JPS60155029A - Vibration isolating device containing fluid - Google Patents
Vibration isolating device containing fluidInfo
- Publication number
- JPS60155029A JPS60155029A JP1173184A JP1173184A JPS60155029A JP S60155029 A JPS60155029 A JP S60155029A JP 1173184 A JP1173184 A JP 1173184A JP 1173184 A JP1173184 A JP 1173184A JP S60155029 A JPS60155029 A JP S60155029A
- Authority
- JP
- Japan
- Prior art keywords
- fluid
- chamber
- frame
- vibration
- damping force
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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
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)
- Fluid-Damping Devices (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明し、１、エンジンを初めとするパワーユニット等
の振動体から入力される振動入力を、流体の絞り通過に
起因する減衰力により減衰して、前記振動が＠（体等の
支持体に伝達することを防止する装置に関する。[Detailed Description of the Invention] [Industrial Application Field] The present invention provides a method for attenuating vibration input from a vibrating body such as an engine or a power unit by a damping force caused by passage of a fluid through a constriction. The present invention relates to a device for preventing the vibrations from being transmitted to a support such as a body.
従来の流体入り防振装置としては、例えば第１図に示す
ようなものがある（特開昭５８−７２７４１号公報記載
）。即ち、振動体側の枠体１と支持体側の枠体２との間
に、両枠体１，２の相対移動により内部の流体主室３の
容積を変化させるゴム状弾性体４を配置し、前記流体主
室３には、当該流体主室３の容積変化に対応して容積変
化する流体副次室５を、枠体２側に支持される仕切６に
形成された絞り７．８を介して連結して、絞り７゜８を
介しての流体主室３と流体副次室５との間の流体９の移
動により振動入力を減衰させるようにしである。絞り７
，８は、その内径と長さとを相互に相違させていて、減
衰特性を相違させている。An example of a conventional fluid-filled vibration isolator is shown in FIG. 1 (described in Japanese Patent Laid-Open No. 72741/1983). That is, a rubber-like elastic body 4 is arranged between the frame body 1 on the vibrating body side and the frame body 2 on the support body side, which changes the volume of the internal fluid main chamber 3 by relative movement of both the frame bodies 1 and 2. A fluid subchamber 5 whose volume changes in response to a change in the volume of the fluid main chamber 3 is provided in the main fluid chamber 3 through a throttle 7.8 formed in a partition 6 supported on the frame body 2 side. The vibration input is damped by the movement of the fluid 9 between the main fluid chamber 3 and the secondary fluid chamber 5 through the throttle 7.8. Aperture 7
, 8 have different inner diameters and lengths, and have different damping characteristics.
１０は、流体副次室５を画成するためのダイヤプラムで
あり、流体副次室５の容積変化に追従して形状を変化す
るようにしである。Reference numeral 10 denotes a diaphragm for defining the sub-fluid chamber 5, which changes its shape in accordance with changes in the volume of the sub-fluid chamber 5.
かくして、枠体１側からの振動入力により流体主室３の
容積が変化して、流体主室３と流体副次室５との間で流
体９が移動し、このとき流体９が絞り７，８を通過する
ことにより絞られて、前記振動入力が減衰される。ここ
で得られる減衰特性は、絞り７による減衰特性と、絞り
８による減衰特性とが複合された、ピークが２つ表れる
減衰特性となり、第２図において実線で示される。第２
図における鎖線は、振動伝達力を示し、前記絞り７．８
で減衰されずに枠体２に伝達される振動である。第２図
におけるＩＶはエンジンのアイドリング振動域である。Thus, the volume of the main fluid chamber 3 changes due to the vibration input from the frame 1 side, and the fluid 9 moves between the main fluid chamber 3 and the sub-fluid chamber 5, and at this time, the fluid 9 moves through the throttle 7, 8, the vibration input is attenuated. The damping characteristic obtained here is a combination of the damping characteristic due to the diaphragm 7 and the damping characteristic due to the diaphragm 8, and has two peaks, and is shown by a solid line in FIG. 2. Second
The chain line in the figure indicates the vibration transmission force, and the aperture 7.8
This is the vibration that is transmitted to the frame 2 without being attenuated. IV in FIG. 2 is the idling vibration range of the engine.
第３図は、第１図の模式図であり、１Ｉｌａは、絞り７
内の流体質量とダイヤフラム１０とによる質量、ｍｂは
、絞り８内の流体質量とダイヤプラム１０とによる質量
であり、ｋａは、ダイヤフラム１０の剛性、ｋｈば、ゴ
ム状弾性体４の剛性、ｃａは、絞り７の１１衰力、ｃｂ
は、絞り８の減衰力を示している。FIG. 3 is a schematic diagram of FIG. 1, and 1Ila is the aperture 7
mb is the mass due to the fluid mass in the throttle 8 and the diaphragm 10, ka is the rigidity of the diaphragm 10, kh is the rigidity of the rubber-like elastic body 4, ca is the 11 damping force of the aperture 7, cb
indicates the damping force of the diaphragm 8.
しかしながら、このような従来の流体入り防振装置にお
いては、流体主室３の容積と流体副次室５の容積とが、
絞り７，８の何れにも共通していて、ダイ４・フラム１
０及び弾性体４の剛性ｋａ、ｋｂが同一なため、防振装
置の振動入力減衰特性をチューニングする領域が限定さ
れやすい。このため、例えば、エンジンの上下方向振動
域は一般に１０Ｈｚ程度、ステアリング共振域は一般に
３０ Ｉｌｚ程度、エンジンのティ）・リング振動域が
一般に２０〜３０（１ｚ程度であるところ、第２図に示
すように、減衰力のピークを］０１１ｚ程度に設定する
と、アイドリング振動域ＩＶ及びステアリング共振域の
減衰力を充分に設定することが困ｊｌＷになるという不
具合がある。However, in such a conventional fluid-filled vibration isolator, the volume of the main fluid chamber 3 and the volume of the secondary fluid chamber 5 are
Common to both apertures 7 and 8, die 4 and flam 1
Since the rigidities ka and kb of the elastic body 4 and the elastic body 4 are the same, the range in which the vibration input damping characteristics of the vibration isolator are tuned is likely to be limited. For this reason, for example, the vertical vibration range of an engine is generally about 10 Hz, the steering resonance range is generally about 30 Ilz, and the engine tee/ring vibration range is generally about 20 to 30 (1 z), as shown in Figure 2. If the peak of the damping force is set to about ]011z, it becomes difficult to set the damping force sufficiently in the idling vibration region IV and the steering resonance region.
本発明は、このような従来の不具合に着目してなされた
ものであり、流体主室に絞りを介して連続する流体副次
室を、流体主室に対して複数形成することにより、流体
副次室及び絞りを他のそれらと独立して設置して、複数
相れる減衰力のピークを、減衰しようとする振動域に適
応さ・ｌ！て設定することを可能にし、！２Ｊて前記従
来の不具合を解決することを目的としている。The present invention has been made by focusing on such conventional problems, and by forming a plurality of fluid sub-chambers that are continuous to the fluid main chamber via a restriction, the fluid sub-chambers are connected to the fluid main chamber via a restriction. By installing the next chamber and the diaphragm independently from the others, the peak of the damping force that occurs in multiple phases can be adapted to the vibration range to be damped. and allows you to configure it! 2J aims to solve the above-mentioned conventional problems.
本発明は、振動体側の枠体と支持体側の枠体との間に、
両枠体の相対移動により内部の流体主室の容積を変化さ
せるゴム状弾性体を配置し、前記流体主室には、当該流
体主室の容積変化に対応して容積変化する流体副次室を
、何れかの枠体側に支持される絞りを介して連結して、
絞りを介しての流体主室と流体副次室との間の流体の移
動により振動入力を減衰させる流体入り防振装置におい
て、前記流体副次室を、流体主室に対して複数形成した
ごとを特徴とする流体入り防振装置にかかる。In the present invention, between the frame on the vibrating body side and the frame on the support side,
A rubber-like elastic body is arranged to change the volume of an internal main fluid chamber by relative movement of both frames, and the main fluid chamber has a secondary fluid chamber whose volume changes in response to a change in the volume of the main fluid chamber. are connected via an aperture supported on either frame side,
In a fluid-filled vibration isolator that damps vibration input by movement of fluid between a fluid main chamber and a fluid sub-chamber via a throttle, a plurality of said fluid sub-chambers are formed relative to the fluid main chamber. The fluid-filled vibration isolator is characterized by:
ｒ実施例〕
以下に、本発明を図示実施例に基づいて説明する。第４
〜８図は、本発明の第１実施例を示す図であり、エンジ
ンを初めとするパワーユニットの防振装置に本発明を適
用した例を示す。Embodiment] The present invention will be described below based on illustrated embodiments. Fourth
8 are diagrams showing a first embodiment of the present invention, and show an example in which the present invention is applied to a vibration isolator for a power unit such as an engine.
まず構成を説明すると、１１が振動体たるパワー１−二
ノト側の枠体、Ｉ２が支持体たる車体側の枠体である。First, the configuration will be described. Reference numeral 11 indicates a frame body on the power 1-2 side that is a vibrating body, and I2 indicates a frame body on the vehicle body side that serves as a support body.
枠体１１には仕切板１３が固定されていて、仕切板１３
の中央部に形成された第１絞り１４を除く部分は、実体
的に枠体１１の一部をなす。また、枠体１２には補助枠
１５と仕切板１６とが固定され、補助枠１５４；ｌ実体
的に枠体１２の一部をなす。仕ＬＪＪ板１６には第２絞
り１７が形成される。A partition plate 13 is fixed to the frame 11, and the partition plate 13
The portion excluding the first diaphragm 14 formed in the center of the frame 11 substantially forms a part of the frame 11. Further, an auxiliary frame 15 and a partition plate 16 are fixed to the frame 12, and the auxiliary frame 154 substantially forms a part of the frame 12. A second aperture 17 is formed on the partition LJJ plate 16.
前記した、実体的に枠体１１をなず仕切板１３と、実体
的に枠体１２をなす補助枠１５との間に、ゴム状弾性体
Ｉ８を加硫接着して、ゴム状弾性体１８の内側の、第１
絞り１４と第２絞り１７との間に流体主室１つが形成さ
れる。仕切板１３の上側には、上面をダイヤフラム２０
で画成した第１流体副次室２１が形成され、また仕切板
１６の下側には、下面をダイードフラム２２で画成した
第２流体副次室２３が形成される。A rubber-like elastic body I8 is vulcanized and bonded between the partition plate 13 which does not substantially form the frame body 11 and the auxiliary frame 15 which substantially forms the frame body 12, as described above. inside the first
One fluid main chamber is formed between the throttle 14 and the second throttle 17. On the upper side of the partition plate 13, there is a diaphragm 20 on the top surface.
A first fluid sub-chamber 21 is formed, and a second fluid sub-chamber 23 is formed below the partition plate 16, the lower surface of which is defined by a diode flamm 22.
枠体Ｉｔとダイヤフラム２０との間には：空気室２４が
形成され、これば、枠体１１に開口された空気孔２５を
介して大気に連通している。また枠体１６とダイヤフラ
ム２２との間には空気室２６が形成され、これは、枠体
１２に開口された空気孔２７を介して大気に連通してい
る。An air chamber 24 is formed between the frame It and the diaphragm 20, and communicates with the atmosphere via an air hole 25 opened in the frame 11. Further, an air chamber 26 is formed between the frame body 16 and the diaphragm 22, and this air chamber 26 communicates with the atmosphere through an air hole 27 opened in the frame body 12.
第１絞りＩ４は、第４，５図に示すように、仕切板１３
に隙間をおいて固定された板体１４ａと、（，１切板１
３に開設された孔１４ｂと、板体１４ａに開設さ１７た
孔１４ｃと、仕切板１３及び板体１４ａの間に、孔１．
ｌｂ及び孔１４ｃを連結し且つ蛇行し２て形成された蛇
行通路１４ｄとからなる。The first aperture I4 is connected to the partition plate 13 as shown in FIGS.
A plate body 14a fixed with a gap between and (,1 cut plate 1
The hole 14b opened in the hole 1.3, the hole 14c opened in the plate 14a, and the hole 14c opened in the plate 14a between the partition plate 13 and the plate 14a.
lb and a meandering passage 14d which is formed by connecting the hole 14c and meanderingly.
第２絞り１７の構造は、第１絞り１４と同様であるが、
その孔＋４ｂ、１４Ｃ蛇行通路＋４ｄの長さや大きさの
寸法を第１絞り１４と相違させて、実体的に絞り１４．
１７の径と長さとを変えて減衰力が相違するようにしで
ある。The structure of the second diaphragm 17 is similar to that of the first diaphragm 14, but
The length and size of the holes +4b and 14C meandering passage +4d are made different from those of the first aperture 14, so that the aperture 14.
By changing the diameter and length of 17, the damping force can be varied.
前記流体主室］９．第１流体副次室２１．第２流体副次
室２３には液体が充填されてあり、この液体は、第１絞
り１４．第２絞り１７を介して各室＋９．２１．２３に
連通ずるようにしである。Said main fluid chamber]9. First fluid subchamber 21. The second fluid subchamber 23 is filled with liquid, and this liquid flows through the first restrictor 14 . It communicates with each chamber +9, 21, and 23 via the second restrictor 17.
また、ダイヤフラＪい２０，２２の剛性は、相互に相違
さ」！でいる。Also, the rigidity of diaphragms 20 and 22 is different! I'm here.
次に作用を説明する。Next, the effect will be explained.
振動体の１−下振動が枠体１１から入力されると仕切板
１３が枠体１１と一体に振動して、ゴム状弾性体１８を
伸縮させる。すると、流体主室１９の容積が拡縮変化し
て、その都度流体主室１９と第１流体副次室２１及び第
２流体副次室２３との間で第１絞り１４．第２絞り１７
を介して液体の往復移動が生しる。この、液体が第１絞
り１４及び第２絞り１７を通過するときに、各絞り１４
゜１７の流通抵抗を受けるため、この抵抗により振動エ
ネルギーが熱エネルギーに変換されて、前記振動が減衰
される。かくして枠体１１に入力された振動は枠体１２
には伝達されないか、又は減衰されて微弱になった振動
が枠体１２に伝達されることになる。When the 1-down vibration of the vibrating body is input from the frame 11, the partition plate 13 vibrates together with the frame 11, causing the rubber-like elastic body 18 to expand and contract. Then, the volume of the main fluid chamber 19 expands or contracts, and the first throttle 14 . Second aperture 17
A reciprocating movement of liquid occurs through the . When the liquid passes through the first aperture 14 and the second aperture 17, each aperture 14
Since it is subjected to a flow resistance of 17°, this resistance converts vibrational energy into thermal energy and damps said vibrations. In this way, the vibration input to the frame 11 is transmitted to the frame 12.
The vibrations that are not transmitted to the frame body 12, or are attenuated and become weak, are transmitted to the frame body 12.
流体主室１９の容積が縮小されたときには、そこの液体
が第１流体副次室２１．第２流体副次室２３に移動する
ため、両副次室２１，２３の容積が増大する。このとき
はダイ４・フラム２０，２２が流体主室１９より遠い側
に変形して前記容積の増大を許容する。そして、このと
きの空気室２４゜２６の容積変化は、孔２５．２７から
空気が外部に逃げ出すことによって許容される。When the volume of the main fluid chamber 19 is reduced, the liquid therein flows into the first sub-fluid chamber 21. Since the fluid moves to the second sub-chamber 23, the volumes of both sub-chambers 21 and 23 increase. At this time, the die 4 and flamms 20, 22 are deformed to the side farther from the main fluid chamber 19, allowing the volume to increase. The change in volume of the air chambers 24 and 26 at this time is allowed by the air escaping to the outside from the holes 25 and 27.
第６図は、第４図のモデル図、第８図は、第４図の模式
図であり、第８図において、ｋｅは流体主室１９の液体
を支える剛性、ｃｃは第１絞り１４の減衰力、ｃｄは第
２絞り１７の減衰力、ｍｃは第１絞り１４内の液体質量
とダイヤフラム２０とによる質ｉｉ、ｍｄは第２絞り１
７内の液体質量とダイヤフラム２２とによる質量、ｋｃ
はダイヤフラム２０の剛性、ｋｄはダイヤフラム２２の
剛性である。かかる減衰力、質量、剛性を適度に設定す
ることにより、防振装置の特性は第７図に示すようにな
る。6 is a model diagram of FIG. 4, and FIG. 8 is a schematic diagram of FIG. 4. In FIG. damping force, cd is the damping force of the second diaphragm 17, mc is the quality ii due to the liquid mass in the first diaphragm 14 and the diaphragm 20, md is the second diaphragm 1
The mass due to the liquid mass in 7 and the diaphragm 22, kc
is the rigidity of the diaphragm 20, and kd is the rigidity of the diaphragm 22. By appropriately setting the damping force, mass, and rigidity, the characteristics of the vibration isolator become as shown in FIG. 7.
第７図において実線が減衰力の変移を示し、鎖線が振動
伝達力の変移を示している。ＩＶはエンジンのアイドリ
ング振動域である。このような特性をもつ防振装置の５
目いは、異なる周波数において減衰力のピークを発生さ
せて、例えば、エンジンの上下振動である］０ＩＩｚ周
辺、ステアリング共振である３ＯＩＩｚ周辺における減
衰力を増大させ、且つ通常のアイドリング振動域ＩＶで
の振動伝達力低下をはかることにある。この図では、減
衰力が右側のピークに至るよりも少し小さい周波数の振
動域、即ちアイドリング振動ｊｇｉＩＶで振動伝達力が
低下しており、目、つ１ＯＩＩｚ及び３０ ＩＩＺ付近
で減衰力が増大していて、前記狙いを達成している。か
がる狙いの達成は、この実施例が流体主室１９に対して
、相互に独立した２つの副次室２１，２３と、各絞り１
４．１７と、各ダイヤフラム２０，２２とを備え、絞り
１４．１７の各減衰力とダイヤフラム２０．２２の各剛
性とを、夫々相違させているからである。In FIG. 7, the solid line shows the change in damping force, and the chain line shows the change in vibration transmission force. IV is the idling vibration range of the engine. 5 types of vibration isolators with such characteristics
The aim is to generate damping force peaks at different frequencies, for example, to increase the damping force around 0IIz, which is the vertical vibration of the engine, and around 3OIIz, which is the steering resonance, and to increase the damping force in the normal idling vibration range IV. The purpose is to reduce the vibration transmission force. In this figure, the vibration transmission force decreases in a frequency range slightly lower than that where the damping force reaches its peak on the right side, that is, the idling vibration jgiIV, and the damping force increases near 1OIIz and 30IIZ. The above aim has been achieved. To achieve this goal, this embodiment has two mutually independent sub-chambers 21 and 23 and each aperture 1 for the main fluid chamber 19.
4.17 and diaphragms 20, 22, and the damping force of the aperture 14.17 and the rigidity of the diaphragm 20.22 are made different.
第９図は、本発明の第２実施例を示す図であり、第１絞
り１４として、仕切板１３に固定した筒体を用い、且つ
仕切板１３に連通孔２９を開設して、これを介して流体
主室１９七第１流体副次室２１とを連通し、仕切板１３
の両面に弁体３０．３１を配置して両弁体３０．３１を
連結した一ヒ、弁体３０．３１と仕切板１３との間に隙
間をおいて、枠体１１に高周波微振幅の振動が人力され
たときには、連通孔２９を介して液体が流体主室１９と
第１流体副次室２１との間で自在に移動するように構成
した。FIG. 9 is a diagram showing a second embodiment of the present invention, in which a cylindrical body fixed to the partition plate 13 is used as the first diaphragm 14, and a communication hole 29 is opened in the partition plate 13. The fluid main chamber 197 communicates with the first fluid subchamber 21 through the partition plate 13.
The valve body 30.31 is arranged on both sides of the valve body 30.31, and the two valve bodies 30.31 are connected.A gap is provided between the valve body 30.31 and the partition plate 13, and a high frequency fine amplitude wave is applied to the frame body 11. When vibration is applied manually, the liquid is configured to freely move between the main fluid chamber 19 and the first sub-fluid chamber 21 via the communication hole 29.
これにより、前記高周波微振動の入力時には、ｌ＆体の
前記移動により、液体が流体主室１９に閉し込められる
ことがないから、ゴム状弾性体１８の伸縮が抵抗なく行
われ、その結果ゴム状弾性体１８の伸縮により高周波微
振動が吸収される。また低周波の振動が入力されたとき
には、仕切板１３の低周波振動により、弁体３０．３１
のいずれかが連通孔２９を閉塞するため、液体は第１絞
り１４を介して移動して、前記第１実施例と同様に１辰
動が減衰される。As a result, when the high-frequency micro-vibration is input, the liquid is not trapped in the main fluid chamber 19 due to the movement of the l& body, so the rubber-like elastic body 18 expands and contracts without resistance, and as a result, the rubber-like elastic body 18 expands and contracts without resistance. High frequency micro vibrations are absorbed by the expansion and contraction of the shaped elastic body 18. Further, when low frequency vibration is input, the low frequency vibration of the partition plate 13 causes the valve body 30.31 to
Since either of them closes the communication hole 29, the liquid moves through the first restrictor 14, and one rotational movement is attenuated as in the first embodiment.
また、補助枠Ｉ５の外周に、ゴム状弾性体Ｉ８と一体の
ゴム状弾性体３３が接着されていて、周辺機器との（ｈ
撃吸収をするようにしである。他の構成及び作用は、第
１実施例と同一である。Further, a rubber-like elastic body 33 integrated with the rubber-like elastic body I8 is adhered to the outer periphery of the auxiliary frame I5, and a
It is designed to absorb shock. Other configurations and operations are the same as in the first embodiment.
第１Ｏ図は、この発明の第３実施例のモデル図であり、
第１実施例の枠体１１．１２を延長屈折させ、且つ枠体
１１側に、仕切板３４と第３絞り３５と第３流体副次室
３６とダイヤフラム３７とを追加してこれらの合計を３
組とした例である。FIG. 1O is a model diagram of a third embodiment of the present invention,
The frames 11 and 12 of the first embodiment are extended and bent, and a partition plate 34, a third diaphragm 35, a third fluid subchamber 36, and a diaphragm 37 are added to the frame 11 side. 3
This is an example of a pair.
そして、この第３絹により、例えば５１１ｚ程度の振１
動を減衰するようにしておくと、自動車の乗り心地を悪
化させる振動をも減衰してこれを改善することができる
。他の構成及び作用は、前記第１実施例と同一である。If the third silk is used to attenuate vibrations of, for example, about 511z, it is possible to attenuate and improve the vibrations that worsen the ride comfort of the automobile. The other configurations and operations are the same as those of the first embodiment.
以上説明したように、本発明によれば、流体主室に絞り
を介して連続する流体副次室を、流体主室に対して複数
形成した。このため、複数の流体副次室が相′１：ｆに
独立して形成され、夫々が絞りを介して流体主室に連通
しているから、各絞り及び流体副次室によりもたらされ
る減衰力が、相互に大きな影響を与えることがない。こ
のため、複数用れる減衰力のピークを、減衰しようとす
る振動域に適応させて設定することが可能となったから
、各種周波数の振動入力を悉く減衰することができる効
果がある。As described above, according to the present invention, a plurality of fluid sub-chambers which are continuous with the fluid main chamber via the throttle are formed with respect to the fluid main chamber. For this reason, since a plurality of fluid sub-chambers are formed independently in phase '1:f, and each communicates with the fluid main chamber via a throttle, the damping force provided by each throttle and fluid sub-chamber is However, they do not significantly influence each other. For this reason, it has become possible to set the peaks of the plurality of damping forces to be applied to the vibration range to be damped, so that it is possible to attenuate all vibration inputs of various frequencies.
第１図は、従来例の断面図、第２図は、従来例の振動伝
達力と減衰力との特性を示すグラフ、第３図は、第１図
の模式図、第４図は、本発明の第１実施例を示す断面図
、第５図は、第４図の■−Ｖ線断面拡大図、第６図は、
第４図のモデル図、第７図は、第１実施例の振動伝達力
と減衰力との特性を示すグラフ、第８図は、第４図の模
式図、第９図は、第２実施例の断面図、第１０図は、第
３実施例のモデル図である。
１１・・・振動体側の枠体、】２・・・支持体側の枠体
、１３，１６．３４・・・仕切板、１４゜１７．３５・
・・絞り、１５・・・補助枠、１８・・・ゴム状弾性体
、１９・・・流体主室、２０゜２２．３７・・・ダイヤ
フラム、２１，２３．３６・・・流体副次室、２４．２
６・・・空気室特許出願人 日産自動車株式会社
代理人 弁理士 森 哲也
代理人 弁理士 内藤 嘉昭
代理人 弁理士 清水 正
代理人 弁理士 掘出 信是
ｔFig. 1 is a sectional view of the conventional example, Fig. 2 is a graph showing the characteristics of vibration transmission force and damping force of the conventional example, Fig. 3 is a schematic diagram of Fig. 1, and Fig. 4 is a graph showing the characteristics of the vibration transmission force and damping force of the conventional example. A cross-sectional view showing the first embodiment of the invention, FIG. 5 is an enlarged cross-sectional view taken along the line ■-V in FIG. 4, and FIG.
Figure 4 is a model diagram, Figure 7 is a graph showing the characteristics of the vibration transmission force and damping force of the first embodiment, Figure 8 is a schematic diagram of Figure 4, and Figure 9 is a graph showing the characteristics of the vibration transmission force and damping force of the first embodiment. An example cross-sectional view, FIG. 10, is a model diagram of the third embodiment. 11... Frame on the vibrating body side, ]2... Frame on the support side, 13, 16.34... Partition plate, 14° 17.35.
... Diaphragm, 15... Auxiliary frame, 18... Rubber-like elastic body, 19... Fluid main chamber, 20°22.37... Diaphragm, 21, 23.36... Fluid sub-chamber , 24.2
6...Air chamber patent applicant Nissan Motor Co., Ltd. Agent Patent attorney Tetsuya Mori Agent Patent attorney Yoshiaki Naito Patent attorney Shimizu Masaru Agent Patent attorney Nobukoro Hide t
Claims (1)
対移動により内部の流体主室の容積を変化させるゴム状
弾性体を配置し、前記流体主室には、当該流体主室の容
積変化に対応して容積変化する流体副次室を、何れかの
枠体側に支持される絞りを介して連結して、絞りを介し
ての流体主室と流体副次室との間の流体の移動により振
動入力を減衰させる流体入り防振装置において、前記流
体副次室を、流体主室に対して複数形成したことを特徴
とする流体入り防振装置。A rubber-like elastic body is disposed between the frame on the vibrating body side and the frame on the support body side, and changes the volume of the internal fluid main chamber by relative movement of both frames, and the fluid main chamber contains the fluid. A secondary fluid chamber whose volume changes in response to a change in the volume of the main chamber is connected via a restrictor supported on either frame side, and the main fluid chamber and the secondary fluid chamber are connected via the restrictor. A fluid-filled vibration isolator that damps vibration input by movement of fluid between the fluid-filled vibration isolators, characterized in that a plurality of the fluid sub-chambers are formed with respect to the fluid main chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1173184A JPS60155029A (en) | 1984-01-25 | 1984-01-25 | Vibration isolating device containing fluid |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1173184A JPS60155029A (en) | 1984-01-25 | 1984-01-25 | Vibration isolating device containing fluid |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60155029A true JPS60155029A (en) | 1985-08-14 |
| JPH0247613B2 JPH0247613B2 (en) | 1990-10-22 |
Family
ID=11786172
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1173184A Granted JPS60155029A (en) | 1984-01-25 | 1984-01-25 | Vibration isolating device containing fluid |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60155029A (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60179541A (en) * | 1984-02-27 | 1985-09-13 | Nissan Motor Co Ltd | Liquid charged power unit mount device |
| JPS6323041A (en) * | 1986-07-16 | 1988-01-30 | Honda Motor Co Ltd | Fluid seal type vibration proofing device |
| JPS6366643U (en) * | 1986-10-22 | 1988-05-06 | ||
| FR2617930A1 (en) * | 1987-07-07 | 1989-01-13 | Peugeot | HYDROELASTIC SUPPORT, IN PARTICULAR FOR PROVIDING THE SUSPENSION OF AN ENGINE IN A VEHICLE |
| US4856750A (en) * | 1987-04-13 | 1989-08-15 | Automobiles Peugeot | Hydroelastic support, in particular for the suspension of a vehicle engine |
| US4871150A (en) * | 1987-01-20 | 1989-10-03 | Automobiles Peugeot | Elastically yieldable support in particular for the suspension of a vehicle engine |
| US4880215A (en) * | 1988-08-05 | 1989-11-14 | Tokai Rubber Industries, Ltd. | Fluid-filled elastic mounting structure |
| US4896867A (en) * | 1987-02-07 | 1990-01-30 | Boge Ag | Hydraulically damping elastic bearing |
| US4971300A (en) * | 1986-04-05 | 1990-11-20 | Firma Carl Freudenberg | Motor mount having improved hydraulic damping |
| FR2690961A1 (en) * | 1992-05-07 | 1993-11-12 | Hutchinson | Improvements to hydraulic anti-vibration devices. |
| US5433421A (en) * | 1991-07-08 | 1995-07-18 | Bridgestone Corporation | Vibration isolating apparatus |
| KR20190022022A (en) * | 2017-08-25 | 2019-03-06 | 현대자동차주식회사 | Hydraulic engine mount |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60132144A (en) * | 1983-12-19 | 1985-07-15 | Bridgestone Corp | Vibration isolator |
| JPS60139941A (en) * | 1983-12-28 | 1985-07-24 | Bridgestone Corp | Vibration isolator |
-
1984
- 1984-01-25 JP JP1173184A patent/JPS60155029A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60132144A (en) * | 1983-12-19 | 1985-07-15 | Bridgestone Corp | Vibration isolator |
| JPS60139941A (en) * | 1983-12-28 | 1985-07-24 | Bridgestone Corp | Vibration isolator |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60179541A (en) * | 1984-02-27 | 1985-09-13 | Nissan Motor Co Ltd | Liquid charged power unit mount device |
| US4971300A (en) * | 1986-04-05 | 1990-11-20 | Firma Carl Freudenberg | Motor mount having improved hydraulic damping |
| JPS6323041A (en) * | 1986-07-16 | 1988-01-30 | Honda Motor Co Ltd | Fluid seal type vibration proofing device |
| JPS6366643U (en) * | 1986-10-22 | 1988-05-06 | ||
| US4871150A (en) * | 1987-01-20 | 1989-10-03 | Automobiles Peugeot | Elastically yieldable support in particular for the suspension of a vehicle engine |
| US4896867A (en) * | 1987-02-07 | 1990-01-30 | Boge Ag | Hydraulically damping elastic bearing |
| US4856750A (en) * | 1987-04-13 | 1989-08-15 | Automobiles Peugeot | Hydroelastic support, in particular for the suspension of a vehicle engine |
| FR2617930A1 (en) * | 1987-07-07 | 1989-01-13 | Peugeot | HYDROELASTIC SUPPORT, IN PARTICULAR FOR PROVIDING THE SUSPENSION OF AN ENGINE IN A VEHICLE |
| US4880215A (en) * | 1988-08-05 | 1989-11-14 | Tokai Rubber Industries, Ltd. | Fluid-filled elastic mounting structure |
| US5433421A (en) * | 1991-07-08 | 1995-07-18 | Bridgestone Corporation | Vibration isolating apparatus |
| FR2690961A1 (en) * | 1992-05-07 | 1993-11-12 | Hutchinson | Improvements to hydraulic anti-vibration devices. |
| KR20190022022A (en) * | 2017-08-25 | 2019-03-06 | 현대자동차주식회사 | Hydraulic engine mount |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0247613B2 (en) | 1990-10-22 |
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