JPS60208649A - Power unit mounting device containing liquid - Google Patents
Power unit mounting device containing liquidInfo
- Publication number
- JPS60208649A JPS60208649A JP6330084A JP6330084A JPS60208649A JP S60208649 A JPS60208649 A JP S60208649A JP 6330084 A JP6330084 A JP 6330084A JP 6330084 A JP6330084 A JP 6330084A JP S60208649 A JPS60208649 A JP S60208649A
- Authority
- JP
- Japan
- Prior art keywords
- orifice
- fluid
- chamber
- damping force
- orifices
- 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
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
- F16F13/107—Passage design between working chambers
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
この発明は、流体入りパワーユニットマウント装置に関
するものである。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a fluid-filled power unit mounting device.
（従来技術）
従来の流体入シパワーユニットマウント装置として、例
えば第１図に示すようなものがある（特開昭５８−７２
７４１号）。すなわち、パワーユニット側の基板５１と
車体側の基板５２との間に流体を封入させた内部空間５
３ａを有するマウントラノ？−５３を固着し、一方の基
板５２側にダイヤフラム５４と仕切板５５とを取付けて
、ダイヤフラム５４と仕切板５５との間に副次室５６を
形成し、仕切板５５と他方の基板５１との間に流体室５
７を形成し、該副次室５６と流体室５７とに流体を封入
させ、かつ仕切板５５に一対のオリフィス５８．５９を
設け、該オリフィス５８．５９にて流体室５７と副次室
５６とを連通させたものである。(Prior Art) As a conventional fluid-filled power unit mounting device, there is one shown in FIG.
No. 741). That is, an internal space 5 in which fluid is sealed between a board 51 on the power unit side and a board 52 on the vehicle body side.
Mt Lano with 3a? -53 is fixed, and a diaphragm 54 and a partition plate 55 are attached to one side of the substrate 52, a subchamber 56 is formed between the diaphragm 54 and the partition plate 55, and a subchamber 56 is formed between the diaphragm 54 and the partition plate 55, and fluid chamber 5 between
A pair of orifices 58,59 are provided in the partition plate 55, and the orifices 58,59 allow the fluid chamber 57 and the secondary chamber 56 to be sealed. It is a communication between
しかしながら、このような従来のマウント装置にあって
は、一対のオリフィス５８．５９は、一方のオリフィス
５８の断面積をＡ′１、他方のオリフィス５９の断面積
をＡ／２としてＡ’ １ ／ Ａ′２ ：４、また一方
のオリフィス５８の長さをｔ′３、径ｆ ｄ’ｔ 、他
方のオリフィス５９の長さを７１、径８ｄ′！ として
Ｚ／ 、／ ｄｔｌ・ｄ’ ｔ／ Ｚ ｔ ： ２の関
係となっており、大きな断面積Ａ’ Ｈのオリフィス５
８のロスファクタか０．３程度と低く、小さな断面ｕｔ
Ａ’ｔ のオリフィス５９のロスファクタはさらにそ
のｌ／４程度と低く、エンジンシェイクを生ずる低周波
数域例えば５〜１５Ｈｚにおいて良好な減衰力を発生さ
せることが困難であるという問題点かあった。However, in such a conventional mounting device, the pair of orifices 58 and 59 have a cross-sectional area of A'1/A'1, and a cross-sectional area of A'1 and A/2 of the other orifice 59, respectively. A'2: 4, and the length of one orifice 58 is t'3 and diameter f d't, and the length of the other orifice 59 is 71 and diameter 8d'! As Z/ , / dtl・d' t/ Z t : 2, the orifice 5 with a large cross-sectional area A' H
Low loss factor of 8 or around 0.3, small cross section ut
The loss factor of the orifice 59 of A't is still as low as about 1/4, and there is a problem in that it is difficult to generate a good damping force in the low frequency range where engine shake occurs, for example, 5 to 15 Hz.
（発明の目的）
この発明は、このような従来の問題点に鑑みてなされた
もので、本発明者等の行なった種々の実験から知得され
た後記する事実に基づき、マウント装置に、流体室と副
次室とを連通させる断面積のほぼ等しい複数個のオリフ
ィスを備えさせ、その一対のオリフィスの長さ比ｉｆ
１５〜９に設定させることにより、減荻力か最大値を示
す周波数をエンジンシェイクを生ずる低周波数域に合致
させ、かつ適正な減衰力を発生させ、上記問題点を解決
することを目的としている。(Object of the Invention) This invention was made in view of such conventional problems, and is based on the facts described later that were learned from various experiments conducted by the present inventors. A plurality of orifices having approximately equal cross-sectional areas are provided to communicate the chamber and the sub-chamber, and the length ratio of the pair of orifices is
By setting the damping force to 15 to 9, the purpose is to match the frequency showing the maximum value of the engine shake to the low frequency range that causes engine shake, and generate an appropriate damping force, thereby solving the above problems. .
（実施例）
以下、この発明について図示の実施例を参照して説４明
する。(Embodiments) The present invention will be explained below with reference to illustrated embodiments.
第２図に、この発明の第−実施例を示す。パワーユニッ
ト側の基板１と単体側の基板２との間に内部空間３ａｉ
有するマウントラバー３を固着し、各基板１，２側にダ
イヤフラム４．５と仕切板６，７とを各々固定し、一方
のダイヤフラム４９１１１ Ｋ第−副次室８を形成し、
他方のダイヤフラム５側に第二副次室９８形成しである
。FIG. 2 shows a second embodiment of the invention. An internal space 3ai is provided between the power unit side board 1 and the single unit side board 2.
The mount rubber 3 having the diaphragm 49111K is fixed, and the diaphragm 4.5 and the partition plates 6 and 7 are fixed to each of the substrates 1 and 2, and one diaphragm 49111K is formed to form a secondary chamber 8.
A second subchamber 98 is formed on the other diaphragm 5 side.
具体的には、マウントラバー３は、仕切板６と円錐蟻状
の支持板１０との間に加硫接着され、仕切板６はダイヤ
フラム４の外縁ヲ挾圧させてその外縁を内１１４＋１に
折曲げて基板１に固定され、支持板ｌＯは、その下部を
基板２に固定されて基板２と一体を成して仕切板７とダ
イヤフラム５の各外周縁を秋眉している。かくしてダイ
ヤフラム４と仕切板６とに′７Ｃ第−副次室８を画成し
、側仕切板６，７間に流体歴１１８形成し、仕切板７と
ダイヤフラム５とにて第二副次室９を画成し、各室８，
９．１１に水、油等の非圧縮性の流体を封入しである。Specifically, the mount rubber 3 is vulcanized and bonded between the partition plate 6 and the conical dovetail-shaped support plate 10, and the partition plate 6 presses the outer edge of the diaphragm 4 and folds the outer edge into the inner part 114+1. The supporting plate 1O is bent and fixed to the substrate 1, and its lower part is fixed to the substrate 2, forming an integral part with the substrate 2 and surrounding the outer peripheral edges of the partition plate 7 and the diaphragm 5. Thus, the diaphragm 4 and the partition plate 6 define a '7C secondary chamber 8, a fluid history 118 is formed between the side partition plates 6 and 7, and the partition plate 7 and the diaphragm 5 define a second secondary chamber 8. 9, each room 8,
9.11 is filled with an incompressible fluid such as water or oil.
そして、一方の仕切板７には、流体室１．１と第二副次
室９とを連通させる絞り流路たるオリフィス１４そ設け
、他方の仕切板６には、流体ｇｌｉと第一副次室８とを
連通させる絞り流路たるオリフィス１５を設ける。オリ
フィス１４゜１５は、第３図に示すように２字状の流路
１４ａ。One partition plate 7 is provided with an orifice 14, which is a throttle flow path that communicates the fluid chamber 1.1 and the second subchamber 9, and the other partition plate 6 is provided with an orifice 14 that connects the fluid gli and the first subchamber 9. An orifice 15 serving as a throttle flow path communicating with the chamber 8 is provided. The orifices 14 and 15 are two-shaped flow passages 14a as shown in FIG.
１５ａよりなり一端の開口１４ｂ、１５ｂにて流体室１
１に遅進させ、他端の開口１５ｃ 、 １４ｃに°Ｃ第
一副次室８または第二副次室９に連通させである。The fluid chamber 1 is formed by openings 14b and 15b at one end.
1, and the openings 15c and 14c at the other end communicate with the first sub-chamber 8 or the second sub-chamber 9.
ここで、本発明者等が行なった実験により、下記の事実
が判明しでいる。すなわち、オリフィス１４．１５の減
其能力か最大値を示す周波数はオリフィス１４．１５の
長さｔと径ｄ（σ、ここにＡは断面積）とに依存してお
り、ｌ／σおよびｄ（４ズー）に比例する。また、減衰
能力は断面積Ａに比例する０
しかして、両オリフィス１４．１５（７）′＃、衰能力
を良好値すなわち減衰能力の目安として一般に用いられ
ているロスファクタを０．４以上として一致させて与え
るためには、一方のオリフィス１４のロスファクタの最
大値ｆ Ｌｌｍａｘ １断面積ｆＡｌまた他方のオリフ
ィス１５のロスファクタの最大値をＬｌｍａｘ １断面
積をＡ！として、Ｌ１ｍａＸ／Ｌａｍａ Ｘ ” Ａｔ
／Ａ、：＝ １であり、従ってＡ、 ＝ Ａ、となる。As a result of experiments conducted by the present inventors, the following facts have been discovered. In other words, the frequency at which the orifice 14.15 exhibits the maximum value of its reduction ability depends on the length t and diameter d (σ, where A is the cross-sectional area) of the orifice 14.15, and l/σ and d (4 zoos). In addition, the damping capacity is proportional to the cross-sectional area A. Therefore, if both orifices are 14.15(7)'#, the damping capacity should be set to a good value, that is, the loss factor generally used as a guideline for the damping capacity should be set to 0.4 or more. In order to match, the maximum value of the loss factor of one orifice 14 f Llmax 1 cross-sectional area fAl and the maximum value of the loss factor of the other orifice 15 must be Llmax 1 cross-sectional area A! As, L1maX/Lama X ” At
/A, := 1, so A, = A.
また、一方のオリフィス１４の減衰能力か最大値を示す
共振周波数をｆＬ、ｍａｘ１長さをｔい径゛をｄｌ、ま
た、他方のオリフィス１５の減衰能力が最大値を示す共
振周波数をｆ Ｌｌｍａ Ｘ ％長さをｔ６、径ｆ ｄ
ｔ トして、エンジンシェイクを生ずる低周波数域例え
ば５〜１５Ｈｚにおいて、一方のオリフィス１４の共振
周波数を８Ｈ２とし、他方のオリフィス１５の共振周波
数を１３Ｈ２とすれば、ｆＬ１ｍａｘ／ ｆＬｆｎａｘ
＝’ｔ／ ａ！′σシｚ’＝； Ｌ ６３、またＡ。In addition, the resonance frequency that indicates the maximum value of the damping capacity of one orifice 14 is fL, the length of max1 is t and the diameter is dl, and the resonance frequency that indicates the maximum value of the damping capacity of the other orifice 15 is f Llma % length t6, diameter f d
If the resonance frequency of one orifice 14 is 8H2 and the resonance frequency of the other orifice 15 is 13H2 in the low frequency range where engine shake occurs, for example 5 to 15Hz, then fL1max/fLfnax
='t/ a! 'σsiz'=; L 63, also A.
＝痴よりｄ、＝ ｄ、ゆえに、ｔ、−２，６４１，とな
る。また、一方のオリフィス１４の共振周波数を５Ｈ２
とし、他方のオリフィス１５の共振周波数を１５Ｈ２と
すれば、ｆ Ｌ、＋ｎａｘ ／ ｆ Ｌ２ｍａｘ ＝
ｄｔｌ ｄ２ ・Ｆレテ＝３ゆえに、ｔｔ： ９ ｔｌ
となる。= d, = d, therefore, t, -2,641. In addition, the resonance frequency of one orifice 14 is set to 5H2.
If the resonance frequency of the other orifice 15 is 15H2, then f L, +nax / f L2max =
dtl d2 ・Frete=3, so tt: 9 tl
becomes.
しかして、ｄをほぼ同じにしてｔを２．５〜９倍変える
必要がある。Therefore, it is necessary to keep d approximately the same and change t by 2.5 to 9 times.
次に作用について説明する。Next, the effect will be explained.
エンジンシェイクを生ずる低周波数域、例えば５〜１３
Ｈ２での大振幅振動か基板ｌより入力されると、マウン
トラノ々−３か大きく伸粗し、流体室１１の体積変化を
生ずる。その結果、低い周波数域においで長さの長いオ
リフィス１４内の流体質量が共振して大きな減放力を発
生させ、それより高い周波数域において長さの短いオリ
フィス１５内の流体質量が共振してほぼ同じ減衰力を発
生させ、エンジンシェイクを効果的に制振させる。Low frequency range that causes engine shake, e.g. 5-13
When large-amplitude vibrations at H2 are input from the substrate 1, the mount Rano-3 is greatly expanded and the volume of the fluid chamber 11 changes. As a result, the fluid mass in the long orifice 14 resonates in a low frequency range, generating a large release force, and the fluid mass in the short orifice 15 resonates in a higher frequency range. Generates almost the same damping force and effectively suppresses engine shake.
第４図に、この発明の第二実施例を示す。パワーユニッ
ト側の基板１０１と車体側の基板１０２との間に内部空
間１１１３ａ−ｉ有するマウントラノ々−１０３を固層
し、一方の基板１０２側にダイヤフラム１０４と仕切板
１０７とを固定し、ダイヤフラム１０４と仕切板１０７
との間に副次室１０９８形成し、他方の基板１０１ （
１１に流体室１１１７ｉ：形成して副次室１０９と流体
室１１１とに流体を封入しである。具体的には、マウン
トラノ々−１０３は覆板１０６と円錐環状の支持板１１
０との間に加硫接着され、覆板１０６は外周縁を基板１
０１に溶接同治され、支持板１１０はその下部フランジ
を仕＋Ｊ１板１０７、ダイヤフラム１０４と共に基：Ｉ
″］Ａ０２の外周縁に接着されている。FIG. 4 shows a second embodiment of the invention. A mount platen 103 having an internal space 1113a-i is solidly layered between the power unit side substrate 101 and the vehicle body side substrate 102, and a diaphragm 104 and a partition plate 107 are fixed to one side of the substrate 102. Partition plate 107
A subchamber 1098 is formed between the other substrate 101 (
A fluid chamber 1117i is formed in 11 and a fluid is sealed in the sub chamber 109 and the fluid chamber 111. Specifically, the mount lano-103 includes a cover plate 106 and a conical ring-shaped support plate 11.
0, and the cover plate 106 has an outer peripheral edge attached to the substrate 1.
01, and the support plate 110 has its lower flange fixed together with the J1 plate 107 and the diaphragm 104.
″] is glued to the outer peripheral edge of A02.
そして、仕切板１０７の流体室１１１側と副次室１０９
側とにはそれぞれ流体ｍ１ｌｌと副次ｇ１０９とを連通
させる絞り流路たるオリフィス１１４゜１１５を設ける
。オリフィス１１４ 、１１５は、第５図に示すように
視ｙｌｘ４ｄ、 ｚｘｓｄ にて区画されたわん曲する
流路１１４ａ 、 １１５ａ よりなり一端の開口１１
４ｂ 、 １１５ｂ にて流体室１１１に連通さぜ、細
端の開口１１４ｃ 、 １１５ｃ にて副次室１０９に
連通させである。Then, the fluid chamber 111 side of the partition plate 107 and the subchamber 109
Orifices 114 and 115 are provided on the sides, respectively, to serve as throttle channels for communicating the fluid m1ll with the subdivision g109. As shown in FIG. 5, the orifices 114 and 115 are curved channels 114a and 115a that are divided at ylx4d and zxsd, and the opening 11 at one end.
4b and 115b communicate with the fluid chamber 111, and narrow end openings 114c and 115c communicate with the subchamber 109.
シカシて、一方のオリフィス１１４の断面ｂｔ Ａ３と
他方のオリフィス１１５の断面積Ａ４とをほぼ等しくす
ると共に、一方のオリフィス１１４の長さをｔｌ、他方
のオリフィス１１５の長さｆ ｔ４として、’ａ／１４
＝２．５〜９の関係を与えである。In other words, the cross-sectional area btA3 of one orifice 114 and the cross-sectional area A4 of the other orifice 115 are approximately equal, and the length of one orifice 114 is tl, and the length of the other orifice 115 is ft4, 'a /14
=2.5 to 9 is given.
しかして、この実施例によっても前記実施例と同様の作
用か得られる。Therefore, this embodiment also provides the same effect as the previous embodiment.
なお、オリフィス１１４，１１５は上記構成に限定され
るものではなく、第６図に示すようにうず巻状の流路１
１６ａの両端に開口１１６ｂ 、 １１６ｃを設けたオ
リフィス１１６とすることもできる。Note that the orifices 114 and 115 are not limited to the above configuration, and as shown in FIG.
The orifice 116 may be provided with openings 116b and 116c at both ends of the orifice 16a.
またオリフィス１１４の共振周波数を例えば５Ｈｚに設
定し、オリフィス１１５の共振周波数を例えば１５ Ｈ
ｚに設定し、史に共振周波数か１０Ｈｚのオリフィスを
仕切板ＩＣ）７に設けることもできる。Further, the resonant frequency of the orifice 114 is set to, for example, 5Hz, and the resonant frequency of the orifice 115 is set to, for example, 15Hz.
z, and an orifice with a resonant frequency of 10 Hz can be provided in the partition plate IC)7.
（発明の構成）
以上説明したように、この発明によればその構成を、ノ
ξワーユニット偵１１の基板と車体側の基板との間に内
部空間を有するマウントラノ々−を固ンｉ） Ｌ／、少
なくとも一方の基板側にダイヤフラムと仕切板とを取付
けで、ダイヤフラムと仕切板との間に副次室を形成し、
他方の基板側に流体室を形成して、該副次室と流体室と
に流体を封入すると共に、上記仕切板は、流体室と副次
室とを連通させ、断面積がほぼ等しく、かつ一対の長さ
比か２５〜９に設定されたオリフィスを復数個備える流
体入りパワーユニットマウント装置とした。(Configuration of the Invention) As explained above, according to the present invention, the configuration is such that the mount planes having an internal space between the base plate of the lower unit 11 and the base plate on the vehicle body side are fixed. /A diaphragm and a partition plate are attached to at least one substrate side, and a subchamber is formed between the diaphragm and the partition plate,
A fluid chamber is formed on the other substrate side, and a fluid is sealed in the sub-chamber and the fluid chamber, and the partition plate communicates between the fluid chamber and the sub-chamber, has approximately equal cross-sectional area, and The fluid-filled power unit mount device is provided with a plurality of orifices having a pair length ratio of 25 to 9.
（発明の、効果）
従って、オリフィスの断面０２ （Ｅ” ：１１″！桶
に設定することにより、減衰能力をほぼ同一の良好値に
設定させ、刀）つそれらの共振周波数をエンジンシェイ
クを生ずる低周波数域に設定させて、エンジンシェイク
を効果的に制像させることかできるという効果が得られ
る。(Effects of the invention) Therefore, by setting the cross section of the orifice to 02 (E": 11"), the damping capacity can be set to almost the same good value, and the resonance frequency of the orifice can be adjusted to cause engine shake. By setting it in a low frequency range, it is possible to effectively suppress engine shake.
第１図は従来のマウント装置の断面図、第２図はこの発
明の第一実施１りｕを示すｌυＩ而図面第３図はオリフ
ィスの断面図、第４図はこの発明の第二実施例を示す断
面図、εＢ５図はオリフィスの断面図、第６図はオリフ
ィスの他の構造例を示す断面図である。
１．１０１，２．１０２ ：基板、３，１０３ ：マウ
ントラノ々−１３ａ、１１１３ａ ：内部空間、４，５
，１０４ ：ダイヤフラム、６，７，１０７ ：仕切板
、８，９，１０９ ：副次室、１１．１１１：流体室、
１４，１５，１１４．１１５ ニオリフイス代理人 弁
理士 前 １）利 之
第１図
５８″：）９ Ｏｂ Ｏ’）
第２図
第３図
第４図
１１５ｃ １１５ａ
第５図
第６図
１１６ＣFig. 1 is a sectional view of a conventional mounting device, Fig. 2 is a drawing showing a first embodiment of the present invention, Fig. 3 is a sectional view of an orifice, and Fig. 4 is a second embodiment of the invention. Figure εB5 is a cross-sectional view of the orifice, and FIG. 6 is a cross-sectional view showing another structural example of the orifice. 1.101, 2.102: Substrate, 3,103: Mount Rano-13a, 1113a: Internal space, 4,5
, 104: Diaphragm, 6, 7, 107: Partition plate, 8, 9, 109: Sub-chamber, 11.111: Fluid chamber,
14, 15, 114.115 Niorifis agent Patent attorney front 1) Toshiyuki Figure 1 58'':) 9 Ob O') Figure 2 Figure 3 Figure 4 115c 115a Figure 5 Figure 6 116C
Claims (1)
内部空間を有するマウントラノ々−を固着し、少なくと
も一方の基板側にダイヤフラムと仕切板とを取付けて、
ダイヤフラムと仕切板との間に副次室を形成し、他方の
基板側に流体室を形成して、該副次室と流体室とに流体
を封入すると共に、上記仕切板は、流体室と副次室とを
連通させ、断面積がほぼ等しく、かつ一対の長さ比が２
．５〜９に設定されたオリフィスを複数個備えることを
特徴とする流体入りノぞワーユニットマウント装置。1. Fix a mount plate having an internal space between the board on the side of the noswer unit and the board on the vehicle body side, and attach a diaphragm and a partition plate to at least one board side,
A sub-chamber is formed between the diaphragm and the partition plate, a fluid chamber is formed on the other substrate side, and a fluid is sealed in the sub-chamber and the fluid chamber. communicate with the secondary chamber, have approximately the same cross-sectional area, and have a length ratio of 2.
．． A fluid-filled nozzle unit mount device comprising a plurality of orifices set in the range of 5 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6330084A JPS60208649A (en) | 1984-04-02 | 1984-04-02 | Power unit mounting device containing liquid |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6330084A JPS60208649A (en) | 1984-04-02 | 1984-04-02 | Power unit mounting device containing liquid |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60208649A true JPS60208649A (en) | 1985-10-21 |
Family
ID=13225318
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6330084A Pending JPS60208649A (en) | 1984-04-02 | 1984-04-02 | Power unit mounting device containing liquid |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60208649A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5145156A (en) * | 1990-02-02 | 1992-09-08 | Tokai Rubber Industries, Ltd. | Fluid-filled elastic mount having two differently tuned orifices selectively utilized for damping or isolating vibrations in different frequency ranges |
| US5286012A (en) * | 1992-05-07 | 1994-02-15 | Hutchinson | Hydraulic antivibration devices |
-
1984
- 1984-04-02 JP JP6330084A patent/JPS60208649A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5145156A (en) * | 1990-02-02 | 1992-09-08 | Tokai Rubber Industries, Ltd. | Fluid-filled elastic mount having two differently tuned orifices selectively utilized for damping or isolating vibrations in different frequency ranges |
| US5286012A (en) * | 1992-05-07 | 1994-02-15 | Hutchinson | Hydraulic antivibration devices |
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