JPS59190531A - Engine mount with fluid inside - Google Patents
Engine mount with fluid insideInfo
- Publication number
- JPS59190531A JPS59190531A JP6179583A JP6179583A JPS59190531A JP S59190531 A JPS59190531 A JP S59190531A JP 6179583 A JP6179583 A JP 6179583A JP 6179583 A JP6179583 A JP 6179583A JP S59190531 A JPS59190531 A JP S59190531A
- Authority
- JP
- Japan
- Prior art keywords
- orifice
- fluid
- damping force
- partition plate
- engine mount
- 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
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】
本発明は流体入りエンジンマウントの改良に係り、特に
低周波域から高周綜域に亘る広い周波数帯域に及んで大
きなダンピングカ全得るようにした流体入りエンジンマ
ウントに関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a fluid-filled engine mount, and particularly to a fluid-filled engine mount that can obtain a large damping force over a wide frequency range from a low frequency range to a high frequency range.
エンジンに連結される数句部材と、車体フレームに連結
はれ、エンジンをマウントするベース部材とを振動の伝
達により弾性変形可能々る弾性部材で結合して内部に室
を形成し、該室内に液体、又は気体等の流体を封入し、
更にベース部材にダイヤフラムを付設し、本体の流体室
とダイヤフラム室とをオリフィスにより連通して成り、
該オリアイスを通る流体の移動により振動全減衰する流
体入りエンジンマウントは既に知られている。An internal chamber is formed by connecting a component connected to the engine and a base component that is connected to the vehicle body frame and mounts the engine using an elastic member that can be elastically deformed by transmitting vibrations. Encloses fluid such as liquid or gas,
Furthermore, a diaphragm is attached to the base member, and the fluid chamber of the main body and the diaphragm chamber are communicated through an orifice.
Fluid-filled engine mounts are already known in which vibrations are totally damped by movement of fluid through the oriice.
例えば第８図に示される如く車体フ詞−ムに固定σれる
ベース部材４１０は、截頭円錐体４１１の上部内周に仕
切板４１２を横設形成するとともに、下部外周には取付
フランジ４１４を形成して成り、仕切板４１２の中央に
はオリフィス４１３が穿設され、又取付フランジ４１４
には車体フレームへの取付孔４１γ・・・が穿設されて
いる。For example, as shown in FIG. 8, a base member 410 fixed to a vehicle body frame has a truncated cone body 411 with a partition plate 412 horizontally formed on the upper inner periphery and a mounting flange 414 on the lower outer periphery. An orifice 413 is bored in the center of the partition plate 412, and a mounting flange 414 is formed.
Attachment holes 41γ to the vehicle body frame are bored in the holes 41γ.
−万エンジンに連結される円板状の取付部材４２０の外
周には下方に開放はれ、」二記載頭円錐体４１１よジも
充分に大径なる截頭円錐体４２１がその上部でもって固
着一体化されており、この取付部材４２０の上面の中心
にはエンジン取付ボルト４２２が上方に突出して固設さ
れている。- A truncated conical body 421 which is opened downwardly on the outer periphery of a disk-shaped mounting member 420 connected to an engine and whose diameter is sufficiently large is fixed at its upper part. An engine mounting bolt 422 is fixed to the center of the upper surface of the mounting member 420 so as to protrude upward.
斯かるベース部材４１０を構成する截頭円錐体４１１の
外周に逆アンブンラ状の弾性部材４３０であるシェアス
プリングゴムの内周全焼料け、更にこのシェアスプリン
グゴム４３０の外周に取付部材４２０の周縁下面及び截
頭円錐体４２１の内周を焼付け、これによυベース部相
４１０の仕切板４１２、シェアスプリングゴム４３０及
び取・Ｎ部拐４２０により本体の流体室４０２が形成さ
れる。On the outer periphery of the truncated conical body 411 constituting the base member 410, the inner periphery of a shear spring rubber, which is an inverted umbrella-like elastic member 430, is completely burnt out, and further, on the outer periphery of this shear spring rubber 430, a lower periphery of the mounting member 420 is coated. Then, the inner periphery of the truncated cone 421 is baked, whereby the fluid chamber 402 of the main body is formed by the partition plate 412 of the υ base part 410, the shear spring rubber 430, and the groove 420.
又ベース部ＩＪ４１０の截頭円錐体４１１の下部内周に
はダイヤフラム４７０がその開局でもって固着一体化σ
れ、これにより斯かる截頭円錐体４１１内にはダイヤフ
ラム室４７１が形成される。Also, a diaphragm 470 is fixedly integrated with the diaphragm 470 on the lower inner periphery of the truncated cone 411 of the base portion IJ410.
As a result, a diaphragm chamber 471 is formed within the truncated cone 411.
斯くして構成された流体入りエンジンマウント４０１の
本体の流体室４０２及びダイヤフラム室４７１内に液体
、又は気体等の流体（図示では液体）を充填して封入す
る。The fluid chamber 402 and diaphragm chamber 471 of the main body of the fluid-filled engine mount 401 configured in this way are filled with a fluid such as liquid or gas (liquid in the illustration) and sealed therein.
以上従来の流体入りエンジンマウント４０１によれば、
オリフィス４１３が固定であるため、その周波数−損失
係数（ｔａｎδ）特性線図を表せば第９図の如く々す、
損失係数、即ちダンピングのビータの周波数帯域が比較
的狭い。According to the conventional fluid-filled engine mount 401 as described above,
Since the orifice 413 is fixed, its frequency-loss coefficient (tan δ) characteristic diagram is as shown in Fig. 9.
The frequency band of the loss factor, that is, the damping beater, is relatively narrow.
このため、低周波帯域でのダンピング力を大きくとるよ
うにオリフィス４１３の径を小てくすると、高周波帯域
でのダンピング力が小さくなる。Therefore, if the diameter of the orifice 413 is made small to increase the damping force in the low frequency band, the damping force in the high frequency band will be reduced.
この特性を第１０図において、実線で示した。This characteristic is shown by a solid line in FIG.
一方上記と逆に高周波帯域でのダンピング力を大きくと
るようにオリフィス４１３の径を大きくすると、反対に
低周波帯域でのダンピング力が小びくなる。この特性全
同図中破線で示した。On the other hand, if the diameter of the orifice 413 is increased to increase the damping force in the high frequency band, contrary to the above, the damping force in the low frequency band will decrease. All of these characteristics are shown by broken lines in the figure.
従って低周波域から高周波域に亘っての広い周波数帯域
に及ぶ太き々ダンピング力’ｘ Ｔ８ることかできなか
った。Therefore, it was only possible to increase the damping force to a large extent over a wide frequency band from the low frequency range to the high frequency range.
本発明は以上の実情に鑑みて成されたもので、その目的
とする処は、低周波域から高周波域に亘る広い周波数帯
域に及んで大きなダンピング力を得るようにし、ダンピ
ング特性の向上ｔａつた流体入りエンジンマウン）ｋ提
供するにある。The present invention has been made in view of the above circumstances, and its purpose is to obtain a large damping force over a wide frequency range from low frequency range to high frequency range, and to improve damping characteristics. Fluid-filled engine mounts are provided.
斯かる目的を達成すべく本発明は、流体入りエンジンマ
ウントのダイヤフラム室を含む流体室内にオリフィスを
直列に複数段設け、流体室を少なくとも３室に画成する
とともに、オリフィス全形成した各仕切板のうち少々く
とも１枚を前記弾性部材に［Ｇ接支持せしめる等して少
なくとも１個のオリフィスを弾性支持して可動としたこ
とを要旨としている。In order to achieve such an object, the present invention provides a plurality of orifices in series in a fluid chamber including a diaphragm chamber of a fluid-filled engine mount, defines the fluid chamber into at least three chambers, and divides each partition plate in which the orifice is completely formed. The gist is that at least one of the orifices is elastically supported and movable by supporting the elastic member in G contact.
以下に本発明の実施例を添付図面に基づいて詳述する。Embodiments of the present invention will be described in detail below with reference to the accompanying drawings.
第１図は第１実施例に係る流体入りエンジンマウントの
中央縦断面図である。FIG. 1 is a central vertical sectional view of a fluid-filled engine mount according to a first embodiment.
第１実施例に係る流体入りエンジンマウント１の本体は
、車体フレームに固定されるベース部材１０と、エンジ
ンに連結される数句部材２０と、これらベース部材１０
と取付部材２０とを結合する逆アンブレラ状及びアンブ
レラ状の上下２段の弾性部材３０．４０とから成ってお
り、ベース部材１０にはダイヤスラム７０が付設てれて
いる。The main body of the fluid-filled engine mount 1 according to the first embodiment includes a base member 10 fixed to the vehicle body frame, a coupler member 20 connected to the engine, and these base members 10.
The base member 10 has a diamond slam 70 attached thereto.
即ちベース部材１０は、截頭円錐体１１の上部内周に仕
切板１２を横設形成するとともに、下部外周に形成した
７ランジ１４に截頭逆円錐体１５の下部内周をカシメ結
合して溶接等により該截頭逆円錐体１５を固着一体化し
、更にこの截頭逆円錐体１５の上部外周には取付フラン
ジ１６を形成して成り、仕切板１２の中央にオリフィス
１３が穿設され、又取付７ランジ１６には車体フレーム
への取付孔１７・・・が穿設されている。That is, the base member 10 has a partition plate 12 horizontally formed on the upper inner periphery of a truncated cone 11, and the lower inner periphery of an inverted truncated cone 15 is caulked to seven flange 14 formed on the lower outer periphery. The truncated inverted conical body 15 is fixed and integrated by welding or the like, and a mounting flange 16 is formed on the upper outer periphery of the truncated inverted conical body 15, and an orifice 13 is bored in the center of the partition plate 12. Further, the mounting 7 langes 16 are provided with mounting holes 17 for connecting to the vehicle body frame.
一方円板状の数句部材２０の外周には上記截頭逆円錐体
１５と略々同径なる截頭円錐体２１がその上部内周でカ
シメ結合して溶接等により固着一体化されており、この
取付部材２０の上面の中心にはエンジン取付ボルト２２
が上方に突出して固設されている。On the other hand, a truncated cone 21 having approximately the same diameter as the truncated inverted cone 15 is attached to the outer periphery of the disc-shaped shuku member 20 by caulking the upper inner periphery of the inverted truncated cone 15 and fixedly integrated with the truncated cone 21 by welding or the like. At the center of the upper surface of this mounting member 20 is an engine mounting bolt 22.
is fixed and protrudes upward.
斯かるベース部材１０を構成する截頭逆円錐体１５の内
周にアンブレラ状の弾性部材４０であるシェアスプリン
グゴムの外周全焼付け、更にこのシェアスプリングゴム
４０の上面に円板状の新た々仕切板５０の下面を焼付け
る。この仕切板５０の中央にはオリフィス５１が穿設さ
れている。The outer periphery of shear spring rubber, which is an umbrella-shaped elastic member 40, is completely baked on the inner periphery of the truncated inverted conical body 15 constituting the base member 10, and a new disc-shaped partition is added to the upper surface of this shear spring rubber 40. The bottom surface of the plate 50 is baked. An orifice 51 is bored in the center of this partition plate 50.
そしてこの仕切板５０の上面に逆アンプレジ状の弾性部
材３０であるシェアスプリングゴムｆ７）下面を焼付け
、更にこのシェアスプリングゴム３０の外周に取付部材
２０の周縁下面及び截頭円錐体２１の内周を焼イて］け
る。Then, the lower surface of the shear spring rubber f7), which is the elastic member 30 in the shape of an inverted ampule, is baked on the upper surface of the partition plate 50, and the lower surface of the peripheral edge of the mounting member 20 and the inner periphery of the truncated cone body 21 are attached to the outer periphery of the shear spring rubber 30. to roast].
尚ベースＴ−１Ｓ相１０と取付部月２０及び新た々仕切
板５０幻回心的に組イ」けられている。The base T-1S phase 10, the mounting part 20, and the new partition plate 50 have been assembled in a phantom manner.
斯くしてエンジンマウント１の本体内には、上下２段の
シェアスプリングゴム３０，４０にサンドインチされ／
こ仕切板５０によｐ上から第１流体室２、第２流体室３
が画成される。In this way, the engine mount 1 is sandwiched between upper and lower shear spring rubbers 30 and 40 in two stages.
The first fluid chamber 2 and the second fluid chamber 3 are separated from the top by the partition plate 50.
is defined.
又ベース部′）ｌ′Ａ１０の截頭円錐体１１の下部外周
に形成したフランジ１４の下面にｉｔダイヤフラム７０
の周縁が重ね合わされ、前記截頭逆円錐体１５の固着一
体化と同時にこのダイヤフラム７０も固着一体化これ、
これにより截頭円鮪：体１１内にはダイヤノラム室７１
が形成される。In addition, an IT diaphragm 70 is attached to the lower surface of the flange 14 formed on the lower outer periphery of the truncated conical body 11 of the base part')l'A10.
The circumferential edges of the diaphragm 70 are overlapped, and at the same time as the truncated inverted cone body 15 is fixed and integrated, the diaphragm 70 is also fixed and integrated.
As a result, the truncated round tuna: the diamondorum chamber 71 inside the body 11
is formed.
以上の如くして構成された流体入りエンジンマウント１
の第１及び第２の流体室２，３並びにダイヤフラム呈７
１内に液体、又は気体等の流体（図示では液体）を充填
して封入する。Fluid-filled engine mount 1 configured as above
the first and second fluid chambers 2, 3 and the diaphragm 7
1 is filled and sealed with a fluid such as liquid or gas (liquid in the illustration).
而してベース部（２１０の仕切板１２に形成した固定の
オリフィス１３の他に、上下２段のシェアスプリングゴ
ム３０．４０にサンドインチされて弾性支持てれた仕切
板５０に形成した可動外るオリフィス５１を設けたブヒ
め、これら２段の１宜列に配設された固定オリフィス１
３及び可動メリフイス５１により下記の優れた作用効果
全発揮することができる。In addition to the fixed orifice 13 formed in the partition plate 12 of the base part (210), there is also a movable orifice formed in the partition plate 50 which is sandwiched and elastically supported by upper and lower two stages of shear spring rubber 30 and 40. Fixed orifices 1 are arranged in the first row of these two stages.
3 and the movable merifice 51, all of the excellent functions and effects described below can be exhibited.
ここで２段のオリフィス１３．５１の径を異ならせたり
、２段のシェアスプリングゴム３０，４０の弾性を異な
らせたりすることにより一方のオリフィス、例えば可動
オリフィス５１ケ低周波域側に損失係数（ｔａｎδ）、
即ちダンピングのピークがくるように設定し、他方の固
定オリフィス１３を高周波域１０１１にダンピングのピ
ークがくるように設定する。Here, by making the diameters of the two-stage orifices 13 and 51 different, and by making the elasticity of the two-stage shear spring rubbers 30 and 40 different, one orifice, for example, the movable orifice 51, has a loss coefficient on the low frequency side. (tanδ),
That is, it is set so that the damping peak occurs, and the other fixed orifice 13 is set so that the damping peak occurs in the high frequency range 1011.
次にその作用を述べる。Next, its effect will be described.
先ず低周波域にあっては、可動オリフィス５１により大
きなダンピング力が得られ、この時、固定オリフィス１
３によっても小さなダンピング力が得られている。First, in the low frequency range, a large damping force is obtained by the movable orifice 51, and at this time, the fixed orifice 1
3 also provides a small damping force.
更に中周波域に移行すると、可動オリフィス５１による
ダンピング力が小さくなり、これに代わって固定オリフ
ィス１３によるダンピング力が大きく々るため、これら
が相俟って適度に大きなダンピング力が得られている。Furthermore, as the frequency shifts to the medium frequency range, the damping force by the movable orifice 51 becomes smaller, and in its place, the damping force by the fixed orifice 13 increases, so that a moderately large damping force is obtained by combining these factors. .
そして高周波域に移行すると、可動オリフィス５１によ
るダンピング力は小さくなるが、逆に固定オリフィス１
３により大きなターンビングカが得られている。Then, when moving to a high frequency range, the damping force by the movable orifice 51 becomes smaller, but conversely, the damping force by the fixed orifice 1 becomes smaller.
3, a large turning force is obtained.
従って本発明に係る流体入りエンジンマウント１によれ
姓ｊ１第５図に示される通、！ンビークは若干減少する
が、低周波域から高周波域に亘っての広い周波数帯域に
及ぶ大きなダンピング力を得ることができ、ダンピング
特性の向上を達成することができる。Therefore, according to the fluid-filled engine mount 1 according to the present invention, the name j1 shown in FIG. Although the peak beak is slightly reduced, it is possible to obtain a large damping force over a wide frequency band from a low frequency region to a high frequency region, and it is possible to achieve an improvement in damping characteristics.
尚本実施例では、例えは可動オリフィスを低周波域用に
、固定オリフィスを高周波域用として設定し、その作用
を述べたが、勿論設定の条件を反対にしても良い。In this embodiment, the movable orifice is set for the low frequency range and the fixed orifice is set for the high frequency range, and the operation thereof is described, but of course, the setting conditions may be reversed.
ところで以上の実施例においては、可動オリフィスを２
段のシェアスプリングゴム間に介装して弾性支持したが
、以下の如く構成しても同様の作用効果を奏することが
できる。By the way, in the above embodiment, there are two movable orifices.
Although the elastic support is provided by interposing the shear spring rubber between the stages, the same effect can be obtained by using the following configuration.
第２図に示されるように第２実施例に係る流体入Ｑエン
ジンマウント１０１’ｌ：構成するベース部材１１０け
、截頭円錐体１１１の上部内周に仕切板１１２を横設形
成するとともに、下部外周には数句フランジ１１４全形
成して成り、仕切板１１２の中央にはオリフィス１１３
が穿設されている。As shown in FIG. 2, a fluid-filled Q engine mount 101'l according to the second embodiment: a base member 110 is formed, and a partition plate 112 is horizontally formed on the upper inner periphery of a truncated cone 111; Several flanges 114 are formed on the outer periphery of the lower part, and an orifice 113 is formed in the center of the partition plate 112.
is drilled.
斯かるベース部材１１０を構成する截頭円錐体１１１の
外周に逆アンプＶう状のシェアスプリングゴム１３０の
内周を焼付け、更にこのシェアスプリングゴム１３０の
外周に前記と同様の数句部材１２０の周縁下面及び截頭
円錐体１２１の内周を焼付ける。The inner periphery of a shear spring rubber 130 in the shape of an inverse amplifier V is baked onto the outer periphery of the truncated conical body 111 constituting the base member 110, and the same numeral member 120 as described above is attached to the outer periphery of this shear spring rubber 130. The lower surface of the periphery and the inner periphery of the truncated cone 121 are baked.
又ベース部材１１０の取付フランジ１１４の内周寄り下
面には円筒体１１８が溶接等により固着一体化され、こ
の円筒体１１８の下部内周にダイヤフラム１７０の外周
を固着一体化する。A cylindrical body 118 is fixedly integrated with the lower surface of the mounting flange 114 of the base member 110 near the inner periphery by welding or the like, and the outer periphery of the diaphragm 170 is fixedly integrated with the lower inner periphery of this cylindrical body 118.
そして本第２実施例では、シェアスプリングゴム１３０
の中間部内周に環状溝１３１を形成し、該環状溝１３１
内に円板状の新たな仕切板１５０の外周を嵌着して焼付
ける。この仕切板１５０の中央にはオリフィス１５１が
穿設されている。In the second embodiment, the shear spring rubber 130
An annular groove 131 is formed on the inner periphery of the intermediate portion of the annular groove 131.
The outer periphery of a new disc-shaped partition plate 150 is fitted inside and baked. An orifice 151 is bored in the center of this partition plate 150.
斯くしてエンジンマウント１０１０本体内には、シェア
スプリングゴム１３０の中間部内周にて支持され／４仕
切板１５０により上方から第１流体室１０２、第２流体
室１０３が画成きれるとともに、当該エンジンマウント
１０１内には、ベース部材１１０の仕切板１１２に形成
した固定オリフィス１１３の他に、シェアスプリングゴ
ム１３０にて支持された仕切板１５０に形成した可動オ
リフィス１５１が直列に配設されることと々る。In this manner, inside the main body of the engine mount 1010, the first fluid chamber 102 and the second fluid chamber 103 are defined from above by the /4 partition plate 150 supported by the inner periphery of the intermediate portion of the shear spring rubber 130, and the engine Inside the mount 101, in addition to the fixed orifice 113 formed on the partition plate 112 of the base member 110, a movable orifice 151 formed on the partition plate 150 supported by the shear spring rubber 130 is arranged in series. That's it.
以上何れの実施例においても、可動オリフィスをエンジ
ンマウント本体の流体室内に配設したが、ダイヤフラム
至内に配設することも可能である。In all of the above embodiments, the movable orifice is disposed within the fluid chamber of the engine mount body, but it is also possible to dispose it within the diaphragm.
即ち第３図に示されるように第３実施例に係る流体入り
エンジンマウント２０１’ｚ構成するベース部材２１０
は、截頭円錐体２１１の上部内周に仕切板２１２ｔｌＪ
設形叛するとともに、下部外周には数句フランジ２１４
全形成して成り、仕切板２１２の中央にはオリフィス２
１３が穿設されている。That is, as shown in FIG. 3, a base member 210 constituting a fluid-filled engine mount 201'z according to the third embodiment
is a partition plate 212tlJ on the upper inner circumference of the truncated cone 211.
In addition to the shape, there are several flanges 214 on the lower outer periphery.
The partition plate 212 has an orifice 2 in the center.
13 are drilled.
斯かるベース部材２１０を構成する截頭円錐体２１１の
外周に前記と同様に逆アンブレラ状のシェアスプリング
ゴム２３０の内周を焼付け、更にこのシェアスプリング
ゴム２３０の外周に同じく数句部材２２０の周縁下面及
び截頭円錆、体２２１の内周を焼付ける。The inner periphery of the reverse umbrella-shaped shear spring rubber 230 is baked on the outer periphery of the truncated cone 211 constituting the base member 210 in the same manner as described above, and the outer periphery of the shear spring rubber 230 is also baked with the periphery of the cylindrical member 220. The lower surface, the truncated circular rust, and the inner periphery of the body 221 are baked.
そして本第３実施例では、ベース都月２１０の截頭円錐
体２１１の内周に円筒体２６１の外周全溶接等により固
着一体化するとともに、円筒体２６１の内周に環状のシ
ェアスプリングゴム２６０の外周を焼付け、更にこのシ
ェアスプリングゴム２６０の内周に上記より小径なる円
筒体２６２の外周全焼付ける。この小径なる円筒体２６
２の上部内周には新たな仕切板２６３が横設形成きれ、
該仕切板２６３の中央にはオリフィス２６４が穿設され
ている。In the third embodiment, the cylindrical body 261 is fixedly integrated with the inner periphery of the truncated cone 211 of the base 210 by welding the entire outer periphery of the cylindrical body 261, and an annular shear spring rubber 260 is attached to the inner periphery of the cylindrical body 261. The outer periphery of a cylindrical body 262 having a smaller diameter than the above is completely baked on the inner periphery of this shear spring rubber 260. This small diameter cylindrical body 26
A new partition plate 263 has been horizontally formed on the upper inner circumference of 2.
An orifice 264 is bored in the center of the partition plate 263.
尚ベース部材２１０の取付フランジ２１４の内周寄り下
面には、内方に開放せる断面コ牢形の環状取付片２１９
が形成され、この取付片２１９にダイヤフラム２７０の
外周を固着一体化する。Incidentally, on the lower surface of the mounting flange 214 of the base member 210 near the inner circumference, there is an annular mounting piece 219 with a cage-shaped cross section that opens inward.
is formed, and the outer periphery of the diaphragm 270 is fixedly integrated with this mounting piece 219.
斯くしてエンジンマウント２０１の本体内には、第１流
体室２０２が形成され、一方ベース部相２１０の截頭円
錐体２１１とダイヤフラム２７０とにより形成される流
体室内には、内外２重の円筒体２６１．２６２間に介装
した環状のシェアスプリングゴム２６０にて支持され７
’ｃ仕切板２６３により上方から第２流体室２０３、ダ
イヤフラム室２７１が１ｉｆｉｉ成されるとともに、当
該エンジンマウント２０１内には、ベース部材２１０の
仕切板２１２に形成した固定オリフィス２１３の他に、
シェアスプリングゴム２６０にて支持された仕切板２６
３に形成した可動オリフィス２６４が直列に配設される
こととなる。In this way, a first fluid chamber 202 is formed within the main body of the engine mount 201, while a fluid chamber formed by the truncated cone 211 of the base portion 210 and the diaphragm 270 has a double inner and outer cylinder. It is supported by an annular shear spring rubber 260 interposed between bodies 261 and 262.
A second fluid chamber 203 and a diaphragm chamber 271 are formed from above by the partition plate 263, and inside the engine mount 201, in addition to the fixed orifice 213 formed in the partition plate 212 of the base member 210,
Partition plate 26 supported by shear spring rubber 260
The movable orifices 264 formed in No. 3 are arranged in series.
以上３種の実施例では、何れも一方のオリフィスを従来
と同様に固定とし、他方を可動オリフィスとして構成し
たが、両方ともに可動オリフィスとして構成することも
可能である。In each of the three embodiments described above, one of the orifices is fixed as in the prior art and the other is configured as a movable orifice, but it is also possible to configure both as movable orifices.
即ち第４図に示はれるように第４実施例に係る流体入り
エンジンマウン）３０１’に構成するベース部材３１０
は、截頭逆円錐体°３１５の」二部外周に取付７ランジ
３１６を形成して成り、斯かるベース部材３１０の截頭
逆円錐体３１５の内周に第１図と同様のアンブレラ状の
シェアスプリングゴム３４０の外周を焼付け、更にこの
シェアスプリングゴム３４０の上面に円板状の第１の仕
切板３５０の下面を焼付ける。この仕切板３５０の中央
にはオリフィス３５１が穿設されている。That is, as shown in FIG. 4, a base member 310 configured in a fluid-filled engine mount 301' according to the fourth embodiment.
A mounting flange 316 is formed on the outer periphery of the two parts of the truncated inverted conical body 315, and an umbrella-shaped flange 316 similar to that shown in FIG. The outer periphery of the shear spring rubber 340 is baked, and the lower surface of the disk-shaped first partition plate 350 is further baked on the upper surface of the shear spring rubber 340. An orifice 351 is bored in the center of this partition plate 350.
そしてこの仕切板３５０の上面に逆アンブレラ状のシェ
アスプリングゴム３３０の下面全焼付け、更にこのシェ
アスプリングゴム３３０の外周に前記と同様に塩４１部
材３２０の周縁下面及び截頭円錐体３２１の内周全焼イ
ボける。Then, the lower surface of a reverse umbrella-shaped shear spring rubber 330 is completely baked on the upper surface of this partition plate 350, and the lower surface of the peripheral edge of the salt 41 member 320 and the inner periphery of the truncated cone body 321 are attached to the outer periphery of the shear spring rubber 330 in the same manner as described above. It's completely burnt and warts.
一方ベース部材３１０全構成する截頭逆円錐体３１５の
下部には、内方に開放せる断面コ字形の環状取付片３１
９が形成をれており、この取付片３１９を円筒体３６１
の上部外周に形成したフランジ３６２にカシメ結合して
溶接等により該円筒体３６１を固着一体化するとともに
、円筒体３６１の内周に第３図と同様の環状のシェアス
プリングゴム３６０の外周を焼付け、更にこのシェアス
プリングコム３６０の内周に上記より小径々る円筒体３
６３の外周全焼伺ける。この小径なる円筒体３６３の上
部内周には紀２の仕切板３６４が横設形成てれ、該仕切
板３６４の中央にはオリフィス３６５が穿設きれている
。On the other hand, at the bottom of the truncated inverted conical body 315 that constitutes the entire base member 310, there is an annular mounting piece 31 with a U-shaped cross section that opens inward.
9 is formed, and this mounting piece 319 is attached to the cylindrical body 361.
The cylindrical body 361 is fixedly integrated with the flange 362 formed on the upper outer periphery of the cylindrical body 361 by welding or the like, and the outer periphery of an annular shear spring rubber 360 similar to that shown in FIG. 3 is baked on the inner periphery of the cylindrical body 361. , Furthermore, a cylindrical body 3 having a smaller diameter than the above is attached to the inner circumference of this shear spring comb 360.
The outer periphery of 63 can be seen completely burnt down. A second partition plate 364 is horizontally formed on the upper inner periphery of this small-diameter cylindrical body 363, and an orifice 365 is bored in the center of the partition plate 364.
尚外側の円筒体３６１の上部外周に形成したフランジ３
６２の下面にはダイヤフラム３７０の周縁が重ね合わさ
れ、ベース部材３１０の截頭逆円り１１１体３′１５へ
の円筒体３６１の固九一体化と同時にこのダイヤフラム
３７０も固着一体化きれる。Furthermore, the flange 3 formed on the upper outer periphery of the outer cylindrical body 361
The periphery of a diaphragm 370 is superimposed on the lower surface of the diaphragm 370, and the diaphragm 370 can be fixed and integrated at the same time as the cylindrical body 361 is fixedly integrated with the truncated inverted circular body 3'15 of the base member 310.
斯くしてエンジンマウント３０１内には、上下２段のシ
ェアスプリングコム３３０，３４０にサンドインチきれ
た第１の仕切板３５０と、内外２重の円筒体３６１，３
６３間に介装した環状のシェアスプリングコム３６０に
て支持てれた第２の仕切板３６４とにより」−力から第
１流体室３０２、第２流体室３０３及びダイヤフラム室
３７１が画成づれるとともに、２段の可動オリフィス、
即ちともに弾性支持はれた第１及び第２の仕切板３５０
゜３６５が直列に配設されることとなる。Thus, inside the engine mount 301, there is a first partition plate 350 sandwiched between the upper and lower shear spring combs 330, 340, and the inner and outer double cylindrical bodies 361, 3.
A first fluid chamber 302, a second fluid chamber 303, and a diaphragm chamber 371 are defined by a second partition plate 364 supported by an annular shear spring comb 360 interposed between 63 and 63. Along with a two-stage movable orifice,
That is, the first and second partition plates 350 are both elastically supported.
365 are arranged in series.
次に以上の流体入りエンジンマウントの構成全第４実施
例を例にとって更に理論的に解析する。Next, the fourth embodiment of the above fluid-filled engine mount configuration will be further theoretically analyzed as an example.
先ず第４実施例の流体入りエンジンマウントの構造は第
６図に示すようにモデル化することができる。First, the structure of the fluid-filled engine mount of the fourth embodiment can be modeled as shown in FIG.
即ちエンジンＸと車体フレームＦとの間に介装される当
該エンジンマウン） ３０１ Ｂ、上段の逆アンブンラ
状シェアスプリングゴム３３０のバネ成分］＜ｚと、上
段の可動オリフィス３５１を弾性支持する上下２段のシ
ェアスプリングゴム３３０゜３４０のバネ成分１り３並
びに該オリフィス３５１での流体の質量流量ＣＩとが並
列に構成され、更に下段のアンプＶう状シェアスプリン
グゴム３４０のバネ成分に２と、下段の可動オリフィス
３ｓ５−を弾１生支持する環状シェアスプリングコム３
６０のバネ成分に４並びに該オリフィス３６５ての流体
の質量流量Ｃ２とが並列に構成てれ、これら前者の成分
と後者の成分とが直列をもって構成式れたものである。That is, the engine mount interposed between the engine The spring components 1 and 3 of the stage shear spring rubber 330 and 340 and the mass flow rate CI of the fluid at the orifice 351 are configured in parallel; An annular shear spring comb 3 that supports the lower movable orifice 3s5- for one bullet.
The spring component 60 and the mass flow rate C2 of the fluid through the orifice 365 are configured in parallel, and the former component and the latter component are configured in series.
断力・るモデルに基づく損失係数ｔａｎδ、即ちダンピ
ングは次式により算出される。The loss coefficient tan δ based on the shear force model, that is, damping, is calculated by the following equation.
イ刀 し、 ＵＪ二に＋］＜ｚｋ ３１＜ ４− ω
ｃｔｃ ２（ｋ １＋Ｌ＋）（ｋ ２＋ｋ ４）Ｕ２
−ω（ｃｘｋ２に４（ｋ１十に３）＋ｃｚｋ＋に３（ｋ
ｚ＋に４）］Ｕ３ ＝ ｋ３１＜４（ｌｕ ＋に２）−
ωｃ１ｃ２（ｋ１＋に２＋］＜３＋ｋｘ）ＴＪ４＝ω［
ｃｌに４（ｌｕ＋ｋＪ−に３） ＋ｃ２１＜３（ｋコ十
に２＋に４）：］面ここでωは振動周波数である。I sword, UJ second +] <zk 31< 4- ω
ctc 2(k 1+L+)(k 2+k 4)U2
-ω (4 for cxk2 (3 for k1) + 3 for czk+ (k
z+4)]U3=k31<4(lu+2)−
ωc1c2 (2+ to k1+]<3+kx)TJ4=ω[
4 for cl (3 for lu+kJ-) +c21<3 (4 for 2+ for k):] where ω is the vibration frequency.
そして各パラメーターとして
ｋｘ−２Ｘ１０ Ｎ７ｍ
ｋ２ ＝ ２Ｘ １０５ｒシ侃
に３ ＝ １．３２ Ｘ １ ０ ” Ｎ／ｍ］（４＝
１．３２ Ｘ １０ Ｎ／ｍＣ１＝ ３ Ｘ １０
Ｎｓ７’ｒｎ
ｃ２−０．３３３ Ｘ １０ ” Ｎｓ／ｙｎ全力え、
これによす皿δを上式から算出すると、第７図に示した
周波数−損失係数特性線図が得られる。And as each parameter kx-2X10N7m k2 = 2X 105r and 3 = 1.32
1.32 x 10 N/mC1= 3 x 10
Ns7'rn c2-0.333
If the disc δ is calculated from the above equation, the frequency-loss coefficient characteristic diagram shown in FIG. 7 is obtained.
従って本発明によれば、広い周波数帯域で大きなダンピ
ングが発生することが理論的にも裏付けられていること
が鹿角￥きれる。Therefore, according to the present invention, it can be concluded that it is theoretically supported that large damping occurs in a wide frequency band.
尚各実施例では、少なくとも１個の可動オリフィスを含
むオリフィス全直列に２段としたが、３段以上の多数段
とすることも可能である。In each embodiment, the orifices including at least one movable orifice are arranged in two stages in series, but it is also possible to have three or more stages.
以上の説明から明らかな如く本発明によれば、流体入り
エンジンマウントの流体室内にオリフィスを直列に複数
段設けるとともに、少々くとも１個のオリフィスを弾性
支持して可動としたため、低周波域から高周波域に亘る
広い周波数帯域に及んで大きなダンピング力を得ること
ができ、ダンピング特性の向上全達成することができる
。As is clear from the above description, according to the present invention, a plurality of orifices are provided in series in the fluid chamber of a fluid-filled engine mount, and at least one orifice is elastically supported to make it movable. A large damping force can be obtained over a wide frequency band covering a high frequency range, and the damping characteristics can be completely improved.
第１図乃至第７図は本発明の実施例を示すもので、第１
図乃至第４図は第１乃至第４実施例に係る流体入りエン
ジンマウントの各中央縦断面図、第５図はその周波数−
損失係数特性線図、第６図は理論的モデル図、第７図は
その算出により得られた周波数−損失係数特性線図、第
８図は従来の流体入りエンジンマウントの一例を示す中
央縦断面図、第９図及び第１０図月夫々その周波数・−
損失係数特性線図である。
１１６図面中１・・３０１は流体入りエンジンマウン１
．２・・３０３及び７１・・・３γ１は流体室、１０・
・・３１０はベース部材、２０・・・３２０は取付部材
、３０・・・３４０は弾性部材、７０・・３７０はダイ
ヤフラム、１３と５１・・・及び３５１と３６５はオリ
フィスである。
特許出願人 本田技研工業株式会社
代 理 人 弁理士下 １）容一部
間 弁理士 大 橋 邦 部
同 弁理士 小 山 上第１図
第２図
第３図
第５図
周ｆＬ［［Ｈｚｌ
第７図
固汲役旧ｚ１
第８図
第
用朕数［Ｈ２Ｊ
第１０図
００1 to 7 show embodiments of the present invention.
Figures to Figures 4 are central vertical sectional views of the fluid-filled engine mounts according to the first to fourth embodiments, and Figure 5 is the frequency -
Loss factor characteristic diagram, Figure 6 is a theoretical model diagram, Figure 7 is a frequency-loss coefficient characteristic diagram obtained by the calculation, and Figure 8 is a central longitudinal section showing an example of a conventional fluid-filled engine mount. Figures 9 and 10 each have their frequency -
It is a loss factor characteristic diagram. 1.301 in 116 drawings is fluid-filled engine mount 1
．． 2...303 and 71...3γ1 are fluid chambers, 10.
. . 310 is a base member, 20 . . . 320 is a mounting member, 30 . . . 340 is an elastic member, 70 . Patent Applicant Honda Motor Co., Ltd. Representative Patent Attorney 1) Patent Attorney Kuni Ohashi Department Patent Attorney Koyama 1 Figure 1 Figure 2 Figure 3 Figure 5 ZhoufL[[Hzl] Figure 7: Old z1 Figure 8: Usage number [H2J Figure 10: 00
Claims (1)
するベース部材と全振動の伝達により弾性変形可能外る
弾性部材で結合するとともに、」二記ベース部材、にダ
イヤフラムを開設し、内部の室内に流体を封入して成る
流体入りエンジンマウントにおいて、流体室内にオリア
イスを直列に複数段設けるとともに、少なくとも１個の
オリフィスを弾性支持して成る流体入りエンジンマウン
ト。The mounting member connected to the engine and the base member on which the engine is mounted are connected by an elastic member that can be elastically deformed by transmitting all vibrations, and a diaphragm is opened in the base member described in 2. What is claimed is: 1. A fluid-filled engine mount comprising a fluid chamber in which a plurality of orifices are arranged in series in a fluid chamber, and at least one orifice is elastically supported.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6179583A JPS59190531A (en) | 1983-04-08 | 1983-04-08 | Engine mount with fluid inside |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6179583A JPS59190531A (en) | 1983-04-08 | 1983-04-08 | Engine mount with fluid inside |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS59190531A true JPS59190531A (en) | 1984-10-29 |
Family
ID=13181388
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6179583A Pending JPS59190531A (en) | 1983-04-08 | 1983-04-08 | Engine mount with fluid inside |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59190531A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0147242A2 (en) * | 1983-12-28 | 1985-07-03 | Bridgestone Corporation | Vibration isolating devices |
| JPS60139941A (en) * | 1983-12-28 | 1985-07-24 | Bridgestone Corp | Vibration isolator |
| FR2589208A1 (en) * | 1985-10-28 | 1987-04-30 | Hutchinson Sa | IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS |
| FR2592114A1 (en) * | 1985-12-24 | 1987-06-26 | Hutchinson Sa | IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS |
| FR2596838A1 (en) * | 1986-04-05 | 1987-10-09 | Freudenberg Carl | Engine bearing with hydraulic damping |
| JPS62270842A (en) * | 1986-05-19 | 1987-11-25 | Mazda Motor Corp | Mounting device for power unit |
| JPS63195441A (en) * | 1987-02-05 | 1988-08-12 | Tokai Rubber Ind Ltd | Fluid sealed type mount device |
| JPH0254939U (en) * | 1988-10-13 | 1990-04-20 |
-
1983
- 1983-04-08 JP JP6179583A patent/JPS59190531A/en active Pending
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0147242A2 (en) * | 1983-12-28 | 1985-07-03 | Bridgestone Corporation | Vibration isolating devices |
| JPS60139941A (en) * | 1983-12-28 | 1985-07-24 | Bridgestone Corp | Vibration isolator |
| US4630808A (en) * | 1983-12-28 | 1986-12-23 | Bridgestone Corporation | Vibration isolating devices |
| JPH0434018B2 (en) * | 1983-12-28 | 1992-06-04 | Burijisuton Kk | |
| FR2589208A1 (en) * | 1985-10-28 | 1987-04-30 | Hutchinson Sa | IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS |
| FR2592114A1 (en) * | 1985-12-24 | 1987-06-26 | Hutchinson Sa | IMPROVEMENTS ON HYDRAULIC ANTIVIBRATORY SUPPORTS |
| FR2596838A1 (en) * | 1986-04-05 | 1987-10-09 | Freudenberg Carl | Engine bearing with hydraulic damping |
| JPS62270842A (en) * | 1986-05-19 | 1987-11-25 | Mazda Motor Corp | Mounting device for power unit |
| JPS63195441A (en) * | 1987-02-05 | 1988-08-12 | Tokai Rubber Ind Ltd | Fluid sealed type mount device |
| JPH0254939U (en) * | 1988-10-13 | 1990-04-20 |
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