止される。又、横側壁３４を薄肉化することは、Ｘ軸方向の動ばね定数の引下げに貢献する。
【００１６】
図１等に示すインシュレータは、Ｘ軸方向の剛性／Ｙ軸方向の剛性を１：３に設定した場合であるが、今、外径がＤで、受圧室１８の最大丈（内筒１０の外周から外筒１２の内周までの最大長さ）をＡ、幅をＷとした場合、隔壁１４の丈Ｌは約０．５１Ａ、縦側壁３２の丈ａは約０．５５Ａ、肉厚ｂは約０．１５Ｄ、横側壁３４の凹陥部３６の丈ｃは約０．４０Ａ、肉厚ｄは約０．３０Ｄ程度に設定すれば、上記の割合になる。
【００１７】
図４は本発明の他の例を示すインシュレータの横断面図、図５は縦断面図であるが、本例のものは、平衡室２０を、Ｘ軸方向にゴム弾性体の仕切壁４０で分割し、内筒１０に近い側を第一平衡室４２、遠い側を第二平衡室４４としたものである。本例の仕切壁４０は、オリフィス兼ねる仕切壁形成体４６に形成されるもので、この仕切壁形成体４６は、芯金４８が封入されたゴム弾性体で構成され、Ｚ軸方向視で半月状をしており、隔壁１４の両端に被せられて平衡室２０に装着される。
【００１８】
図６は仕切壁形成体４６の平面図であるが、表面（外筒１２側）に第一平衡室４２に通ずる第一オリフィス５０と、第二平衡室４４に通ずる第二オリフィス５２が形成されたものである。このうち、第一オリフィス５０は、仕切壁形成体４６の一端の一側からオリフィス２２に連続して他端側に延出し、他端で周回して再び他側に戻り、第一平衡室４２に開口して形成された孔５４に終結しているものである。これにより、受圧室１８の液体は、第一オリフィス５０から孔５４を通って第一平衡室４２に移動する（孔５４より一端側には堰５６が形成されて行き止まりとなっている）。
【００１９】
第二オリフィス５２は、仕切壁形成体４６の一端の中央からオリフィス２２に連続して他端側に延び、仕切壁４０を有する第二平衡室４４に通じている。これにより、受圧室１８の液体は、第二オリフィス５２を通って第二平衡室４４に移動する（一端側には同じく堰５８が形成されて行き止まりとなっている）。この場合、第一オリフィス５０は断面積が小さくて経路が長いし、第二オリフィス５２は断面積が大きくて経路が短い。シェイク振動時の減衰性を向上させ、アイドリング振動時における液移動を容易にするためである。
【００２０】
そして、受圧室１８、第一オリフィス５０及び第一平衡室４２からなる第一流体系の共振振動数を低周波のシェイク振動の振動数に、受圧室１８、第二オリフィス５２及び第二平衡室４４からなる第二流体系の共振振動数を中高周波のアイドリング振動の振動数にそれぞれチューニングしておく。これにより、シェイク振動が発生すると、先ず、第一流体系に液の移動が起こって振動は減衰する。
【００２１】
シェイク振動が過ぎると、第一流体系は目詰まりを起こすが、次に来るアイドリング振動では、第二流体系に液が流れ、動ばね定数の上昇を抑えて振動を吸収する。このとき、第一平衡室４２の室壁を構成する第二隔壁２６は、肉厚が薄くて貫通孔に面しているから、目詰まりを起こした後も更なる変形が可能であり、、振動吸収に一層貢献する。
【００２２】
更に、仕切壁４０を第二隔壁２６とは別部材で構成すると、その剛性比の幅を広げることができるから、目詰まり解消の振動数チューニングの幅を広くとることができる。尚、本例では、仕切壁４０を第二隔壁２６と別部材にしたが、成形可能な構造にしてこれらを同部材としても、貫通孔２４を存在させて第二隔壁２６を薄肉にしてその形状を調整すれば、その効果は維持できる。
【００２３】
【発明の効果】
以上、本発明によれば、受圧室の側壁を縦側壁と横側壁とで構成するとともに、横側壁の外面に、中央に支柱部を残してＺ軸方向に凹ませた凹陥部を形成したものであるから、Ｘ軸方向の剛性を下げてＹ軸方向の剛性を相対的に上げられるとともに、併せて凹陥部の形状を換えることでＸ軸とＹ軸との剛性比を適宜に設定できる。この場合において、縦側壁は受圧室の液体が存在している部分のみの短い区間に存在しており、且つ、横側壁で互いが連結されているから、外方膨出も起こさない。
【図面の簡単な説明】
【図１】 本発明の一例を示すハイドロリックインシュレータの横断面図である。
【図２】 本発明の一例を示すハイドロリックインシュレータの縦断面図である。
【図３】 本発明の一例を示すハイドロリックインシュレータの正面図である。
【図４】 本発明の他の一例を示すハイドロリックインシュレータの横断面図である。
【図５】 本発明の他の一例を示すハイドロリックインシュレータの縦断面図である。
【図６】 本発明の他の一例を示す仕切体形成体の平面図である。
【符号の説明】
１０ 内筒
１２ 外筒
１４ 隔壁
１６ 側壁
１８ 受圧室
２０ 平衡室
２８ 外套部材
３２ 縦側壁
３４ 横側壁
３６ 凹陥部
４０ 仕切壁
４２ 第一平衡室
４４ 第二平衡室[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an automotive hydraulic insulator that supports a vibration body such as an engine in a vibration-proof manner on a vehicle body.
[0002]
[Prior art]
As a support member for supporting the engine on the vehicle body, there is a bush type hydraulic insulator in which a liquid sealing liquid chamber connected with an orifice is formed in a rubber elastic body stretched between inner and outer cylinders. When installing an engine to the vehicle body, if a hydraulic insulator (hereinafter simply referred to as an insulator) with a resonance frequency set to the frequency of the vibration to be damped is used, the liquid chamber is particularly affected when low-frequency shake vibration occurs. A large liquid movement occurs in the meantime, and the vibration transmitted to the vehicle body is attenuated to improve the ride comfort.
[0003]
Engine vibration occurs in three directions: the Z-axis, which is the cylinder axis of the insulator, and the X-axis and Y-axis, which are orthogonal to the Z-axis and orthogonal to each other. In order to respond to the vibration load to the maximum, the liquid chamber is opposed to this direction, and generally the rigidity (spring strength) in this direction is set to the maximum. However, the insulator mounting method differs depending on the vehicle type and the like, and the rigidity in other directions may have to be increased.
[0004]
The greatest factor related to the rigidity is the wall thickness of the chamber wall constituting the liquid chamber, but in order to increase the rigidity in the other direction, the rigidity in the X-axis direction must be relatively lowered. However, since the chamber wall of the liquid chamber is in contact with the liquid, if this wall thickness is reduced to darkness, only the chamber wall is deformed outward when a compressive load based on vibration is applied. Liquid movement does not occur, leading to a decrease in damping performance.
[0005]
For this reason, attempts have been made to prevent outward bulging by curving the chamber wall inward, but the rigidity in the other direction is relatively reduced by lowering the rigidity in the X-axis direction without reducing the durability. As long as the chamber wall is bridged between the inner and outer cylinders, there is a limit.
The present invention solves such a problem, and makes it possible to reduce rigidity while preventing outward expansion of the chamber wall of the liquid chamber in the X-axis direction.
[0006]
[Means for Solving the Problems]
Under the above problems, the present invention provides a rubber that includes an inner cylinder in the Y-axis direction perpendicular to the Z axis that is a cylinder axis and is bridged between the outer cylinders between the inner cylinder and the outer cylinder arranged in parallel. and the partition wall of the elastic body, in the same side wall of the rubber elastic body is bridged between the inner and outer tubes in succession in the Z-axis direction end of the partition wall, in facing position sandwiching the inner tube perpendicular to the Y axis and the Z-axis, the main In the hydraulic insulator in which the liquid is sealed in the load direction and the X-axis direction set to the maximum rigidity and the pressure receiving chamber and the equilibrium chamber are connected by an orifice, the side wall of the pressure receiving chamber is A vertical side wall extending in the X-axis direction from the cylinder and a horizontal side wall extending in the Z-axis direction from the end of the vertical side wall to the outer cylinder, and in the Z-axis direction leaving a column portion in the center on the outer surface of both horizontal side walls recessed allowed to form a recess, Z-axis direction beyond the thickness of the vertical side wall of the recess from the inner surface of the vertical side walls It intruded to the side, to provide a hydraulic insulator, characterized in that by lowering the rigidity in the X-axis direction to raise the rigidity of the Y-axis direction.
[0007]
By taking the above means, that is, the side wall of the pressure receiving chamber is constituted by the vertical side wall extending in the X axis direction from the inner cylinder and the horizontal side wall extending in the Z axis direction from the end of the vertical side wall to the outer cylinder. The vertical side wall of the pressure receiving chamber is not naturally long and can prevent outward bulge and does not deteriorate the damping performance. In addition, the recessed portion formed in the lateral side wall contributes to lowering the rigidity in the X-axis direction and relatively increasing the rigidity in other directions. In this respect, the recessed portion can also be an adjustment element that adjusts the rigidity ratio between the X axis and the Y axis.
[0008]
Further, the present invention is Te insulator smell of the above configuration, provides a means by fitting the mantle member on the outer periphery of the inner cylinder. This can be said to be a better means for increasing the rigidity in the other direction without increasing the rigidity in the X-axis direction.
[0009]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings. 1 is a cross-sectional view of an insulator showing an example of the present invention, FIG. 2 is a longitudinal cross-sectional view, and FIG. 3 is a front view. The insulator is disposed between an inner cylinder 10 and an outer cylinder 12 arranged in parallel. A rubber elastic partition 14 including the inner cylinder 10 in the Y-axis direction perpendicular to the Z-axis that is the cylinder axis and bridged between the outer cylinders 12, and the inner and outer cylinders 10 are continuously connected to both ends of the partition 14 in the Z-axis direction. , 12 and a side wall 16 of the same rubber elastic body, in which two vacant chambers 18, 20 are arranged in the X-axis direction perpendicular to the Y-axis and the Z-axis at a position opposite to the inner cylinder 10 It is. The main load is applied in the X-axis direction, and the inner cylinder 10 is eccentric with respect to the outer cylinder 12 on the opposite load side.
[0010]
In this case, the outer cylinder 12 is fitted to the outer periphery of the side wall 16 including the inner cylinder 10, and the insulator is squeezed so as not to pass through both ends in the Z-axis direction of the outer cylinder 12, and this operation is performed in the liquid. Thus, the vacant chambers 18 and 20 are filled with liquid to form the liquid chambers 18 and 20. At this time, if grooves 22 are formed at both ends of the partition wall 14 in the Y-axis direction, the orifices 22 communicate with the liquid chambers 18 and 20. One of the liquid chambers 18 and 20 (the lower side in FIG. 1 and the like) is referred to as the pressure receiving chamber 18, and the other (the upper side in FIG. 1 and the like) is referred to as the equilibrium chamber 20.
[0011]
In addition, in this example, the partition wall 14 enters the equilibrium chamber 20 side, and a through hole 24 is formed near the end of the partition wall 14 so as to be elongated in both directions of the Y axis centering on the X axis and penetrating in the Z axis direction. is doing. As a result, the partition wall 14 facing the equilibrium chamber 20 forms a thin second partition wall 26, and durability can be increased and a diaphragm action can be expected. In addition, a mantle member 28 is fitted to the central portion of the outer periphery of the inner cylinder 10 in the Z-axis direction. This is because the rigidity in the Y-axis direction is increased without increasing the rigidity in the X-axis direction. The outer member 28 is generally made of metal or resin, and the inner and outer peripheral shapes are not limited to cylinders, and various shapes are conceivable. Further, it may be formed integrally with the inner cylinder 14. Further, a reinforcing ring 30 in which the pressure receiving chamber 18 and the equilibrium chamber 20 are cut out in a window shape is embedded on the outer peripheral side of the side wall 16 to increase the strength.
[0012]
Next, according to the present invention, the side wall 16 of the pressure receiving chamber 18 includes a vertical side wall 32 extending from the inner cylinder 10 in the X-axis direction and a horizontal side wall 34 extending from the end of the vertical side wall 32 to the outer cylinder 12 in the Z-axis direction. At the same time, a recessed portion 36 that is recessed in the Z-axis direction is formed on the outer surface of the lateral side wall 34. Accordingly, the column portion 37 remains in the center of the lateral side wall 34 in the Z-axis direction. Further, in this example, a V-shaped groove 38 is formed on the central X-axis line of the lateral side wall 34 to increase the volume of the pressure receiving chamber 18 and to make the wall thickness facing the recessed portion 36 constant. ing.
[0013]
When the inner cylinder 10 and the outer cylinder 12 are interposed between the vibrating body and the support body, the pressure receiving chamber 18 and the equilibrium chamber 20 are deformed along with the vibration of the vibrating body, and are enclosed in both the chambers 18 and 20. The liquid thus moved moves through the orifice 22. Thereby, the vibration is attenuated. At this time, the vertical side wall 32 of the pressure receiving chamber 18 is provided only in the range of the pressure receiving chamber 18, and both the vertical side walls 32 are connected to each other by the horizontal side wall 34. Therefore, outward bulge during compression is prevented. Therefore, a sufficient volume change is caused to move the liquid, and a great damping performance is exhibited. In this respect, it is preferable that the vertical side wall 32 is thick to some extent.
[0014]
On the other hand, the recessed portion 36 described above contributes to reducing the rigidity in the X-axis direction by reducing the thickness of the lateral side wall 34. However, even if this recess 36 is provided, the rigidity in the Y-axis direction does not decrease much. This is because the lateral side wall 34 is connected to the outer cylinder 12 over the entire length in the Y-axis direction, so that the decrease in rigidity in the Y-axis direction is moderate compared to the rate of decrease in rigidity in the X-axis direction. is there.
[0015]
In this case, when the recessed portion 36 is inserted deeper in the Z-axis direction than the inner surface of the vertical side wall 32, the lateral side walls 34 facing both ends in the Z-axis direction of the pressure receiving chamber 18 have a relatively thin wall thickness. The rigidity is further reduced. However, the function of connecting both the vertical side walls 32 of this part does not change, and outward bulging during compression is prevented. Further, reducing the thickness of the lateral side wall 34 contributes to lowering the dynamic spring constant in the X-axis direction.
[0016]
The insulator shown in FIG. 1 and the like is a case where the rigidity in the X-axis direction / the rigidity in the Y-axis direction is set to 1: 3, but now the outer diameter is D and the maximum length of the pressure receiving chamber 18 (the inner cylinder 10 When the maximum length from the outer periphery to the inner periphery of the outer cylinder 12 is A and the width is W, the height L of the partition wall 14 is about 0.51 A, the length a of the vertical side wall 32 is about 0.55 A, and the wall thickness b. If the height c of the recessed portion 36 of the lateral side wall 34 is set to about 0.40 A, and the thickness d is set to about 0.30 D, the above ratio is obtained.
[0017]
4 is a cross-sectional view of an insulator showing another example of the present invention, and FIG. 5 is a vertical cross-sectional view. In this example, the balance chamber 20 is divided by a rubber elastic partition wall 40 in the X-axis direction. The side closer to the inner cylinder 10 is divided into a first equilibrium chamber 42 and the far side is a second equilibrium chamber 44. The partition wall 40 of this example is formed in a partition wall forming body 46 that also serves as an orifice. The partition wall forming body 46 is composed of a rubber elastic body in which a core metal 48 is enclosed, and is half a moon as viewed in the Z-axis direction. It is attached to both ends of the partition wall 14 and attached to the equilibrium chamber 20.
[0018]
6 is a plan view of the partition wall forming body 46. On the surface (on the outer cylinder 12 side), a first orifice 50 communicating with the first equilibrium chamber 42 and a second orifice 52 communicating with the second equilibrium chamber 44 are formed. It is a thing. Of these, the first orifice 50 extends from one side of one end of the partition wall forming body 46 to the other end side continuously to the orifice 22, circulates at the other end and returns to the other side again. And ends with a hole 54 formed in the opening. As a result, the liquid in the pressure receiving chamber 18 moves from the first orifice 50 through the hole 54 to the first equilibrium chamber 42 (a weir 56 is formed on one end side from the hole 54 to make a dead end).
[0019]
The second orifice 52 extends from the center of one end of the partition wall forming body 46 to the other end side continuously to the orifice 22 and communicates with the second equilibrium chamber 44 having the partition wall 40. As a result, the liquid in the pressure receiving chamber 18 moves to the second equilibrium chamber 44 through the second orifice 52 (a weir 58 is also formed on one end side to make a dead end). In this case, the first orifice 50 has a small cross-sectional area and a long path, and the second orifice 52 has a large cross-sectional area and a short path. This is to improve the attenuation during shake vibration and facilitate liquid movement during idling vibration.
[0020]
Then, the resonance frequency of the first fluid system composed of the pressure receiving chamber 18, the first orifice 50, and the first equilibrium chamber 42 is changed to the frequency of the low-frequency shake vibration, and the pressure receiving chamber 18, the second orifice 52, and the second equilibrium chamber 44. The resonance frequency of the second fluid system consisting of the above is tuned to the frequency of the mid-high frequency idling vibration. As a result, when shake vibration occurs, first, liquid movement occurs in the first fluid system, and the vibration is attenuated.
[0021]
When the shake vibration is over, the first fluid system becomes clogged, but in the next idling vibration, the liquid flows into the second fluid system, suppressing the increase of the dynamic spring constant and absorbing the vibration. At this time, since the second partition wall 26 constituting the chamber wall of the first equilibrium chamber 42 is thin and faces the through hole, further deformation is possible even after clogging, Further contributes to vibration absorption.
[0022]
Furthermore, if the partition wall 40 is formed of a member different from the second partition wall 26, the width of the rigidity ratio can be widened, so that the frequency tuning width for eliminating clogging can be widened. In this example, the partition wall 40 is formed as a separate member from the second partition wall 26. However, even if these are formed as a moldable structure, the through-hole 24 is present to make the second partition wall 26 thinner. If the shape is adjusted, the effect can be maintained.
[0023]
【The invention's effect】
As described above, according to the present invention, the side wall of the pressure receiving chamber is composed of the vertical side wall and the side wall, and the outer surface of the side wall is formed with the recessed portion that is recessed in the Z-axis direction leaving the column portion in the center. Therefore, the rigidity in the X-axis direction can be lowered to relatively increase the rigidity in the Y-axis direction, and the rigidity ratio between the X-axis and the Y-axis can be appropriately set by changing the shape of the recessed portion. In this case, the vertical side wall exists in a short section of only the portion where the liquid in the pressure receiving chamber exists, and since the side walls are connected to each other, the outward bulge does not occur.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of a hydraulic insulator showing an example of the present invention.
FIG. 2 is a longitudinal sectional view of a hydraulic insulator showing an example of the present invention.
FIG. 3 is a front view of a hydraulic insulator showing an example of the present invention.
FIG. 4 is a cross-sectional view of a hydraulic insulator showing another example of the present invention.
FIG. 5 is a longitudinal sectional view of a hydraulic insulator showing another example of the present invention.
FIG. 6 is a plan view of a partition body forming body showing another example of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 10 Inner cylinder 12 Outer cylinder 14 Partition 16 Side wall 18 Pressure receiving chamber 20 Equilibrium chamber 28 Outer member 32 Vertical side wall 34 Horizontal side wall 36 Recessed part 40 Partition wall 42 First equilibrium chamber 44 Second equilibrium chamber

Claims (3)

平行配置された内筒と外筒との間に、筒軸であるＺ軸と直角なＹ軸方向に内筒を含んで外筒間に架橋されるゴム弾性体の隔壁と、隔壁のＺ軸方向両端に連続して内外筒間に架橋される同じくゴム弾性体の側壁とで、内筒を挟む対向位置でＹ軸とＺ軸とに直角な、主荷重方向であって最大の剛性に設定されたＸ軸方向に、液が封入され、且つ、オリフィスで連絡された受圧室と平衡室を対設したハイドロリックインシュレータにおいて、受圧室の側壁を、内筒からＸ軸方向に延びる縦側壁と、縦側壁の終端から外筒にかけてＺ軸方向に延びる横側壁とで構成するとともに、両横側壁の外面に、中央に支柱部を残してＺ軸方向に凹ませた凹陥部を形成し、この凹陥部を縦側壁の内面から縦側壁の肉厚を超えてＺ軸方向内側まで入り込ませ、Ｘ軸方向の剛性を下げてＹ軸方向の剛性を上げたことを特徴とするハイドロリックインシュレータ。Between the inner cylinder and the outer cylinder arranged in parallel, a partition wall of a rubber elastic body that includes the inner cylinder in the Y-axis direction perpendicular to the Z axis that is the cylinder axis and is bridged between the outer cylinders, and the Z axis of the partition wall Set to the maximum rigidity in the main load direction, perpendicular to the Y and Z axes, at opposite positions across the inner cylinder, with the rubber elastic body side wall continuously bridged between the inner and outer cylinders at both ends in the direction. In a hydraulic insulator in which liquid is sealed in the X-axis direction and the pressure-receiving chamber and the equilibrium chamber are connected to each other by an orifice, the side wall of the pressure-receiving chamber is a vertical side wall extending from the inner cylinder in the X-axis direction. , from the end of the vertical side wall toward the outer cylinder while constituted by a transverse side wall extending in the Z axis direction, the outer surface of both lateral side walls, leaving the pillar portion to form a recessed portion recessed in the Z-axis direction in the center, this The recessed part is inserted from the inner surface of the vertical side wall to the inner side in the Z axis direction beyond the thickness of the vertical side wall, and the X axis direction. Hydraulic insulator, characterized in that raised the rigidity of the Y-axis direction to lower the rigidity. 内筒の外周に外套部材を嵌着した請求項１に記載のハイドロリックインシュレータ。  The hydraulic insulator according to claim 1, wherein a mantle member is fitted to the outer periphery of the inner cylinder. 平衡室を、Ｘ軸方向にゴム弾性体の仕切壁で分割し、内筒に近い側を第一平衡室、遠い側を第二平衡室とした請求項１又は２に記載のハイドロリックインシュレータ。  The hydraulic insulator according to claim 1 or 2, wherein the equilibrium chamber is divided by a rubber elastic partition wall in the X-axis direction, and a side closer to the inner cylinder is a first equilibrium chamber and a far side is a second equilibrium chamber.
JP07668198A 1998-03-09 1998-03-09 Hydraulic insulator Expired - Fee Related JP4215221B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP07668198A JP4215221B2 (en) 1998-03-09 1998-03-09 Hydraulic insulator
KR1019990003768A KR19990077402A (en) 1998-03-09 1999-02-04 Hydraulic Insulator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP07668198A JP4215221B2 (en) 1998-03-09 1998-03-09 Hydraulic insulator

Related Child Applications (1)

Application Number Title Priority Date Filing Date
JP6420599A Division JPH11315879A (en) 1999-03-11 1999-03-11 Hydraulic insulator

Publications (2)

Publication Number Publication Date
JPH11257415A JPH11257415A (en) 1999-09-21
JP4215221B2 true JP4215221B2 (en) 2009-01-28

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JP07668198A Expired - Fee Related JP4215221B2 (en) 1998-03-09 1998-03-09 Hydraulic insulator

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Country Link
JP (1) JP4215221B2 (en)
KR (1) KR19990077402A (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2876429B1 (en) * 2004-10-11 2007-02-23 Hutchinson Sa HYDRAULIC ANTI-VIBRATION DEVICE FOR A VEHICLE AND METHOD OF MANUFACTURING SUCH A DEVICE
FR2876430B1 (en) * 2004-10-11 2008-10-10 Hutchinson Sa ANTI-VIBRATORY HYDRAULIC DEVICE AND METHOD OF MANUFACTURING THE SAME
JP2015105672A (en) * 2013-11-28 2015-06-08 トヨタ自動車株式会社 Liquid-sealed vibration control device

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