JPH02129426A - Fluid enclosed type mount device - Google Patents
Fluid enclosed type mount deviceInfo
- Publication number
- JPH02129426A JPH02129426A JP27991288A JP27991288A JPH02129426A JP H02129426 A JPH02129426 A JP H02129426A JP 27991288 A JP27991288 A JP 27991288A JP 27991288 A JP27991288 A JP 27991288A JP H02129426 A JPH02129426 A JP H02129426A
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- receiving chamber
- fluid
- pressure receiving
- metal fitting
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000012530 fluid Substances 0.000 title claims description 46
- 239000002184 metal Substances 0.000 claims abstract description 61
- 230000007246 mechanism Effects 0.000 claims abstract description 26
- 239000012528 membrane Substances 0.000 claims abstract description 21
- 230000005489 elastic deformation Effects 0.000 claims abstract description 11
- 238000010521 absorption reaction Methods 0.000 claims description 24
- 239000007788 liquid Substances 0.000 claims description 8
- 239000010409 thin film Substances 0.000 claims description 4
- 230000000694 effects Effects 0.000 abstract description 33
- 238000005192 partition Methods 0.000 abstract description 25
- 238000013016 damping Methods 0.000 description 12
- 230000002093 peripheral effect Effects 0.000 description 8
- 230000001105 regulatory effect Effects 0.000 description 6
- 238000004891 communication Methods 0.000 description 5
- 230000033001 locomotion Effects 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000012779 reinforcing material Substances 0.000 description 2
- 238000010079 rubber tapping Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000002195 synergetic effect Effects 0.000 description 2
- -1 alkylene glycol Chemical compound 0.000 description 1
- 230000004888 barrier function Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- LYCAIKOWRPUZTN-UHFFFAOYSA-N ethylene glycol Natural products OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 1
- WGCNASOHLSPBMP-UHFFFAOYSA-N hydroxyacetaldehyde Natural products OCC=O WGCNASOHLSPBMP-UHFFFAOYSA-N 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 229920001515 polyalkylene glycol Polymers 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 229920002545 silicone oil Polymers 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 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
- F16F13/10—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
- F16F13/105—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 partitions between two working chambers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
Description
【発明の詳細な説明】
(技術分野)
本発明は、内部に封入された流体の流動に基づいて振動
の伝達を低減乃至は防止するようにした流体封入式マウ
ント装置に係り、特に広い周波数域に亘って優れた防振
特性を発揮し得る流体封入式マウント装置に関するもの
である。Detailed Description of the Invention (Technical Field) The present invention relates to a fluid-filled mount device that reduces or prevents vibration transmission based on the flow of fluid sealed inside, and particularly relates to a fluid-filled mount device that reduces or prevents transmission of vibrations based on the flow of fluid sealed inside. The present invention relates to a fluid-filled mount device that can exhibit excellent vibration damping characteristics over a wide range of periods.
(背景技術)
従来から、自動車のエンジンマウント等の如く、振動伝
達系を構成する二つの部材間に介装されて、それらの部
材を防振連結し、或いは一方の部材を他方の部材に対し
て防振支持せしめるマウント装置の一種として、特開昭
55−107142号公報や実開昭58−114933
号公報等に開示されているように、互いに所定距離を隔
てて配置された第一の支持金具と第二の支持金具とを、
それらの間に介装せしめられたゴム弾性体にて弾性的に
連結して、連結体を構成する一方、該連結体の内部に、
所定の非圧縮性流体が封入された流体収容室を形成する
と共に、該流体収容室内に仕切部材を配して、該仕切部
材を挟んだ両側に、防振すべき振動が入力される受圧室
と、少なくとも一部が弾性薄膜にて画成された容積可変
の平衡室とを形成し、更にそれら受圧室と平衡室とを相
互に連通ずるオリフィス通路を設けてなる構造の、所謂
流体封入式マウント装置が知られている。かかるマウン
ト装置にあっては、振動の入力に際して生ぜしめられる
、受圧室と平衡室との間での、オリフィス通路を通じて
の流体の流動に基づく共振作用によって、該オリフィス
通路に設定された所定の防振効果が発揮され得ることと
なるのである。(Background Art) Conventionally, devices such as automobile engine mounts have been interposed between two members constituting a vibration transmission system to connect these members in a vibration-proof manner, or to connect one member to the other. As a type of mount device for anti-vibration support, Japanese Patent Laid-Open No. 55-107142 and Utility Model Laid-Open No. 58-114933
As disclosed in the above publication, a first support metal fitting and a second support metal fitting are arranged at a predetermined distance from each other,
They are elastically connected by a rubber elastic body interposed between them to form a connecting body, and inside the connecting body,
A pressure receiving chamber that forms a fluid storage chamber sealed with a predetermined incompressible fluid, and a partition member is disposed within the fluid storage chamber, and vibrations to be damped are input to both sides of the partition member. The so-called fluid-filled type has a structure in which a volume-variable equilibrium chamber is defined at least in part by an elastic thin film, and an orifice passage is provided to communicate the pressure-receiving chamber and the equilibrium chamber with each other. Mounting devices are known. In such a mounting device, a predetermined barrier set in the orifice passage is caused by a resonance effect based on the flow of fluid between the pressure receiving chamber and the equilibrium chamber through the orifice passage, which is generated when vibration is input. This means that a vibration effect can be exerted.
ところが、かかる構造のマウント装置では、そのオリフ
ィス通路内における流体の共振作用に基づく防振効果が
、該オリフィス通路内を流動せしめられる流体の共振点
付近の比較的狭い周波数域の入力振動に対してしか、有
効には発揮され得す、それよりも更に高周波数域の振動
入力時には、該オリフィス通路が実質的に閉塞状態とな
るために、マウント動ばね定数の著しい上昇が惹起され
て、却って防振機能が低下するといった問題を有してい
たのである。However, in a mounting device having such a structure, the vibration damping effect based on the resonance effect of the fluid in the orifice passage is not effective against input vibration in a relatively narrow frequency range near the resonance point of the fluid flowing in the orifice passage. However, when vibrations are input in a higher frequency range than that which can be effectively exerted, the orifice passage becomes substantially blocked, causing a significant increase in the mount dynamic spring constant, and rather preventing prevention. The problem was that the vibration function deteriorated.
そこで、特開昭57−9340号公報等には、前記受圧
室と平衡室とを仕切る仕切壁の内部に、それら受圧室及
び平衡室に対してそれぞれ連通せしめられた連通空間を
形成すると共に、該連通空間内に薄肉板状の可動部材を
収容配置せしめてなる構造の液圧吸収機構が提案されて
いる。即ち、かかる液圧吸収機構を備えたマウント装置
に対し、低周波大振幅の振動が入力された際には、連通
空間を受圧室乃至は平衡室に連通ずる通孔が可動板によ
って閉塞せしめられることにより、その液圧吸収機構が
実質的に機能することなく、前記オリフィス通路内を流
動する流体の共振作用による防振効果が有効に確保され
得るのであり、また一方、高周波小振幅の振動が入力さ
れた際には、可動板の変位に基づいて受圧室と平衡室と
の間での実質的な流体の流動が許容されて、受圧室内の
液圧上昇に伴うマウント高動ばね化が回避され得ること
となる。Therefore, in Japanese Patent Application Laid-Open No. 57-9340, etc., a communication space is formed inside a partition wall that partitions the pressure receiving chamber and the equilibrium chamber, and communicates with the pressure receiving chamber and the equilibrium chamber, respectively. A hydraulic pressure absorption mechanism has been proposed in which a thin plate-like movable member is accommodated and arranged within the communication space. That is, when low-frequency, large-amplitude vibrations are input to a mount device equipped with such a hydraulic pressure absorption mechanism, the movable plate closes the communication hole that communicates the communication space with the pressure receiving chamber or the equilibrium chamber. As a result, the vibration damping effect due to the resonance effect of the fluid flowing in the orifice passage can be effectively ensured without the hydraulic pressure absorption mechanism substantially functioning. When input, substantial fluid flow is allowed between the pressure receiving chamber and the equilibrium chamber based on the displacement of the movable plate, thereby avoiding the mount from becoming a highly dynamic spring due to an increase in liquid pressure within the pressure receiving chamber. This means that it can be done.
ところが、このような構造の液圧吸収機構にあっては、
構造が橿めて複雑であるために、製作上およびコスト上
の問題を有していたのであり、更にま゛た、振動入力に
際して、可動板が連通空間内面に当接せしめられること
によって、打音が生じるといった問題をも内在していた
のである。However, in a hydraulic pressure absorption mechanism with such a structure,
The structure is extremely complex, which poses manufacturing and cost problems.Furthermore, when vibration is input, the movable plate comes into contact with the inner surface of the communication space, causing damage to the vibration. It also had the problem of generating noise.
一方、特開昭58−163842号公報や特開昭61−
197836号公報等には、受圧室と平衡室とを仕切る
仕切壁の一部を、ゴム弾性膜にて構成せしめてなる構造
の液圧吸収機構が、明らかにされている。即ち、かかる
構造の液圧吸収機構を備えたマウント装置にあっては、
低周波数域の振動入力時において、かかるゴム弾性膜の
変形量が、それ自体の弾性力によって制限されることに
より、液圧吸収機構が実質的に機能することなく、前記
オリフィス通路内を流動する流体の共振作用による防振
効果が有効に確保され得るのであり、また一方、高周波
小振幅の振動入力時には、かかるゴム弾性膜の弾性変形
に基づいて受圧室と平衡室との間での実質的な流体の流
動が許容されて、受圧室内の液圧上昇に伴うマウント高
動ばね化が、効果的に回避され得ることとなる。On the other hand, JP-A-58-163842 and JP-A-61-
Publication No. 197836 discloses a hydraulic pressure absorption mechanism having a structure in which a part of a partition wall that partitions a pressure receiving chamber and an equilibrium chamber is made of a rubber elastic membrane. That is, in a mounting device equipped with a hydraulic pressure absorption mechanism having such a structure,
When vibration is input in a low frequency range, the amount of deformation of the rubber elastic membrane is limited by its own elastic force, so that the fluid flows through the orifice passage without the hydraulic pressure absorption mechanism substantially functioning. The vibration damping effect due to the resonance effect of the fluid can be effectively ensured, and on the other hand, when high frequency and small amplitude vibrations are input, the elastic deformation of the rubber elastic membrane effectively reduces the vibration between the pressure receiving chamber and the equilibrium chamber. As a result, the mount can be effectively prevented from becoming a highly dynamic spring due to an increase in the fluid pressure within the pressure receiving chamber.
しかしながら、このような構造の液圧吸収機構にあって
は、マウントに対する大荷重入力時に、ゴム弾性膜に対
して過大な応力が生ぜしめられることとなるために、該
ゴム弾性膜自体の耐久性や仕切壁に対する固着部位の耐
久性が大きな問題となり、充分な製品耐久性および信鯨
性が得られ難いというた問題を有していたのである。ま
た、かかるゴム弾性膜の耐久性の向上と変形量の規制効
果の向上とを図るべく、その内部に帆布等の補強材を埋
設せしめてなる構造のものも提案されているが、それに
よっても充分な耐久性を得ることは難しく、逆に、補強
材の埋設のために製造が困難でコスト的にも不利となる
といった問題が惹起されることとなるのである。However, in a hydraulic pressure absorption mechanism having such a structure, when a large load is applied to the mount, excessive stress is generated on the rubber elastic membrane, which reduces the durability of the rubber elastic membrane itself. The durability of the parts fixed to the walls and partition walls became a major problem, and it was difficult to obtain sufficient product durability and reliability. In addition, in order to improve the durability of the rubber elastic membrane and improve the effect of regulating the amount of deformation, a structure in which a reinforcing material such as canvas is embedded inside the membrane has been proposed. It is difficult to obtain sufficient durability, and conversely, problems arise in that the reinforcing material is embedded, making manufacturing difficult and disadvantageous in terms of cost.
(解決課題)
ここにおいて、本発明は、上述の如き事情を背景として
為されたものであって、その解決課題とするところは、
オリフィス通路内を流動せしめられる流体の共振作用に
基づく防振効果を確保しつつ、該オリフィス通路に設定
された共振周波数よりも更に高周波数域の振動入力時に
おけるマウント動ばねの著しい上昇を解消せしめ得る、
簡単で且つ新規な構造の液圧吸収機構を明らかにし、以
て広い周波数域の入力振動に対して優れた防振効果を発
揮し得る流体封入式マウント装置を提供することにある
。(Problem to be solved) Here, the present invention has been made against the background of the above-mentioned circumstances, and the problem to be solved is:
While ensuring the vibration damping effect based on the resonance effect of the fluid flowing in the orifice passage, it eliminates the significant rise of the mount moving spring when vibration is input in a higher frequency range than the resonance frequency set in the orifice passage. obtain,
The object of the present invention is to clarify a hydraulic pressure absorption mechanism with a simple and novel structure, and thereby to provide a fluid-filled mount device that can exhibit an excellent vibration damping effect against input vibrations in a wide frequency range.
(解決手段)
そして、かかる課題を解決すべく、本発明にあっては、
互いに所定距離を隔てて配置された第一の支持金具と第
二の支持金具とを、ゴム弾性体にて一体的に連結せしめ
る一方、それら第一の支持金具と第二の支持金具との間
に、それぞれ、所定の非圧縮性流体が封入された、防振
すべき振動が入力される受圧室と、少なくとも一部が弾
性薄膜にて画成された容積可変の平衡室とを形成すると
共に、それら受圧室と平衡室とを相互に連通ずるオリフ
ィス通路を設けてなる流体封入式マウント装置において
、前記受圧室内の液圧が及ぼされる部位の少なくとも一
部に可撓性膜を有すると共に、該可撓性膜の背後に所定
容積の密閉された空気室を備え、かかる受圧室内に内圧
変動が生ぜしめられた際、該空気室の容積変化を伴う該
可撓性膜の弾性変形が生ぜしめられる液圧吸収機構を、
前記受圧室内に配したことを、その特徴とするものであ
る。(Solution Means) In order to solve this problem, the present invention includes:
A first support metal fitting and a second support metal fitting that are arranged at a predetermined distance from each other are integrally connected by a rubber elastic body, while a gap between the first support metal fitting and the second support metal fitting is a pressure-receiving chamber filled with a predetermined incompressible fluid and into which vibrations to be damped are input; and a variable-volume equilibrium chamber at least partially defined by an elastic thin film. , a fluid-filled mounting device provided with an orifice passage that communicates the pressure receiving chamber and the equilibrium chamber with each other; A sealed air chamber with a predetermined volume is provided behind the flexible membrane, and when an internal pressure fluctuation occurs in the pressure receiving chamber, elastic deformation of the flexible membrane occurs accompanied by a change in the volume of the air chamber. The hydraulic pressure absorption mechanism
Its feature is that it is disposed within the pressure receiving chamber.
(実施例)
以下、本発明を更に具体的に明らかにするために、本発
明の実施例について、図面を参照しつつ、詳細に説明す
ることとする。(Examples) Hereinafter, in order to clarify the present invention more specifically, examples of the present invention will be described in detail with reference to the drawings.
先ず、第1図及び第2図には、本発明を自動車用エンジ
ンマウントに通用したものの一興体例が示されている。First, FIGS. 1 and 2 show an example of an engine mount for an automobile in which the present invention is applied.
かかる図において、1o及び12は、それぞれ第−及び
第二の支持金具であって、−振動入力方向(第1図中、
上下方向)に所定距離を隔てて配置されている。また、
これら第一の支持金具10と第二の支持金具12との間
には、ゴム弾性体30が介装されており、該ゴム弾性体
30にて、かかる第一の支持金具lOと第二の支持金具
12とが、相互に一体的に且つ弾性的に連結せしめられ
ている。そして、本実施例におけるエンジンマウントに
あっては、かかる第一の支持金具10および第二の支持
金具12が、それぞれエンジンユニット側および車体側
に取り付けられることにより、かかるエンジンユニット
を車体に対して防振支持するようになっているのである
。In this figure, 1o and 12 are the first and second support fittings, respectively, and - vibration input direction (in FIG. 1,
They are arranged at a predetermined distance apart in the vertical direction. Also,
A rubber elastic body 30 is interposed between the first support metal fitting 10 and the second support metal fitting 12, and the rubber elastic body 30 allows the first support metal fitting lO and the second support metal fitting 10 to The support fittings 12 are integrally and elastically connected to each other. In the engine mount in this embodiment, the first support fitting 10 and the second support fitting 12 are attached to the engine unit side and the vehicle body side, respectively, so that the engine unit is attached to the vehicle body. It is designed to provide anti-vibration support.
なお、そのような装着時には、かかるエンジンマウント
に対して、エンジンユニット重量が及ぼされることによ
って、第4図に示されている如き、成る程度の初期荷重
が作用せしめられた状態下に配されることとなる。When mounted in this manner, the weight of the engine unit is applied to the engine mount, so that the engine mount is placed under a state where an initial load of the extent shown in FIG. 4 is applied. That will happen.
より詳細には、前記第一の支持金具10は、全体として
略円板形状を呈しており、その−径方向に対向する外周
縁部が、それぞれ、周方向略凹半周に亘る部位において
、径方向外方に所定幅で延長された延出部13とされて
いる。また、該第−の支持金具10の中央部には、内側
面に固着されたブロック状の支持部14と、外側面上に
突出する取付ボルト16とが、それぞれ、一体的に設け
られている。More specifically, the first support fitting 10 has an approximately disk shape as a whole, and the outer circumferential edges facing each other in the radial direction each have a radial diameter at a portion extending over an approximately concave half circumference in the circumferential direction. The extending portion 13 extends outward in the direction by a predetermined width. Furthermore, a block-shaped support portion 14 fixed to the inner surface and a mounting bolt 16 protruding from the outer surface are each integrally provided at the center of the second support fitting 10. .
一方、第二の支持金具12は、略浅底の有底円筒形状を
呈し、開口周縁部において外フランジ部20を有する底
金具18と、全体として略円筒形状を呈し、軸方向一端
側開口部においてかしめ部22を備えた筒金具24とに
よって構成されており、該底金具18の外フランジ部2
0に対して、筒金具24のかしめ部22が、かしめ固定
されることによって、一体的に組み付けられている。ま
た、かかる第二の支持金具12を構成する底金具18に
は、底部外面上に突出する取付ボルト25.25が、一
体的に設けられている。On the other hand, the second support fitting 12 has a substantially shallow cylindrical shape with a bottom, and has a bottom fitting 18 having an outer flange portion 20 at the opening periphery. The outer flange portion 2 of the bottom metal fitting 18 is composed of a cylindrical metal fitting 24 having a caulked portion 22 at the bottom.
0, the caulking portion 22 of the cylindrical metal fitting 24 is integrally assembled by caulking and fixing. Further, the bottom fitting 18 constituting the second support fitting 12 is integrally provided with mounting bolts 25, 25 that protrude from the outer surface of the bottom portion.
そして、これら第一の支持金具10と第二の支持金具1
2とは、該第二の支持金具12が、第一の支持金具10
側に開口する状態で、互いに所定距離を隔てて同心的に
対向配置せしめられている。These first support fittings 10 and second support fittings 1
2 means that the second support fitting 12 is the first support fitting 10.
They are arranged concentrically facing each other with a predetermined distance apart, with openings on the sides.
また、そこにおいて、第二の支持金具12を構成する筒
金具24における第一の支持金具lO側の開口周縁部に
は、径方向一方向に対向する略四半周部分に位置して、
それぞれ、径方向内方に所定長さで延び出す内側当接部
26が、屈曲形成されている一方、該内側当接部26.
26の対向方向とは直交する方向に対向する略四半周部
分に位置して、それぞれ、斜め外方に所定長さで延び出
す外側当接部28が屈曲形成されている。そして、該筒
金具24の外側当接部28.28が、前記第一の支持金
具10に設けられた延出部13.13に対して、振動入
力方向に対向せしめられる相対的位置関係をもって、配
置せしめられているのである。In addition, at the opening peripheral portion of the cylindrical metal fitting 24 constituting the second support fitting 12 on the side of the first support metal fitting 10, located at approximately a quarter circumferential portion facing in one direction in the radial direction,
Each of the inner abutting portions 26 extending radially inward by a predetermined length is bent.
Outer abutting portions 28 are bent and extend diagonally outward by a predetermined length, respectively, at approximately quarter circumferential portions facing each other in a direction orthogonal to the opposing direction of the outer abutting portions 26 . Then, the outer contact portion 28.28 of the cylindrical metal fitting 24 has a relative positional relationship in which it is opposed to the extension portion 13.13 provided on the first support metal fitting 10 in the vibration input direction, It has been placed in place.
さらに、これら第一の支持金具10と第二の支持金具1
2との間に介装されて、それら筒金具10.12を弾性
的に連結するゴム弾性体30は、略中空円錐台形状を呈
している。そして、その小径側端面において、第一の支
持金具10の内側面に、またその大径側端面において、
第二の支持金具12を構成する筒金具24の開口側周縁
部に、それぞれ、加硫接着されることにより、それら第
一の支持金具10と筒金具24とを有する一体加硫成形
品として形成されているのである。なお、かかるゴム弾
性体30の軸方向中央部には、略テーバ円筒形状の補強
金具31が埋設されていることにより、該ゴム弾性体3
0の変形が規制され得るようになっている。Furthermore, these first support metal fittings 10 and second support metal fittings 1
A rubber elastic body 30, which is interposed between the cylindrical fittings 10 and 2 and elastically connects the cylindrical fittings 10 and 12, has a substantially hollow truncated conical shape. Then, on the small diameter side end surface, on the inner surface of the first support fitting 10, and on the large diameter side end surface,
By being vulcanized and bonded to the opening-side peripheral edge of the cylindrical metal fitting 24 constituting the second support metal fitting 12, an integral vulcanized molded product having the first support metal fitting 10 and the cylindrical metal fitting 24 is formed. It is being done. Note that a reinforcing metal fitting 31 having a substantially Taber cylindrical shape is embedded in the axial center of the rubber elastic body 30, so that the rubber elastic body 3
The deformation of 0 can be regulated.
また一方、このような構造とされたマウントの内部には
、第二の支持金具12を構成する底金具18と筒金具2
4とのかしめ部間において、その外周縁部を流体密に挟
持されることにより、弾性薄膜としてのダイヤフラム3
2が配設されている。On the other hand, inside the mount having such a structure, there are a bottom metal fitting 18 and a cylindrical metal fitting 2 that constitute the second support metal fitting 12.
The outer peripheral edge of the diaphragm 3 is fluid-tightly sandwiched between the caulked portions of the diaphragm 3 and the elastic thin film.
2 are arranged.
そして、該ダイヤフラム32によって、マウントの内部
が、第一の支持金具10側に位置する密閉された流体室
と、底金具18側に位置して、該ダイヤフラム32の膨
出変形を許容する空間34とに仕切られている。なお、
かかる空間34は、通孔36にて大気中に連通されてお
り、その内圧によるダイヤフラム32の変形阻害が防止
されている。The inside of the mount is formed by the diaphragm 32 into a sealed fluid chamber located on the first support fitting 10 side and a space 34 located on the bottom fitting 18 side that allows the diaphragm 32 to expand and deform. It is divided into two parts. In addition,
This space 34 is communicated with the atmosphere through a through hole 36, and the deformation of the diaphragm 32 is prevented from being inhibited by the internal pressure.
そして、上記流体室内には、筒金具24のかしめ部22
に対する底金具18のかしめ固定が、水やアルキレング
リコール、ポリアルキレングリコール、シリコーン油等
の、所定の非圧縮性流体中にて行なわれること等によっ
て、かかる所定の非圧縮性流体が封入されている。In the fluid chamber, a caulking portion 22 of the cylindrical metal fitting 24 is provided.
The bottom fitting 18 is caulked and fixed in a predetermined incompressible fluid such as water, alkylene glycol, polyalkylene glycol, silicone oil, etc., so that the predetermined incompressible fluid is enclosed. .
さ・らに、かかる流体室内には、全体として略円盤形状
を呈する仕切部材38が、前記振動入力方向に対して直
角な方向に配されており、それによって、かかる流体室
内が、該仕切部材3日を挟んで、第一の支持金具10側
に位置して、振動入力に際し、ゴム弾性体30の弾性変
形に基づいて、内圧変動が惹起される受圧室40と、ダ
イヤフラム32側に位置して、該ダイヤフラム32の変
形に基づいて、内圧変動が回避される平衡室42とに仕
切られているのである。Furthermore, within the fluid chamber, a partition member 38 having an approximately disk shape as a whole is disposed in a direction perpendicular to the vibration input direction, so that the inside of the fluid chamber is separated by the partition member 38. Three days apart, a pressure receiving chamber 40 is located on the first support fitting 10 side, where internal pressure fluctuations are caused based on the elastic deformation of the rubber elastic body 30 upon vibration input, and a pressure receiving chamber 40 is located on the diaphragm 32 side. Based on the deformation of the diaphragm 32, it is partitioned into an equilibrium chamber 42 in which internal pressure fluctuations are avoided.
ここにおいて、かかる仕切部材38の外周部分は、全体
として略円環板形状を呈すると共に、その内孔周縁部に
おいて、軸方向に所定高さで立ち上がる筒部44が一体
的に設けられてなる支持金具46によって構成されてい
る。そして、かかる支持金具46には、その筒部44に
おける突出端側の開口部に対して、略円板形状を呈する
可撓性膜としてのゴム弾性板48が、一体的に加硫接着
せしめられており、該ゴム弾性板48によって、該筒部
44の突出端側の開口が閉塞せしめられている。更にま
た、かかる支持金具46には、筒部44が突出する側と
は反対側の面上に、中央部に円形凸部50を有するハツ
ト形状の蓋金具52が重ね合わせられており、その円形
凸部50が、支持金具46の筒部44に対して気密に嵌
入されることによって、かかる筒部44内において、上
記ゴム弾性板48との間に、略円盤形状を呈する所定容
積の密閉された空気室54が画成されているのである。Here, the outer circumferential portion of the partition member 38 has a generally annular plate shape as a whole, and a support formed by integrally providing a cylindrical portion 44 rising at a predetermined height in the axial direction at the inner hole circumferential edge of the partition member 38. It is constituted by a metal fitting 46. A rubber elastic plate 48 as a flexible membrane having a substantially disk shape is integrally vulcanized and bonded to the opening on the protruding end side of the cylindrical portion 44 of the support fitting 46. The opening on the protruding end side of the cylindrical portion 44 is closed by the rubber elastic plate 48. Furthermore, on the support fitting 46, a hat-shaped lid fitting 52 having a circular convex portion 50 in the center is superimposed on the surface opposite to the side from which the cylindrical portion 44 protrudes. By fitting the convex portion 50 airtightly into the cylindrical portion 44 of the support fitting 46, a predetermined volume of a substantially disc-shaped sealed space is formed between the cylindrical portion 44 and the rubber elastic plate 48. An air chamber 54 is defined therein.
なお、このような仕切部材38にあっては、その内部に
形成される空気室54の気密性を確保すべく、第3図に
示されているように、ゴム弾性板48が、支持金具46
に加硫接着せしめられた一体加硫成形品として形成され
ていると共に、該支持金具46における筒部44の内周
面上には、所定厚さのシールゴム層57が一体的に設け
られ、そこに嵌入せしめられる前記蓋金具52の円形凸
部50との間におけるシール性の向上が図られている。In addition, in such a partition member 38, in order to ensure the airtightness of the air chamber 54 formed inside the partition member 38, the rubber elastic plate 48 is attached to the support metal fitting 46 as shown in FIG.
A sealing rubber layer 57 of a predetermined thickness is integrally provided on the inner circumferential surface of the cylindrical portion 44 of the support fitting 46. The sealing performance between the lid fitting 52 and the circular convex portion 50 that is fitted into the lid fitting 52 is improved.
また、かかる仕切部材38の外周部分には、支持金具4
6における筒部44の先端周縁部が径方向外方に屈曲さ
れることにより、外周面上に開口して周方向に延びる凹
溝56が形成せしめられている。Further, a supporting metal fitting 4 is provided on the outer peripheral portion of the partition member 38.
By bending the distal end peripheral edge of the cylindrical portion 44 at 6 radially outward, a groove 56 that opens on the outer circumferential surface and extends in the circumferential direction is formed.
そして、上述の如き構造とされた仕切部材38は、その
支持金具46および差金具52の外周縁部において、前
記ダイヤフラム32と共に、第二の支持金具12を構成
する底金具18と筒金具24とのかしめ部位において挟
持されることによって、そのゴム弾性板48が、受圧室
40内に露呈される状態で組み付けられている。そして
また、かかる仕切部材38の組付けによって、その凹溝
56の開口が筒金具24の内周面にて覆蓋されることに
より、そこに、周方向に所定長さで延びる、受圧室40
と平衡室42とを相互に連通ずるオリフィス通路58が
形成されている。The partition member 38 having the above-mentioned structure has the bottom metal fitting 18 and the cylindrical metal fitting 24, which constitute the second support fitting 12, together with the diaphragm 32, at the outer peripheral edge of the support fitting 46 and the differential fitting 52. The rubber elastic plate 48 is assembled in a state where it is exposed in the pressure receiving chamber 40 by being held at the caulked portion. Furthermore, by assembling the partition member 38, the opening of the groove 56 is covered with the inner circumferential surface of the cylindrical metal fitting 24, so that a pressure receiving chamber 40 is formed therein which extends for a predetermined length in the circumferential direction.
An orifice passageway 58 is formed that interconnects the balance chamber 42 and the balance chamber 42 .
すなわち、このような構造の仕切部材38にあっては、
受圧室40内の液圧が、そのゴム弾性板48の前面側に
対して直接に及ぼされることとなり、そこにおいてかか
るゴム弾性板48は、空気室54内の空気の圧縮/膨張
に基づいて、その変形が許容され得るところから、かか
る受圧室40内の液圧上昇が、該ゴム弾性体48の弾性
変形によって低減乃至は解消され得るのであり、また−
方、このゴム弾性板48の裏面側は、そのような弾性変
形時に、空気室54内の空気の圧縮に伴う空気圧を受け
ることとなるところから、その弾性変形量がかかる空気
圧によって規制されることとなるのである。That is, in the partition member 38 having such a structure,
The liquid pressure in the pressure receiving chamber 40 will be directly applied to the front side of the rubber elastic plate 48, and the rubber elastic plate 48 will act as Since the deformation is permissible, the rise in hydraulic pressure within the pressure receiving chamber 40 can be reduced or eliminated by the elastic deformation of the rubber elastic body 48, and -
On the other hand, since the back side of the rubber elastic plate 48 receives air pressure due to the compression of the air in the air chamber 54 during such elastic deformation, the amount of elastic deformation is regulated by the applied air pressure. It becomes.
それ故、かかる仕切部材38を備えたエンジンマウント
に対して、第一の支持金具10と第二の支持金具12と
の間に振動が入力された際、かかる入力振動が、エンジ
ンシェイクやバウンス等に相当する10Hz前後の低周
波大振幅振動である場合には、受圧室40内に生ぜしめ
られる内圧変動が大きく、ゴム弾性板48の弾性変形に
よっては吸収しきれないことから、該受圧室40と平衡
室42との間での、オリフィス通路58を通じての流体
の流動量が有効に確保され得るのであり、以てかかる流
体の共振作用に基づく高減衰効果が、有効に発揮され得
ることとなる。Therefore, when vibration is input between the first support metal fitting 10 and the second support metal fitting 12 to the engine mount including the partition member 38, the input vibration causes engine shake, bounce, etc. In the case of low-frequency, large-amplitude vibrations of around 10 Hz corresponding to the The amount of fluid flowing through the orifice passage 58 between the balance chamber 42 and the balance chamber 42 can be effectively ensured, and the high damping effect based on the resonance effect of the fluid can be effectively exhibited. .
また一方、かかる入力振動が、オリフィス通路58が実
質的に閉塞状態となる、高周波小振幅振動である場合に
は、受圧室40内に生ぜしめられる内圧変動が小さく、
ゴム弾性板48の弾性変形によって吸収され得ることか
ら、該受圧室40内の内圧上昇が回避されることとなり
、以てマウントの低動ばね化が有利に図られ得るのであ
る。なお、特に、かかるゴム弾性板48に作用する空気
圧は、空気室54内の容積に反比例することから、その
変形量が小さい場合には、柔らかいばね特性が有利に発
揮され得るのであり、それによってマウントの低動ばね
化が極めて効果的に達成され得るのである。On the other hand, if the input vibration is a high-frequency, small-amplitude vibration that substantially closes the orifice passage 58, the internal pressure fluctuations generated in the pressure receiving chamber 40 are small;
Since this can be absorbed by the elastic deformation of the rubber elastic plate 48, an increase in internal pressure within the pressure receiving chamber 40 is avoided, and the mount can advantageously have a low dynamic spring. In particular, since the air pressure acting on the rubber elastic plate 48 is inversely proportional to the volume inside the air chamber 54, when the amount of deformation is small, soft spring characteristics can be advantageously exhibited. This makes it possible to extremely effectively reduce the spring movement of the mount.
なお、上述の説明から明らかなように、本実施例におい
ては、仕切部材38を構成するゴム弾性板48、差金具
52およびそれら両部材間に画成された空気室54によ
って、液圧吸収機構が構成されている。As is clear from the above description, in this embodiment, the hydraulic pressure absorption mechanism is created by the rubber elastic plate 48, the metal fitting 52, and the air chamber 54 defined between these members, which constitute the partition member 38. is configured.
また、空気室54の容積は、上述の如く、高減衰特性が
要求される周波数域の振動入力時には、受圧室54内に
生ぜしめられる内圧変動を吸収してしまわない程度に、
そのゴム弾性板48の変形を阻止せしめ得る一方、低動
ばね特性が要求される周波数域の振動入力時には、その
ゴム弾性板48における、受圧室54内に惹起される内
圧上昇を充分に吸収し得るだけの変形を許容し得るよう
に、入力される振動の特性やゴム弾性板48の面積、弾
性率および受圧室40内の容積などを総合的に考慮して
設定されることとなる。In addition, as described above, the volume of the air chamber 54 is set to such an extent that it does not absorb internal pressure fluctuations generated within the pressure receiving chamber 54 when vibration is input in a frequency range that requires high damping characteristics.
While this can prevent deformation of the rubber elastic plate 48, when vibration is input in a frequency range that requires low dynamic spring characteristics, the rubber elastic plate 48 can sufficiently absorb the increase in internal pressure caused in the pressure receiving chamber 54. The setting is made by comprehensively considering the characteristics of the input vibration, the area of the rubber elastic plate 48, the elastic modulus, the volume inside the pressure receiving chamber 40, etc., so as to allow sufficient deformation.
ところで、本実施例におけるエンジンマウントにあって
は、更に、受圧室40内において、略有底円筒形状を呈
する傘金具60が、収容配置せしめられている。この傘
金具60は、小径部62と大径部64とからなる段付円
筒形状を呈しており、その小径部62側において、第一
の支持金具10の支持部14に対してかしめ固定される
ことによリ、第二の支持金具12側に向かって開口する
状態で配設されている。そして、かかる全金具60によ
り、受圧室40内が、該全金具60を挟んで、振動入力
方向両側に位置する二つの室に略二分されていると共に
、該全金具60における大径部64の外周面と受圧室4
0の内周面との間に、それらの分割室を相互に連通ずる
環状の狭窄部66が、形成されている。Incidentally, in the engine mount according to the present embodiment, an umbrella fitting 60 having a substantially bottomed cylindrical shape is further accommodated in the pressure receiving chamber 40 . This umbrella fitting 60 has a stepped cylindrical shape consisting of a small diameter part 62 and a large diameter part 64, and is caulked and fixed to the support part 14 of the first support fitting 10 on the small diameter part 62 side. Particularly, it is disposed in such a manner that it opens toward the second support fitting 12 side. The inside of the pressure receiving chamber 40 is approximately divided into two chambers located on both sides in the vibration input direction with the full metal fittings 60 in between, and the large diameter portion 64 of the full metal fittings 60 is divided into two chambers located on both sides in the vibration input direction. Outer surface and pressure receiving chamber 4
An annular narrowed portion 66 is formed between the inner circumferential surface of 0 and the divided chambers to communicate with each other.
また、かかる全金具60における大径部64の開口部に
は、外周縁部に取付リング70を、内周縁部にマスリン
グ6日を、それぞれ一体的に備えた円環板状の環状ゴム
72が、その取付リング70を大径部64内に圧入され
ることによって、取り付けられていると共に、該全金具
60の小径部62には、複数の通孔74が設けられてお
り、それによって、かかる全金具60の内部において、
該全金具60にて仕切られた上記二つの分割室を相互に
連通ずる流路が形成されている。Further, in the opening of the large diameter portion 64 of the full fitting 60, an annular plate-shaped annular rubber 72 is integrally provided with a mounting ring 70 on the outer peripheral edge and a mass ring 6 day on the inner peripheral edge. is attached by press-fitting the mounting ring 70 into the large diameter portion 64, and the small diameter portion 62 of the entire metal fitting 60 is provided with a plurality of through holes 74, thereby, Inside the metal fittings 60,
A flow path is formed that communicates the two divided chambers partitioned by the metal fittings 60 with each other.
すなわち、このような全金具60が受圧室40内に配さ
れていることにより、前記第−及び第二の支持金具10
.12間への振動入力に際し、かかる全金具60が受圧
室40内を振動入力方向に移動せしめられて、該全金具
60を挟んだ両側に形成された前記分割室間において、
前記狭窄部66および全金具60の内部を通じての流体
の流動が、それぞれ生ぜしめられることとなるのである
。That is, by disposing all the metal fittings 60 in the pressure receiving chamber 40, the first and second supporting metal fittings 10
.. When vibration is input to the space between 12 and 12, all the metal fittings 60 are moved in the vibration input direction within the pressure receiving chamber 40, and between the divided chambers formed on both sides of the all metal fittings 60,
Fluid flow is caused through the constriction 66 and the interior of the fitting 60, respectively.
そして、それによって、かかる狭窄部66内を流動せし
められる流体の共振作用と、全金具60の開口部に配さ
れたマスリング68のダンパー作用および該マスリング
68内を流動せしめられる流体の共振作用の相乗作用と
によって、それぞれ、所定の高周波数域の入力振動に対
する低動ばね効果が発揮され得ることとなるのである。As a result, the resonance effect of the fluid flowing through the narrowed portion 66, the damper effect of the mass ring 68 disposed at the opening of the metal fitting 60, and the resonance effect of the fluid flowing inside the mass ring 68. Due to the synergistic effect of the above, a low dynamic spring effect can be exerted against input vibrations in a predetermined high frequency range.
なお、特に、本実施例においては、それら狭窄部66内
における流体の共振作用による低動ばね効果と、マスリ
ング68のダンパー作用および該マスリング6日内にお
ける流体の共振作用の相乗作用による低動ばね効果とが
、それぞれ、前述の如き液圧吸収機構による低動ばね効
果が発揮され得る周波数域よりも、更に高周波数側で且
つ互いに異なる周波数域に設定されることとなる。In particular, in this embodiment, the low motion spring effect due to the resonance effect of the fluid within the narrowed portion 66, the damper effect of the mass ring 68, and the synergistic effect of the resonance effect of the fluid within 6 days of the mass ring reduce the low motion. The spring effects are respectively set in frequency ranges higher than the frequency range in which the low motion spring effect due to the hydraulic pressure absorption mechanism as described above can be exhibited, and in different frequency ranges from each other.
更にまた、本実施例におけるエンジンマウントにあって
は、第二の支持金具12を構成する筒金具24の外側当
接部28が、第一の支持金具lOの延出部13に対して
、振動入力方向に所定距離を隔てて対向配置されており
、該延出部13に対する当接によって、振動入力時にお
けるバウンド方向の過大変位が規制され得るようになっ
ていると共に、前記全金具60の大径部64が、筒金具
24の内側当接部26に対して、振動入力方向に所定距
離を隔てて対向配置されており、該内側当接部26に対
する当接によって、振動入力時におけるリバウンド方向
の過大変位が規制され得るようになっている。Furthermore, in the engine mount according to the present embodiment, the outer contact portion 28 of the cylindrical metal fitting 24 constituting the second support metal fitting 12 is able to resist vibrations with respect to the extending portion 13 of the first support metal fitting IO. They are arranged facing each other at a predetermined distance in the input direction, and by contacting the extension portion 13, excessive displacement in the bounding direction at the time of vibration input can be restricted, and all the metal fittings 60 The large diameter portion 64 is arranged to face the inner abutting portion 26 of the cylindrical metal fitting 24 at a predetermined distance in the vibration input direction, and by contacting the inner abutting portion 26, a rebound occurs when vibration is input. Excessive displacements in direction can be regulated.
従って、上述の如き構造とされたエンジンマウントにあ
っては、オリフィス通路58内を流動せしめられる流体
の共振作用によって、低周波数域の振動入力時における
高減衰効果が発揮され得ると共に、該オリフィス通路5
8がチューニングされた周波数よりも高周波数域の振動
入力時には、液圧吸収機構を構成するゴム弾性板48の
弾性変形に基づいて、低動ばね効果が発揮され得るので
あり、以て広い周波数域に亘って良好なる防振特性が発
揮され得ることとなるのである。Therefore, in the engine mount having the above-described structure, due to the resonance effect of the fluid flowing in the orifice passage 58, a high damping effect can be exhibited when vibration is input in a low frequency range, and the orifice passage 5
When vibration is input in a frequency range higher than the frequency to which 8 is tuned, a low dynamic spring effect can be exerted based on the elastic deformation of the rubber elastic plate 48 constituting the hydraulic pressure absorption mechanism, and thus a wide frequency range can be achieved. This means that good vibration damping characteristics can be exhibited over the entire period.
そして、特に、かかる液圧吸収機構にあっては、ゴム弾
性板48と蓋金具52との間に空気室54を画成せしめ
てなる極めて簡略な構造を有していることから、マウン
ト装置に対する、上述の如き優れた防振特性の付与が、
良好なる製作性と低コスト性とをもって、有利に実現さ
れ得るのである。In particular, this liquid pressure absorption mechanism has an extremely simple structure in which an air chamber 54 is defined between the rubber elastic plate 48 and the lid fitting 52, so that , imparting the excellent anti-vibration properties as described above,
This can be advantageously realized with good manufacturability and low cost.
また、かかる液圧吸収機構にあっては、ゴム弾性板48
の変形量の規制が、その背面に及ぼされる空気室54内
の気圧の上昇によって為されることから、該ゴム弾性板
48における過大な変形が完全に防止され得て、充分な
耐久性が発揮され得ると共に、その変形規制時に打音等
が生じるようなこともないのである。In addition, in such a hydraulic pressure absorption mechanism, the rubber elastic plate 48
Since the amount of deformation of the rubber elastic plate 48 is regulated by increasing the air pressure within the air chamber 54 on the back surface thereof, excessive deformation of the rubber elastic plate 48 can be completely prevented and sufficient durability can be achieved. At the same time, there is no occurrence of tapping sounds or the like when the deformation is restricted.
さらに、本実施例におけるエンジンマウントにあっては
、かかる液圧吸収機構が、受圧室40と平衡室42とを
仕切る仕切壁部材38として構成されているところから
、部品点数の増加が有効に抑えられ得るといった利点を
も有しているのである。Furthermore, in the engine mount of this embodiment, since the hydraulic pressure absorption mechanism is configured as a partition wall member 38 that partitions the pressure receiving chamber 40 and the equilibrium chamber 42, an increase in the number of parts can be effectively suppressed. It also has the advantage of being able to be used.
更にまた、本実施例におけるエンジンマウントにあって
は、受圧室40内を二つの分割室に仕切る全金具60を
有しており、それら分割室間に生ぜしめられる狭窄部6
6を通じての流体の流動およびマスリング6日の内孔を
通じての流体の流動によっても、それぞれ、高周波数域
の振動入力時におけるマウントの低動ばね化が図られ得
るところから、より一層優れた防振効果が発揮され得る
こととなるのである。Furthermore, the engine mount in this embodiment has a metal fitting 60 that partitions the inside of the pressure receiving chamber 40 into two divided chambers, and a narrow portion 6 created between the divided chambers.
The fluid flow through the mass ring 6 and the fluid flow through the inner hole of the mass ring 6 can also reduce the spring movement of the mount when vibration is input in a high frequency range, resulting in even better protection. This means that a vibration effect can be exerted.
以上、本発明の一実施例について詳述してきたが、これ
は文字通りの例示であって、本発明は、かかる具体例に
のみ限定して解釈されるものではない。Although one embodiment of the present invention has been described in detail above, this is a literal illustration, and the present invention is not to be construed as being limited only to this specific example.
例えば、液圧吸収機構の具体的構造は、前記実施例のも
のに限定解釈されるものでは決してなく、受圧室(40
)内に露呈して、その液圧が及ぼされる部位の少なくと
も一部に可撓性膜を備えると共に、該可撓性膜の背後に
所定容積の密閉された空気室を備えてなる構造のもので
あれば良く、具体的には、筒金具24の内周面部分に液
圧吸収機構を配することも可能であり、更には、全体が
ゴム弾性体にて形成されてなる中空部材を用い、該中空
部材を受圧室(40)内に配することによっても、液圧
吸収機構を構成することが可能である。For example, the specific structure of the hydraulic pressure absorption mechanism is by no means limited to that of the embodiment described above, and the pressure receiving chamber (40
) A structure comprising a flexible membrane on at least a part of the area exposed within the liquid pressure and to which the liquid pressure is applied, and a sealed air chamber with a predetermined volume behind the flexible membrane. Specifically, it is possible to arrange a hydraulic pressure absorption mechanism on the inner circumferential surface of the cylindrical metal fitting 24, and furthermore, it is possible to use a hollow member formed entirely of a rubber elastic body. It is also possible to configure a hydraulic pressure absorption mechanism by arranging the hollow member within the pressure receiving chamber (40).
また、本発明に係る流体封入式マウント装置においては
、受圧室(40)と平衡室(42)とが、仕切部材(3
8)を隔てて対向位置せしめられていることは、必ずし
も必要ではなく、それら受圧室と平衡室とを、隔たった
位置に設置することも可能である。Further, in the fluid-filled mount device according to the present invention, the pressure receiving chamber (40) and the equilibrium chamber (42) are separated from each other by the partition member (3).
It is not necessarily necessary that the pressure receiving chamber and the equilibrium chamber be located opposite each other with the space 8) in between, and it is also possible to install the pressure receiving chamber and the equilibrium chamber at separate positions.
さらに、それら受圧室(40)と平衡室(42)とを連
通ずるオリフレス通路(58)としても、その具体的な
構造は限定されるものではなく、目的とするマウント装
置に要求される防振特性等に応じて、その長さや断面積
を含む形態は、適宜変更されるべきものである。Furthermore, the specific structure of the ori-free passageway (58) that communicates the pressure receiving chamber (40) and the equilibrium chamber (42) is not limited, and the vibration isolation required for the intended mounting device is not limited. The shape, including its length and cross-sectional area, should be changed as appropriate depending on the characteristics.
また、本発明では、受圧室(40)内に配された全金具
(60)を必須の要件とするものでなく、かかる全金具
(60)は、要求される防振特性に応じて任意に設定さ
れるものである。Further, in the present invention, all the metal fittings (60) arranged in the pressure receiving chamber (40) are not an essential requirement, and all the metal fittings (60) can be optionally provided depending on the required vibration-proofing characteristics. It is set.
加えて、前記実施例では、本発明を自動車用エンジンマ
ウントに適用したものの一例を示したが、本発明は、そ
の他、各種機械装置等のマウント装置に対しても、有利
に適用され得るものであることは、勿論である。In addition, although the embodiment described above shows an example in which the present invention is applied to an automobile engine mount, the present invention can also be advantageously applied to mounting devices for various other mechanical devices. Of course there is.
その他、−々列挙はしないが、本発明は、当業者の知識
に基づいて種々なる変更、修正、改良等を加えた態様に
おいて実施され得るものであり、またそのような実施態
様が、本発明の趣旨を逸脱しない限り、何れも本発明の
範囲内に含まれるものであることは、言うまでもないと
ころである。In addition, although not listed, the present invention can be implemented in embodiments with various changes, modifications, improvements, etc. added based on the knowledge of those skilled in the art, and such embodiments are not limited to the present invention. It goes without saying that any of these are included within the scope of the present invention as long as they do not depart from the spirit of the invention.
(発明の効果)
上述の説明から明らかなように、本発明に従う構造とさ
れた流体封入式マウント装置にあっては、低周波大振幅
の振動入力に際し、その液圧吸収機構を構成する可撓性
膜の変形が、該可撓性膜の背面に及ぼされる空気室内の
圧力にて規制されることにより、該液圧吸収機構の機能
が、実質上、阻止せしめられて、受圧室内の内圧変動が
有効に生ぜしめられ得ることから、オリフィス通路内を
流動せしめられる流体の共振作用による防振効果が良好
に発揮され得るのであり、また一方、高周波小振幅の振
動入力に際しては、空気室の容積変化によって許容され
る可撓性膜の弾性変形に基づいて、かかる液圧吸収機構
が機能せしめられることにより、受圧室内の内圧上昇が
解消されて、マウント特性の低動ばね化が、効果的に達
成され得ることとなるのである。(Effects of the Invention) As is clear from the above description, in the fluid-filled mount device structured according to the present invention, when a low frequency and large amplitude vibration is input, the flexible As the deformation of the flexible membrane is regulated by the pressure within the air chamber applied to the back surface of the flexible membrane, the function of the hydraulic pressure absorption mechanism is substantially inhibited, and internal pressure fluctuations within the pressure chamber are prevented. can be effectively generated, so that the vibration damping effect due to the resonance effect of the fluid flowing in the orifice passage can be well exhibited.On the other hand, when high frequency and small amplitude vibration input is applied, Based on the elastic deformation of the flexible membrane allowed by the change, the hydraulic pressure absorption mechanism is activated, eliminating the increase in internal pressure in the pressure receiving chamber, and effectively reducing the dynamic spring characteristics of the mount. This is something that can be achieved.
また、かかる液圧吸収機構にあっては、受圧室内の液圧
が及ぼされる可撓性膜の背後に、所定容積の空気室を形
成せしめてなる簡単な構造によって構成され得ることか
ら、上述の如き優れた防振特性を有するマウント装置が
、良好なる製造性と低コスト性とをもって、有利に提供
され得るのである。In addition, such a liquid pressure absorption mechanism can be constructed with a simple structure in which an air chamber of a predetermined volume is formed behind a flexible membrane to which the liquid pressure in the pressure receiving chamber is applied. A mounting device having such excellent vibration damping properties can be advantageously provided with good manufacturability and low cost.
更にまた、かかる液圧吸収機構においては、ゴム弾性板
48の変形規制が、空気の圧力によって為されるところ
から、その過大な変形が有利に防止されて、充分な耐久
性が発揮され得ると共に、その変形規制時に打音等が生
じるようなこともないのである。Furthermore, in such a hydraulic pressure absorption mechanism, since the deformation of the rubber elastic plate 48 is restricted by air pressure, excessive deformation thereof is advantageously prevented, and sufficient durability can be exhibited. , there is no occurrence of tapping sounds or the like when the deformation is restricted.
第1図は、本発明に従う構造とされたエンジンマウント
の一興体例を示す縦断面説明図であって、第2図におけ
るI−1断面に相当する図であり、第2図は、かかるエ
ンジンマウントの平面図である。また、第3図は、第1
図に示されているエンジンマウントを構成する仕切部材
の構造を説明するための分解説明図である。更に、第4
図は、第1図に示されているエンジンマウントの装着状
態を示す、第1図に対応する縦断面図である。
52:型金具
58ニオリフイス通路
:空気室FIG. 1 is a vertical cross-sectional explanatory view showing an example of an integrated engine mount having a structure according to the present invention, and is a view corresponding to the I-1 cross section in FIG. FIG. Also, Figure 3 shows the first
FIG. 3 is an exploded explanatory view for explaining the structure of a partition member that constitutes the engine mount shown in the figure. Furthermore, the fourth
1 is a longitudinal sectional view corresponding to FIG. 1, showing the mounted state of the engine mount shown in FIG. 1. 52: Mold fitting 58 Niorifice passage: Air chamber
Claims (1)
二の支持金具とを、ゴム弾性体にて一体的に連結せしめ
る一方、それら第一の支持金具と第二の支持金具との間
に、それぞれ、所定の非圧縮性流体が封入された、防振
すべき振動が入力される受圧室と、少なくとも一部が弾
性薄膜にて画成された容積可変の平衡室とを形成すると
共に、それら受圧室と平衡室とを相互に連通するオリフ
ィス通路を設けてなる流体封入式マウント装置において
、 前記受圧室内の液圧が及ぼされる部位の少なくとも一部
に可撓性膜を有すると共に、該可撓性膜の背後に所定容
積の密閉された空気室を備え、かかる受圧室内に内圧変
動が生ぜしめられた際、該空気室の容積変化を伴う該可
撓性膜の弾性変形が生ぜしめられる液圧吸収機構を、前
記受圧室内に配したことを特徴とする流体封入式マウン
ト装置。[Scope of Claims] A first support metal fitting and a second support metal fitting arranged at a predetermined distance from each other are integrally connected by a rubber elastic body, while the first support metal fitting and the second support metal fitting are integrally connected by a rubber elastic body. A pressure-receiving chamber filled with a predetermined incompressible fluid and into which vibrations to be damped are input, and a variable-volume equilibrium at least partially defined by an elastic thin film are provided between the support fittings of the In the fluid-filled mounting device, the fluid-filled mount device is provided with an orifice passage that forms a chamber and communicates the pressure receiving chamber and the equilibrium chamber with each other, wherein at least a portion of the portion to which the liquid pressure is applied in the pressure receiving chamber is flexible. The flexible membrane has a membrane and a sealed air chamber of a predetermined volume behind the flexible membrane, and when an internal pressure fluctuation occurs in the pressure receiving chamber, the flexible membrane changes in volume of the air chamber. A fluid-filled mount device characterized in that a fluid pressure absorption mechanism that causes elastic deformation is disposed within the pressure receiving chamber.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP27991288A JPH02129426A (en) | 1988-11-05 | 1988-11-05 | Fluid enclosed type mount device |
DE19893936720 DE3936720A1 (en) | 1988-11-05 | 1989-11-03 | Elastic mounting with hydraulic damping - incorporating pneumatic cushion to extend damping range |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP27991288A JPH02129426A (en) | 1988-11-05 | 1988-11-05 | Fluid enclosed type mount device |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH02129426A true JPH02129426A (en) | 1990-05-17 |
Family
ID=17617644
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP27991288A Pending JPH02129426A (en) | 1988-11-05 | 1988-11-05 | Fluid enclosed type mount device |
Country Status (2)
Country | Link |
---|---|
JP (1) | JPH02129426A (en) |
DE (1) | DE3936720A1 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03107636A (en) * | 1989-09-22 | 1991-05-08 | Bridgestone Corp | Antirattler |
EP0635656A1 (en) * | 1993-07-06 | 1995-01-25 | Yamashita Rubber Kabushiki Kaisha | Sealed liquid vibration damping apparatus |
JP2014009814A (en) * | 2012-06-28 | 2014-01-20 | Hyundai Motor Company Co Ltd | Fluid-filled mount |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0510373A (en) * | 1991-07-08 | 1993-01-19 | Bridgestone Corp | Vibration-proof device |
JP3449012B2 (en) * | 1995-02-06 | 2003-09-22 | 東海ゴム工業株式会社 | Fluid-filled mounting device |
US7111705B2 (en) * | 2004-02-02 | 2006-09-26 | Kurashiki Kako Co., Ltd. | Vibration isolating mount device |
DE102016101829A1 (en) * | 2016-02-02 | 2017-08-03 | Vibracoustic Gmbh | Hydraulic bearing with switchable oscillating absorber channel |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS612940A (en) * | 1984-06-07 | 1986-01-08 | メツツエラー、ゲゼルシヤフト、ミツト、ベシユレンクテル、ハフツング | Double chamber engine mount |
JPS6262033A (en) * | 1985-09-07 | 1987-03-18 | Bridgestone Corp | Vibro-isolating device |
JPS6315345B2 (en) * | 1983-08-29 | 1988-04-04 | Sekisui Chemical Co Ltd |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3447950A1 (en) * | 1984-06-07 | 1985-12-12 | Audi AG, 8070 Ingolstadt | Hydraulic engine mount |
JPS6165932A (en) * | 1984-09-05 | 1986-04-04 | Bridgestone Corp | Anti-vibration device |
DE3443618A1 (en) * | 1984-11-29 | 1986-06-05 | Metzeler Kautschuk GmbH, 8000 München | ENGINE MOUNT WITH HYDRAULIC DAMPING |
FR2577641B1 (en) * | 1985-02-15 | 1989-05-05 | Hutchinson | IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS |
-
1988
- 1988-11-05 JP JP27991288A patent/JPH02129426A/en active Pending
-
1989
- 1989-11-03 DE DE19893936720 patent/DE3936720A1/en not_active Ceased
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6315345B2 (en) * | 1983-08-29 | 1988-04-04 | Sekisui Chemical Co Ltd | |
JPS612940A (en) * | 1984-06-07 | 1986-01-08 | メツツエラー、ゲゼルシヤフト、ミツト、ベシユレンクテル、ハフツング | Double chamber engine mount |
JPS6262033A (en) * | 1985-09-07 | 1987-03-18 | Bridgestone Corp | Vibro-isolating device |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH03107636A (en) * | 1989-09-22 | 1991-05-08 | Bridgestone Corp | Antirattler |
EP0635656A1 (en) * | 1993-07-06 | 1995-01-25 | Yamashita Rubber Kabushiki Kaisha | Sealed liquid vibration damping apparatus |
JP2014009814A (en) * | 2012-06-28 | 2014-01-20 | Hyundai Motor Company Co Ltd | Fluid-filled mount |
Also Published As
Publication number | Publication date |
---|---|
DE3936720A1 (en) | 1990-05-31 |
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