JPS62270842A - Mounting device for power unit - Google Patents
Mounting device for power unitInfo
- Publication number
- JPS62270842A JPS62270842A JP11253286A JP11253286A JPS62270842A JP S62270842 A JPS62270842 A JP S62270842A JP 11253286 A JP11253286 A JP 11253286A JP 11253286 A JP11253286 A JP 11253286A JP S62270842 A JPS62270842 A JP S62270842A
- Authority
- JP
- Japan
- Prior art keywords
- orifice
- fluid
- partition plate
- support member
- 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.)
- Pending
Links
- 239000012530 fluid Substances 0.000 claims abstract description 58
- 238000005192 partition Methods 0.000 claims abstract description 31
- 239000012528 membrane Substances 0.000 claims description 14
- 238000000638 solvent extraction Methods 0.000 claims description 2
- 238000009434 installation Methods 0.000 claims 1
- 238000000034 method Methods 0.000 abstract 1
- 238000006073 displacement reaction Methods 0.000 description 7
- 230000005540 biological transmission Effects 0.000 description 5
- 238000013016 damping Methods 0.000 description 3
- 230000004323 axial length Effects 0.000 description 2
- 210000005069 ears Anatomy 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 101800001092 Protein 3B Proteins 0.000 description 1
- 101800003106 VPg Proteins 0.000 description 1
- 101800001133 Viral protein genome-linked Proteins 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000002401 inhibitory effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
- F16F13/04—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper
- F16F13/06—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper
- F16F13/08—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a plastics spring and a damper, e.g. a friction damper the damper being a fluid damper, e.g. the plastics spring not forming a part of the wall of the fluid chamber of the damper the plastics spring forming at least a part of the wall of the fluid chamber of the damper
- F16F13/10—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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
- Combined Devices Of Dampers And Springs (AREA)
Abstract
Description
【発明の詳細な説明】
３、発明の詳細な説明
（産業上の利用分野）
本発明は、例えばエンジンのパワーユニットを車両の車
体に対して弾性的にマウンティングするための流体封入
マウンティング装置に関する。Detailed Description of the Invention 3. Detailed Description of the Invention (Field of Industrial Application) The present invention relates to a fluid-filled mounting device for elastically mounting, for example, a power unit of an engine to the body of a vehicle.
（従来技術）
従来、この種のマウンティング装置として、例えば実開
昭５９−１９６７４６号公報に開示されているものが知
られている。このマウンティング装置は、エンジンに取
付けられる第１の支持部材と、このエンジンをマウント
する基台に取付けられる第２の支持部材とを連結する筒
状の弥生体を備え、この弾性体の内部に、一端が第１の
支持部材により閉塞され、他端が弾性膜（ダイアフラム
）により閉塞されて密閉された室が形成され、この室内
に流体が封入された構成を存する。そして上記室は、１
枚の仕切板によって、上記第１の支持部材と上記仕切板
との間の第１の流体室と、上記仕切板と上記弾性膜との
間の第２の流体室とに仕切られ、さらに、上記仕切板に
上記第１および第２の流体室間を連通ずるオリフィスが
設けられており、このオリフィスを通る流体の移動によ
って振動を減衰させる機能を有する。(Prior Art) Conventionally, as this type of mounting device, one disclosed in, for example, Japanese Unexamined Utility Model Publication No. 59-196746 is known. This mounting device includes a cylindrical support member that connects a first support member attached to the engine and a second support member attached to a base on which the engine is mounted, and inside this elastic body, One end is closed by the first support member and the other end is closed by an elastic membrane (diaphragm) to form a sealed chamber, and a fluid is sealed in this chamber. And the above room is 1
partitioned into a first fluid chamber between the first support member and the partition plate and a second fluid chamber between the partition plate and the elastic membrane, and The partition plate is provided with an orifice that communicates between the first and second fluid chambers, and has a function of damping vibrations by moving fluid through the orifice.
ところで、上記構成においては、オリフィスの断面積、
長さおよび流体の密度によって定まる上記オリフィスに
おける流体の共振周波数を、例えば１０Ｈｚ〜１５Ｈｚ
で生しる「シェイク」と呼ばれるエンジンの振動の周波
数に合致するように設定した場合、その周波数付近にお
ける振動伝達率が低下するから、これにより振動は吸収
されるが、単一のオリフィスによっては、そのオリフィ
スの断面積および長さに応した一義的なダンピング特性
しか得られないため−１低い周波数で発生するエンジン
シェイクと、それよりも高い周波数帯域で発生するこも
り音との双方を低減させることは不可能であった。そこ
で前述の公報においては、径の異なる２個のオリフィス
を１枚の仕切板に設けて２つの周波数帯域において振動
伝達率を下げるように意図している。By the way, in the above configuration, the cross-sectional area of the orifice,
The resonant frequency of the fluid in the orifice determined by the length and density of the fluid is set to, for example, 10 Hz to 15 Hz.
If the setting is set to match the frequency of the engine vibration called "shake" generated by the Since only unique damping characteristics can be obtained depending on the cross-sectional area and length of the orifice, -1 reduces both engine shake that occurs at low frequencies and muffled noise that occurs at higher frequency bands. That was impossible. Therefore, in the above-mentioned publication, two orifices with different diameters are provided on one partition plate to reduce the vibration transmission rate in two frequency bands.
しかしながら、２個のオリフィスが１枚の仕切板に設け
られている場合、共振周波数の高い方のオリフィス、す
なわち断面積の大きいオリフィスは、低い周波数におい
ては単に連通状態になるため、これが共振周波数の低い
方のオリフィスによる低い周波数におけるダンピング効
果を阻害する欠点があった。However, when two orifices are provided on one partition plate, the orifice with a higher resonant frequency, that is, the orifice with a larger cross-sectional area, simply communicates with each other at lower frequencies; This had the disadvantage of inhibiting the damping effect at low frequencies due to the lower orifice.
（発明の目的）
上記事情に鑑みて、本発明は２つの異なる周波数帯域に
おいて共振伝達率を効果的に低下させることができるパ
ワーユニットのマウンティング装置を提供することを目
的とする。(Object of the Invention) In view of the above circumstances, an object of the present invention is to provide a mounting device for a power unit that can effectively reduce the resonance transmission rate in two different frequency bands.
（発明の構成）
本発明によるマウンティング装置においては、パワーユ
ニットに取付けられる第１の支持部材と、パワーユニッ
トをマウントする基台に取付けられる第２の支持部材と
を連結する弾性体を備え、この弾性体の内部に形成され
る空間の一端を弾性膜で閉塞して密閉された空を形成し
た構成において、上記室を第１および第２の仕切板で仕
切ることにより、第１の支持部材側の第１の流体室と、
中間の第２の流体室と、前記弾性膜側の第３の流体室と
を直列に形成し、上記第１の仕切板に第１および第２の
流体室間を連通ずる第１のオリフィスを設け、かつ、上
記第２の仕切板に第２および第３の流体室を連通ずる第
２のオリフィスを設けるとともに、この第２のオリフィ
スにおける流体の共振周波を、第１のオリフィスにおけ
る流体の共振周波数よりも裔く設定したことを特徴とす
る。(Structure of the Invention) A mounting device according to the present invention includes an elastic body that connects a first support member attached to a power unit and a second support member attached to a base on which the power unit is mounted, and the elastic body In a configuration in which one end of a space formed inside the chamber is closed with an elastic membrane to form a sealed cavity, by partitioning the chamber with first and second partition plates, the first support member side 1 fluid chamber;
An intermediate second fluid chamber and a third fluid chamber on the elastic membrane side are formed in series, and a first orifice communicating between the first and second fluid chambers is provided in the first partition plate. and a second orifice communicating the second and third fluid chambers is provided in the second partition plate, and the resonance frequency of the fluid in the second orifice is set to the resonance frequency of the fluid in the first orifice. It is characterized by being set more closely than the frequency.
（発明の効果）
本発明によれば、第１のオリフィスの共振周波数付近の
低い周波数において、流体は第２のオリフィスを通って
第２、第３の流体室間を抵抗なく流れるから第２の仕切
板は存在しない場合と等価になり、第１のオリフィスの
みが機能し、また、第２のオリフィスの共振周波数付近
の高い周波数においては、第１のオリフィスは目詰まり
状態となり、第２のオリフィスのみが機能するから、２
つの異なる周波数帯域において振動伝達率を低下させる
ことができ、エンジンシェイクとこもり音との双方を効
果的に減衰させることができる。また、本発明において
は、高い方の周波数で共振する第２のオリフィスに連通
ずる第３の流体室の室壁の一部が弾性膜で構成されてい
るから、上記２つの共振周波数の間の周波数帯域におけ
る振動伝達率を低くすることができ、したがって耳を圧
迫する低周波こもり音を減衰させるのに特にを効である
。(Effects of the Invention) According to the present invention, at a low frequency near the resonance frequency of the first orifice, the fluid flows between the second and third fluid chambers through the second orifice without resistance. This is equivalent to the case where the partition plate is not present, and only the first orifice functions, and at high frequencies near the resonant frequency of the second orifice, the first orifice becomes clogged and the second orifice Since only 2
The vibration transmission rate can be reduced in two different frequency bands, and both engine shake and muffled noise can be effectively damped. Furthermore, in the present invention, since a part of the chamber wall of the third fluid chamber communicating with the second orifice that resonates at a higher frequency is constituted by an elastic membrane, It can reduce the vibration transmission rate in the frequency band, and is therefore particularly effective in attenuating low-frequency muffled sounds that press on the ears.
（実 施 例）
以下図面を参照して本発明の一実施例について詳細に説
明する。(Example) An example of the present invention will be described in detail below with reference to the drawings.
第１図において、流体封入マウント１は、エンジンに取
付けられるボルト２を備えた上部の第１支持部材３と、
エンジンをマウントする基台としての車体に取付けられ
る孔４を備えた下部の第２支持部材５と、これら上下の
支持部材３．５を連結する上下に分割された筒状の弾性
体６．７とを有する。上方の第１弾性体６は截頭円雄状
に形成され、その上端面に第１支持部材３が固着されて
いる。第１弾性体６の下端面と、その下方の弾性体７の
上端面とは第１仕切板８を介して固着されて、第１支持
部材３と第１仕切板８との間に第１弾性体６で囲まれた
第１流体室９が形成されている。また、下方の第２弾性
体７の下端面には第２支持部材５が固着されているが、
第２支持部材５には第２仕切板１０が一体に形成されて
、第１仕切板８と第２仕切板１０との間に第２弾性体７
で囲まれた第２流体室１１が形成されている。さらに、
第２仕切板１０の下面には、弾性膜１２が、この第２仕
切板１０との間で第３流体室１３を形成するように固着
され、上記弾性膜１２の下方を覆ってカップ状の保護部
材１４が取付けられている。In FIG. 1, the fluid-filled mount 1 includes an upper first support member 3 with bolts 2 for attachment to the engine;
A lower second support member 5 with a hole 4 that is attached to the vehicle body as a base for mounting the engine, and a cylindrical elastic body 6.7 that is divided into upper and lower parts and connects these upper and lower support members 3.5. and has. The upper first elastic body 6 is formed into a truncated male shape, and the first support member 3 is fixed to its upper end surface. The lower end surface of the first elastic body 6 and the upper end surface of the elastic body 7 below the first elastic body 6 are fixed to each other via the first partition plate 8. A first fluid chamber 9 surrounded by an elastic body 6 is formed. Further, a second support member 5 is fixed to the lower end surface of the second elastic body 7 located below.
A second partition plate 10 is integrally formed on the second support member 5, and a second elastic body 7 is provided between the first partition plate 8 and the second partition plate 10.
A second fluid chamber 11 is formed surrounded by. moreover,
An elastic membrane 12 is fixed to the lower surface of the second partition plate 10 so as to form a third fluid chamber 13 with the second partition plate 10, and covers the lower part of the elastic membrane 12 to form a cup-shaped A protection member 14 is attached.
上方の第１仕切板８には第１および第２流体室９．１１
間を連通ずる第１オリフイス１５が設けられ、また下方
の第２仕切板１０には第２および第３流体室１１．１３
間を連通ずる第２オリフイス１６が設けられているが、
第１オリフイス１５は小径でかつ軸長が長く形成され、
第２オリフイス１６は第１オリフイス１５に比較して大
径でかつその軸長が短く形成されている。したがって、
第１オリフイス１５における液体の共振周波数ｆ１は低
く、第２オリフイス１６における流体の共振周波数ｆ２
は高くなる。なお、弾性膜１２と保護部材１４との間に
は空気室１７が形成されるが、この空気室１７は、保護
部材１４に透孔を形成して外部と連通してもよい。The upper first partition plate 8 has first and second fluid chambers 9.11.
A first orifice 15 is provided to communicate between the fluid chambers 11 and 13.
A second orifice 16 is provided to communicate between the
The first orifice 15 is formed with a small diameter and a long shaft length,
The second orifice 16 is formed to have a larger diameter and a shorter axial length than the first orifice 15. therefore,
The resonance frequency f1 of the liquid in the first orifice 15 is low, and the resonance frequency f2 of the fluid in the second orifice 16 is low.
becomes higher. Note that an air chamber 17 is formed between the elastic membrane 12 and the protection member 14, but this air chamber 17 may be communicated with the outside by forming a through hole in the protection member 14.
以上が本発明の一実施例の構成であるが、上記構成にお
いて、第２図に示すように第１オリフイス１５における
流体の共振周波数ｒ１はエンジンシェイクの発生周波数
１０Ｈｚ〜１５Ｈｚに設定され、かつ第２オリフイス１
６における流体の共振周波数ｆ２は、こもり音が発生す
る周波数帯域ｒ−〜ｒｂ （８０〜２００Ｈｚ ）よ
りもやや高い周波数に設定されている。第２オリフイス
１６は第１オリフイス１５に比較して径が大きく、かつ
その軸長が短いため、周波数ｒ１の付近では、流体は第
２オリフイス°１６を通って第２および第３流体室１１
．１３間を抵抗なく流動し、したがって第２仕切板１０
が存在しない場合と等価になり、第１オリフイス１５に
おける液体の周波数ｒ１での共振によって、エンジンシ
ェイクの発生が防止される。The above is the configuration of an embodiment of the present invention. In the above configuration, as shown in FIG. 2 orifice 1
The resonant frequency f2 of the fluid in No. 6 is set to a slightly higher frequency than the frequency band r- to rb (80 to 200 Hz) in which muffled sounds occur. Since the second orifice 16 has a larger diameter and a shorter axial length than the first orifice 15, near the frequency r1, the fluid passes through the second orifice 16 and enters the second and third fluid chambers 11.
．． 13 without resistance, and therefore the second partition plate 10
This is equivalent to the case where no .
一方、高い周波数ｒ２においては、径の小さく軸長の長
い第１オリフイス１５は目詰まり状態となるから、この
第１オリフイス１５を閉塞する場合と等価になり、第２
オリフイス１６における液体の周波数ｆ２での共振によ
って、こもり音の発生が防止される。さらに、第１図の
構成においては、弾性膜１２が、共振周波数ｒ２を有す
る第２オリフイス１６に連通ずる第３流体室１３の室壁
の一部を構成するように設けられているから、周波数ｆ
１とｒ２との間の部分（第２図に１点鎖線と比較して示
されている部分）の振動伝達率を下げることができ、し
たがって耳を圧迫する低周波こもり音を減衰させること
もできる。On the other hand, at high frequency r2, the first orifice 15 with a small diameter and long axis becomes clogged, so this is equivalent to blocking this first orifice 15, and the second
The resonance of the liquid at the frequency f2 in the orifice 16 prevents the generation of muffled sounds. Furthermore, in the configuration of FIG. 1, the elastic membrane 12 is provided so as to constitute a part of the chamber wall of the third fluid chamber 13 communicating with the second orifice 16 having the resonance frequency r2. f
It is possible to lower the vibration transmission rate of the part between 1 and r2 (the part shown in comparison with the dashed line in Fig. 2), and therefore it is also possible to attenuate the low-frequency muffled sound that presses the ears. can.
次に第３図は本発明によるマウンティング装置を等価的
に示したもので、各部分のパラメータを下記の通りに選
定する。Next, FIG. 3 equivalently shows the mounting device according to the present invention, and the parameters of each part are selected as follows.
八、−・第１流体室９の有効面積
Ａ２−第２流体室１１の有効面積
八、−・第３流体室１３のを効面積
Ｂ、−第１流体室１１の有効拡張面積
Ｂ２ ・・第２流体室１３の有効拡張面積ａ１ ・・第
１オリフイス１５の断面積ａ２ ・・第２オリフイス１
６の断面積１１ ・第１オリフイス１５の長さ
１ｔ −・第２オリフイス１６の長さ
に、−第１支持部材３の支持弾性
ｋａ−一第２支持部材５の支持弾性
に、−一第１弾性体６の拡張弾性
に２−第２弾性体７の拡張弾性
に、−弾性膜１２の拡張弾性
ρ −流体密度
Ｐｌ−第１流体室９の圧力
Ｐｔ−・第２流体室１１の圧力
Ｐ、−第３流体室１３の圧力
ｘｌ−第１弾性体６の横方向の変位
ｘよ・−・第２弾性体１１の横方向の変位Ｘ、・−弾性
膜１２の横方向の変位
ｙＩ・−・第１オリフイス１５内の流体の縦方向変位ｙ
２・・・第２オリフイス１６内の流体の縦方向変位ｚ１
−・・第１支持部材３の縦方向変位ｚ２−・・第２支持
部材５の縦方向変位Ｆ７・・・・−伝達力
したがって
第１オリフイス１５内の流体質量ｍ１＝ρａ、ｊ！。8, - Effective area A2 of the first fluid chamber 9 - Effective area A2 of the second fluid chamber 11 8, - Effective area B of the third fluid chamber 13, - Effective expanded area B2 of the first fluid chamber 11 . Effective expansion area a1 of the second fluid chamber 13...Cross-sectional area a2 of the first orifice 15...Second orifice 1
6 cross-sectional area 11 - Length 1t of first orifice 15 - Length of second orifice 16 - Support elasticity ka of first support member 3 - Support elasticity ka of second support member 5 - First 1 - Expansion elasticity of the elastic body 6 2 - Expansion elasticity of the second elastic body 7 - Expansion elasticity ρ of the elastic membrane 12 - Fluid density Pl - Pressure Pt of the first fluid chamber 9 - Pressure of the second fluid chamber 11 P, - Pressure xl of the third fluid chamber 13 - Lateral displacement x of the first elastic body 6, - Lateral displacement X of the second elastic body 11, - Lateral displacement yI of the elastic membrane 12. ---Longitudinal displacement y of the fluid in the first orifice 15
2...Longitudinal displacement z1 of the fluid in the second orifice 16
--Longitudinal displacement z2 of the first support member 3 --Longitudinal displacement F7 of the second support member 5 --Transmission force Therefore, the fluid mass in the first orifice 15 m1 = ρa, j! .
第２オリフイス１６内の流体質１ｍ、＝ρａｚｊ！ｚｍ
＋ｙ＋ −（Ｐｚ Ｐ＋）ａ＋
ｍｚＹｚ ＝ （Ｐ３ Ｐｚ）ａ２
ｋｌＸ＋＝ ＰｌＢｌ
ｋｔｘ、＝ Ｐ２８２
に３Ｘ３” Ｐ３Ｂｓ
ｋＡｚ＋＋ｋｓ（ｚ＋−ｚｏ）＝＝−Ｐ＋（Ａ＋−ａ＋
）＋ Ｐ ｇ（Ａ ｔ −ａ ＋）
Ａ＋２＋”Ｂ＋Ｘ＋＋ａ＋（ｙ＋−２＋）＝０−２＋
（）’＋ ２＋）＋ＢｚＸｚ＋ａｉ （ｙｚ−２＋）
”＜Ａｔ ａｔ）（Ｚｏ ２＋）”０２ｘ（ｙｓ
２１１）＋Ｂ）Ｘ３＝ ＯＢ、
ＢｘＢ。The fluid quality in the second orifice 16 is 1 m, = ρazj! zm
+y+ -(Pz P+)a+ mzYz = (P3 Pz)a2 klX+= PlBl ktx, = P282 to 3X3" P3Bs kAz++ks(z+-zo) ==-P+(A+-a+
)+ P g(A t -a +) A+2+"B+X++a+(y+-2+)=0-2+
()'+ 2+)+BzXz+ai (yz-2+)
"<At at) (Zo 2+)"02x(ys
211)+B)X3=OB,
BxB.
とすると、下記の式が成立する。Then, the following formula holds.
この式を解くと Ｆ ｔ ” Ｋ ＡＺＩ ＋ Ｐ Ｉ
Ａ ＋より振動伝達率を計算できる。Solving this equation gives F t ” K AZI + P I
Vibration transmissibility can be calculated from A+.
以上の説明で明らかなように、本発明においては、２つ
の異なる周波数帯域において振動伝達率を低下させるこ
とができるから、エンジンシェイクとこもり音との双方
を効果的に減衰させることができる。As is clear from the above description, in the present invention, the vibration transmissibility can be reduced in two different frequency bands, so both engine shake and muffled noise can be effectively attenuated.
第１図は本発明の実施例を示す断面図、第２図は第１図
の構成における周波数に対する損失ばね定数と振動伝達
率とを示すグラフ、第３図は第１図の構成を等価的に示
す説明図である。
１−一流体封入マウント ３−・−第１支持部材５−
・第２支持部材 ６・・・第１弾性体７−第２弾
性体 ８〜・・第１仕切板９−・・第１流体室
ｌＯ・・・第２仕切板１１−・・第２流体室
１２・−・弾性膜１３・−・第３流体室 １５
−・・第１オリフィス１６−・第２オリフイスFIG. 1 is a sectional view showing an embodiment of the present invention, FIG. 2 is a graph showing the loss spring constant and vibration transmissibility versus frequency in the configuration of FIG. 1, and FIG. 3 is an equivalent diagram of the configuration of FIG. 1. FIG. 1-Fluid-enclosed mount 3-.-First support member 5-
- Second support member 6... First elastic body 7 - Second elastic body 8 -... First partition plate 9 -... First fluid chamber lO... Second partition plate 11 -... Second fluid room
12.--Elastic membrane 13.--Third fluid chamber 15
--・First orifice 16-・Second orifice
Claims (1)
パワーユニットをマウントする基台に取付けられる第２
の支持部材とを連結する弾性体を備え、この弾性体の内
部に形成される空間の一端を弾性膜で閉塞して密閉され
た室を形成し、この室内に流体を封入したパワーユニッ
トのマウンティング装置において、 前記室を第１および第２の仕切板で仕切ることにより、
前記第１の支持部材側の第１の流体室と、中間の第２の
流体室と、前記弾性膜側の第３の流体室とを直列に形成
し、 前記第１の仕切板に、前記第１および第２の流体室間を
連通する第１のオリフィスを設け、かつ、前記第２の仕
切板に、前記第２および第３の流体室間を連通する第２
のオリフィスを設けるとともに、この第２のオリフィス
における前記流体の共振周波数を前記第１のオリフィス
における前記流体の共振周波数よりも高く設定したこと
を特徴とするパワーユニットのマウンティング設置。[Claims] A first support member attached to a power unit, and a second support member attached to a base on which the power unit is mounted.
A power unit mounting device comprising an elastic body connected to a supporting member, one end of a space formed inside the elastic body being closed off with an elastic membrane to form a sealed chamber, and a fluid sealed in the chamber. In, by partitioning the chamber with first and second partition plates,
A first fluid chamber on the first supporting member side, a second intermediate fluid chamber, and a third fluid chamber on the elastic membrane side are formed in series, and the first partition plate has the A first orifice communicating between the first and second fluid chambers is provided, and a second orifice communicating between the second and third fluid chambers is provided in the second partition plate.
A power unit mounting installation characterized in that an orifice is provided, and the resonance frequency of the fluid in the second orifice is set higher than the resonance frequency of the fluid in the first orifice.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11253286A JPS62270842A (en) | 1986-05-19 | 1986-05-19 | Mounting device for power unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11253286A JPS62270842A (en) | 1986-05-19 | 1986-05-19 | Mounting device for power unit |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS62270842A true JPS62270842A (en) | 1987-11-25 |
Family
ID=14588999
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11253286A Pending JPS62270842A (en) | 1986-05-19 | 1986-05-19 | Mounting device for power unit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62270842A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4976412A (en) * | 1988-11-09 | 1990-12-11 | Hutchinson | Resilient support with anisotropic stiffnesses particularly for bodywork suspensions |
| US5280886A (en) * | 1991-05-07 | 1994-01-25 | Firma Carl Freudenberg | Alternating-resilience engine mount |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59190531A (en) * | 1983-04-08 | 1984-10-29 | Honda Motor Co Ltd | Engine mount with fluid inside |
| JPS6138346B2 (en) * | 1978-10-27 | 1986-08-28 | Yamaha Motor Co Ltd |
-
1986
- 1986-05-19 JP JP11253286A patent/JPS62270842A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6138346B2 (en) * | 1978-10-27 | 1986-08-28 | Yamaha Motor Co Ltd | |
| JPS59190531A (en) * | 1983-04-08 | 1984-10-29 | Honda Motor Co Ltd | Engine mount with fluid inside |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4976412A (en) * | 1988-11-09 | 1990-12-11 | Hutchinson | Resilient support with anisotropic stiffnesses particularly for bodywork suspensions |
| US5280886A (en) * | 1991-05-07 | 1994-01-25 | Firma Carl Freudenberg | Alternating-resilience engine mount |
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