JPS59131048A - Fluid mounting structure for power unit - Google Patents
Fluid mounting structure for power unitInfo
- Publication number
- JPS59131048A JPS59131048A JP575383A JP575383A JPS59131048A JP S59131048 A JPS59131048 A JP S59131048A JP 575383 A JP575383 A JP 575383A JP 575383 A JP575383 A JP 575383A JP S59131048 A JPS59131048 A JP S59131048A
- Authority
- JP
- Japan
- Prior art keywords
- elastic member
- vibration
- rubber
- proof rubber
- power unit
- 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
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】
本発明は自@車vcおけるエンジン等パワーユニットと
電体1vlVr配股して該パワーユニットの振動ll方
1hてろマウント構造の改良fl卯てる。DETAILED DESCRIPTION OF THE INVENTION The present invention provides an improved mount structure for arranging a power unit such as an engine in a vehicle and an electric body to vibrate the power unit.
従来、内燃轡関ゲ搭載した自@車Vrあっては。Previously, there was a personal vehicle VR equipped with an internal combustion engine.
パワーユニットをマウントでるに際して、該パワーユニ
ットと歪体闇f均′6のインシュレータラバーン介勢さ
せてパワーユニットからの優@Y制撮し、又は路面から
入力する感動の防振機症ケ受は持たせているのが通常で
ある。このよへな従来のマウント手段にあっては前記イ
ンシュレータラバーに対する負荷変動によってラバーが
大穴くたわみ、パワーユニットが91 位f 6のでエ
ンジンルー入内にこの変位?吸収−fるためのクリアラ
ンスン設けなければならない。こnK対処でるためにイ
ンシュレータラバーのゴム剛性を大モ<シて変位の抑制
gfる試みも行わnているが減衰力が低下しイパワーユ
ニットと止体聞の制振醍び防振特性が悪化する囃点があ
る。このよへにインシュレータラバーのゴム剛性I/r
は、たわみ菫と防振特性との相反で^要求を満足させな
け几ばならrrいという間魂点があり、設計トの1点と
もt【つイいろ。When mounting the power unit, use the insulator rubber between the power unit and the distorted body to obtain excellent @Y control from the power unit, or to receive the impressive vibration isolation mechanism input from the road surface. There is usually one. With this type of conventional mounting means, the insulator rubber is bent by a large hole due to load fluctuations, and since the power unit is at 91 f6, this displacement occurs within the engine loop. A clearance must be provided for absorption. In order to deal with this problem, attempts have been made to suppress the displacement by increasing the rubber rigidity of the insulator rubber, but the damping force decreases and the vibration damping properties of the power unit and static body deteriorate. There is a musical accompaniment. Rubber rigidity I/r of the insulator rubber
However, due to the conflict between the deflection violet and the anti-vibration characteristics, there is a certain point that if the requirements are not satisfied, it will be difficult to maintain the stability.
上記要求ン満足でる一手段として流体入りのマウント構
造も考えらnでおり、その−例ン第1図に示す。ldD
ち同図において1はパワーユニット側に固定されたPカ
バー、2は車体側に固定さnた下カバーであって1両者
間にはゴム等弾性部材3が弁装されている。該弾性部材
3は上下方向の感動を吸収fろ筒状防振ゴム3aと、該
筒状防融ゴム3aの仙1壁中途部より延設されて慣方向
の振動?吸収fる鍔状防融ゴム3bとから成り、夫々の
端部が前記上カバー1)lLび下カバー2と直接又はl
v+接的に一体に結合されている。(f上記弾性部材3
によって形成された中空部には、固定金、K aによっ
て支持固定さnたダイヤフラム5NLび仕切機6が設け
てあつイ、夜室A及び液室Bン形成でろ1.仕切機6の
路中央部πばオリフイスフを設けてあり、*荷変動によ
って該オリフィス7内ケ液1本がl油I自するよへKな
っている。As a means of satisfying the above requirements, a fluid-filled mount structure has been considered, and an example thereof is shown in FIG. ldD
In the figure, 1 is a P cover fixed to the power unit side, 2 is a lower cover fixed to the vehicle body side, and an elastic member 3 such as rubber is fitted between the two. The elastic member 3 includes a cylindrical anti-vibration rubber 3a that absorbs vibrations in the vertical direction, and is extended from the middle part of the wall of the cylindrical melt-proof rubber 3a to absorb vibrations in the inertial direction. It consists of a flange-like melt-proof rubber 3b that absorbs water, and its respective ends are connected directly or directly to the upper cover 1) and the lower cover 2.
v+ are tangentially coupled together. (fThe above elastic member 3
A diaphragm 5NL and a partition device 6 supported and fixed by a fixed metal are installed in the hollow part formed by 1. to form a night chamber A and a liquid chamber B. An orifice is provided at the center of the path of the partitioning machine 6, and one liquid in the orifice 7 becomes liquid depending on the load fluctuation.
上記の様な従来の流体マウント構1貴の場合5弾性部材
3ffかかる負荷♂動がオリフィス7乞通過でる流体の
流通低杭によって吸収さ几、過闇なたわみ及びnM振特
性が得られることになるが、前記負荷変動が可成大穴く
なった場脅には弾性部材3内の曲折部、@ff円Cで囲
んだ部分の座屈…、象が発生し易い@点がある。これ!
第2図のグラフによって説明でろと、弾性部材3に対′
fる荷重Gが111次大穴くなるf従って弾性部材3の
たわみ量Xが増大し、このたわみ量Xが一定の眼界点D
Y越えた吟に前記円Cで囲んだ部分の座屈現象が発生で
ろ。この限界点Dヶ越えてpttrfr重Gが大きくy
cろと弾性部材3のたわみ量も更に増大することw t
rる。この禰な座屈現象の発生はパワーユニットの支持
構債上好ましいもの↑はなく、防振性卵W爬化させると
ともf、#座屈部外のゴム等弾性部材の劣化!促進し、
耐久性が態くなるといへ欠点があった。In the case of the conventional fluid mount structure 1 as described above, the load motion applied to the elastic member 5 is absorbed by the low pile through which the fluid flows through the orifice 7, resulting in smooth deflection and nM vibration characteristics. However, when the load fluctuation becomes a relatively large hole, there is a bend in the elastic member 3, buckling of the part surrounded by @ff circle C, etc., and there are @ points where elephants are likely to occur. this!
As explained by the graph of FIG. 2, the elastic member 3'
The load G becomes a 111th large hole. Therefore, the amount of deflection X of the elastic member 3 increases, and this amount of deflection X reaches a constant eye point D.
A buckling phenomenon will occur in the area surrounded by circle C above when Y is exceeded. Beyond this limit point D, the pttrfr weight G increases y
The amount of deflection of the elastic member 3 also increases further w t
ru. The occurrence of this severe buckling phenomenon is not desirable in terms of the support structure of the power unit, and when the vibration-proofing structure is deteriorated, the elastic members such as rubber outside the buckling part deteriorate! promote,
There were drawbacks when it came to durability.
本発明は上記の如芦従来のパワーユニットの流体マウン
ト構造vrr!1faYn口えて、大所な荷重が弾性部
材に加えらnても容易f座屈しない+* Wt Y得る
ことケ目的とてろものであり、この目的ケ達成fるため
π組付けの際vc前記鍔状防振ゴムf対して、これと一
体に形成さ′rした筒状防融ゴムケ士方へ移動さぜるよ
へなブリテンションを付勢した構造l提供てろものであ
る。The present invention is based on the above conventional power unit fluid mount structure vrr! In other words, even if a large load is applied to the elastic member, it will not buckle easily. The present invention provides a structure l in which a tension is applied to the flange-shaped anti-vibration rubber f so as to cause it to move toward the cylindrical melt-proof rubber gage formed integrally therewith.
以下に図面ya−参照して不発明の実施例y!l−説明
て):、、、囲も第3図にRいて弾性部材11は上下方
向の橋@Y吸収でろ筒状防振ゴムllaと、該筒状防融
ゴムの111!中途部より延設され、+11方向の躯S
を吸収する鍔状防融ゴムllhより成り、この弾性部材
11に対して無#改時πは実巌の形状−ロち下カバー2
の全高りの位置よりも前記鍔状防融ゴムllbの多くの
部分が上方にあるよらな斜傾した位置を占めており1弾
性部材11の端部夫々が十カバーπ連結てる固定金具4
a及び下カバー2と直接又は間接的に刀口硫接着によっ
て一体に結合さnている。次に前記弾性部材11Vr対
して上下方向のfr I Y 710えると、該弾性部
材11は同図の実線の形状から、点線の形状Kf形し、
結局第4図に示した組み付は形成状轢が得らnる。この
よ)か土工方向の荷重は組み付は時π図外の十カバー及
び下カバー2MK押圧力?加えることによって実施する
ことがで茂るが、実際には上体側に固定した下カバー2
に対して、エンジン等パワーユニットy図外の上カバー
側へ固定することにより、該パワーユニットの自重によ
って鍔状防融ゴム11i+%j第4図のα口〈略水平の
状態に変形させることができろ。DESCRIPTION OF THE PREFERRED EMBODIMENTS Reference is made below to the drawings ya - illustrative embodiments of the invention! (l-explanation):,,,The elastic member 11 is also surrounded by R in FIG. 3, and the vertical bridge @ Y absorption filters the cylindrical anti-vibration rubber lla, and the cylindrical melt-proof rubber 111! Extended from the middle part, the frame S in the +11 direction
The elastic member 11 is made of a flanged melt-proof rubber llh that absorbs
A large part of the flanged melt-proof rubber llb occupies a tilted position above the full height position of the elastic member 11, and each end of the elastic member 11 is connected to the fixing metal 4.
a and the lower cover 2 directly or indirectly by sulfur bonding. Next, considering fr I Y 710 in the vertical direction with respect to the elastic member 11Vr, the elastic member 11 changes from the shape of the solid line in the figure to the shape of the dotted line Kf,
In the end, the assembly shown in FIG. 4 results in a well-formed shape. Is the load in the earthwork direction the pressing force of the ten cover and bottom cover 2MK outside the diagram? It can be done by adding the lower cover 2 fixed to the upper body side.
On the other hand, by fixing a power unit such as an engine to the upper cover side (outside of the figure), the brim-shaped melt-proof rubber 11i+%j can be deformed into a substantially horizontal state (α-port in Figure 4) by the weight of the power unit. reactor.
上記の様f鍔状防融ゴムllbが変形した状態を保持し
てパワーユニットの組み付けが行われるので、第4図の
状態時において上記鍔状防振ゴム11hには、これと一
体に連結さnている筒状防融ゴム11aYk万へ移動さ
せるよへな弾発力。Since the power unit is assembled while maintaining the deformed state of the flanged anti-fusible rubber llb as described above, in the state shown in FIG. It has a strong elastic force that moves the cylindrical melt-proof rubber 11aYk.
即ち矢印Eで示てよへな力が付勢されている。この弾発
力、喫イfれば鍔状防振ゴム11 tlvr付勢さtた
ブリテンションは、十カバー11111 K +固定さ
れろ図外のパワーユニットの荷重f対抗するよ5に働く
ことになる。尚弾性部材11の中窒室1−■にオリフィ
スを有する仕切板で+離さnた液室を設ける構成は第1
図に示した従来例と同様であるから詳細な説明及び図示
は省略しである。That is, a greater force is applied as shown by arrow E. If this elastic force is applied, the tension exerted by the collar-shaped vibration isolating rubber 11 tlvr will act against the load f of the fixed cover 11111 K + power unit not shown in the figure. . Note that the configuration in which a liquid chamber is provided at a distance from the middle nitrogen chamber 1-■ of the elastic member 11 by a partition plate having an orifice is the first one.
Since it is the same as the conventional example shown in the figure, detailed explanation and illustration will be omitted.
以上説明した構成において1弾性部材11に対てろ負荷
変動が発生した際に前記鍔状防振ゴム11hに付勢さn
た弾発力が負荷の変I!!I分ケ受は止め。In the configuration described above, when a load fluctuation occurs on one elastic member 11, the brim-shaped vibration isolating rubber 11h is biased.
The elastic force changes the load! ! Stop accepting I minutes.
弾性部材110曲折部におけろ座屈現象ン防止でろ効果
ケもたらて。こ7tY第5図のグラフによって説明てる
と5弾性部材11に対する荷重Gが111次大きくなる
にしたがって該弾性部材11のたわみ量Xが増大するこ
とは当然であるが、このたわみ量Xが一定の限界点Dン
越えた場会、第2図に示した座屈1il象が発生しない
。この従来の限界点Dl博えて四に荷重Gが大般くなり
、第2の限界点D′にまで達した場付に弾性部材110
年屈現象が発生することになる。よって座屈するたわみ
量がDからD′にまで延びろことになり、弾性部材11
に加えられろ荷重の許容限界をfからf’Kまで増大さ
せることかで穴る。通常パワーユニット側の自重等によ
って決まる荷重Gの大きさYrよりも小さくなるよ^に
設定しておけば上記の座屈現象が発生する惧れかない。The elastic member 110 has the effect of preventing buckling at the bent portion. This is explained using the graph in FIG. 5. As the load G on the elastic member 11 increases by the 111th order, it is natural that the amount of deflection X of the elastic member 11 increases. When the limit point D is exceeded, the buckling phenomenon shown in FIG. 2 does not occur. At this conventional limit point Dl, the load G becomes general and the elastic member 110 reaches the second limit point D'.
An annual flexion phenomenon will occur. Therefore, the amount of deflection that causes buckling extends from D to D', and the elastic member 11
The solution is to increase the permissible limit of the load that can be applied from f to f'K. Normally, if the load G is set to be smaller than Yr, which is determined by the power unit's own weight, etc., there is no risk that the above-mentioned buckling phenomenon will occur.
以上詳細f説明したよへに本発明に係るパワーユニット
の流体マウント構造は予じめ鍔状防振ゴムに対して荷重
に対抗し傅る弾発カゲ付勢入せで組付は形成しているの
で、弾性部材が座屈する限界荷重音大穴くすることがで
きるとともに該弾性部材の劣化を防1ヒして高寿時が得
ら7’Lる利点ケも発揮し、各種銀画πおけろパワーユ
ニットの流体マウント構造に過用して者効ゲ奏てるもの
である。As explained above in detail, the fluid mount structure of the power unit according to the present invention is assembled in advance by applying an elastic force to the collar-shaped vibration isolating rubber to resist and meet the load. Therefore, the limit load sound at which the elastic member buckles can be reduced, and the deterioration of the elastic member can be prevented, resulting in a long service life. It is effective for those who overuse the fluid mount structure of the fluid mount structure.
第1図は従来の流体入りパワーユニットのマウント構造
例!示f要部晧面図、第2図は第1図に示した構造例f
おけ6弾曲部材の変形状帽ヲ示すグラフ、第3図及び第
4図は本発明に係るパワー 0
ユニットの流体マウント槽重の組付状態を示す部分断面
図、第5図は本発明におけろ弾性部材の変形状幅?示す
グラフである。
l・・・上カバー、2・・・下カバー、4・・・固定金
具。
5・・・ダイヤフラム、6・・・仕切様、7・・・オリ
フィス。
11・・・弾性部材、11a・・・筒状防融ゴム、ll
h・・・鍔状防融ゴム。Figure 1 is an example of the mount structure of a conventional fluid-filled power unit! Figure 2 shows the structure example shown in Figure 1.
FIGS. 3 and 4 are partial cross-sectional views showing the assembled state of the fluid mount tank weight of the power 0 unit according to the present invention, and FIG. Deformation width of elastic member? This is a graph showing. l...upper cover, 2...lower cover, 4...fixing metal fittings. 5...Diaphragm, 6...Partition, 7...Orifice. 11... Elastic member, 11a... Cylindrical melt-proof rubber, ll
h... Flange-shaped melt-proof rubber.
Claims (1)
する弾性部材?弁!f−させ、該中空累内fオリフィス
v頁てる仕切板で′J+聯された液室ケ設けた流体マウ
ント49を造においで、前@e弾性部材は上下方向の娠
@ケ吸収丁^筒状防稿ゴムと、該筒状防融ゴムのl11
1壁中途部より延役さ几、横方向の儒動を吸収でる鍔状
防蝙ゴムより成り、且つ該鍔状防振ゴムVrは、この鍔
状防振ゴムと一体に連結されている面状防撮ゴムを上方
へ移動させるよ^な弾発力?付勢しで組み付は形成した
ことY46F4とするパワーユニットの流体マウント構
造。[Claims] ... A hicaber fixed to the power unit 1llll. An elastic member with a hollow chamber in the lower cover that is fixed to the vehicle body 1μIII/r? valve! f-, and a fluid mount 49 is constructed with a liquid chamber connected to the hollow internal f orifice by a partition plate, and the front elastic member is vertically compressed. l11 of the cylindrical anti-melt rubber and the cylindrical melt-proof rubber
1 consists of a flange-shaped vibration-proofing rubber that extends from the middle of the wall and absorbs lateral vibration, and the flange-shaped vibration-proof rubber Vr is a surface that is integrally connected with this flange-shaped vibration-proof rubber. What is the force of the bullet that moves the anti-camera rubber upward? The fluid mount structure of the power unit is made of Y46F4, which is assembled with force.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP575383A JPS59131048A (en) | 1983-01-17 | 1983-01-17 | Fluid mounting structure for power unit |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP575383A JPS59131048A (en) | 1983-01-17 | 1983-01-17 | Fluid mounting structure for power unit |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS59131048A true JPS59131048A (en) | 1984-07-27 |
Family
ID=11619876
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP575383A Pending JPS59131048A (en) | 1983-01-17 | 1983-01-17 | Fluid mounting structure for power unit |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS59131048A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02125119A (en) * | 1988-09-30 | 1990-05-14 | Carl Freudenberg:Fa | Rubber seat |
EP0775844A2 (en) * | 1995-11-20 | 1997-05-28 | WOCO Franz-Josef Wolf & Co. | Support |
-
1983
- 1983-01-17 JP JP575383A patent/JPS59131048A/en active Pending
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02125119A (en) * | 1988-09-30 | 1990-05-14 | Carl Freudenberg:Fa | Rubber seat |
EP0775844A2 (en) * | 1995-11-20 | 1997-05-28 | WOCO Franz-Josef Wolf & Co. | Support |
EP0775844A3 (en) * | 1995-11-20 | 1999-06-02 | WOCO Franz-Josef Wolf & Co. | Support |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US4437653A (en) | Fluid-filled engine mount device | |
US4407491A (en) | Rubber bearing device having air damping capacity | |
US8454002B2 (en) | Fluid filled vibration damping device | |
JPS59131048A (en) | Fluid mounting structure for power unit | |
JPH06257638A (en) | Liquid-sealed rubber mount | |
KR20030003535A (en) | an engine mounting structure on a front side member of vehicles | |
JPH01229132A (en) | Fluid sealed type mount device | |
JP3104402B2 (en) | Liquid filled vibration isolator | |
CN112211945B (en) | Vibration-proof unit mounting structure | |
JPH07266896A (en) | Supporting structure of radiator | |
JPS6040841A (en) | Vibration-proof device | |
US20060138719A1 (en) | Hydraulic antivibration device with a spacer | |
KR100508175B1 (en) | Baffle plate of fuel tank | |
JP3474249B2 (en) | Liquid-filled engine mount | |
JPH03292431A (en) | Fluid sealing mounting device | |
JPH11247917A (en) | Engine mount | |
JPS59133843A (en) | Fluid mount structure of power unit | |
US20070182076A1 (en) | Vibration isolator with reflective external travel restrictor and compressive snubber | |
JP3491777B2 (en) | Fluid power unit mounting device | |
JPH01220736A (en) | Stopper for resilient liquid sealed bush | |
JP2013036540A (en) | Liquid-filled vibration isolator | |
JP3040836B2 (en) | Anti-vibration device | |
JP2572377Y2 (en) | Liquid-filled mount | |
KR100255609B1 (en) | Hydraulic mounting system | |
KR20230159951A (en) | Dual mass type dynamic damper |