JPS6357656B2 - - Google Patents

Info

Publication number
JPS6357656B2
JPS6357656B2 JP25155183A JP25155183A JPS6357656B2 JP S6357656 B2 JPS6357656 B2 JP S6357656B2 JP 25155183 A JP25155183 A JP 25155183A JP 25155183 A JP25155183 A JP 25155183A JP S6357656 B2 JPS6357656 B2 JP S6357656B2
Authority
JP
Japan
Prior art keywords
liquid chambers
liquid
elastic body
axial direction
inner cylinder
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.)
Expired
Application number
JP25155183A
Other languages
Japanese (ja)
Other versions
JPS60139942A (en
Inventor
Toshiaki Abe
Junkichi Konishi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Priority to JP25155183A priority Critical patent/JPS60139942A/en
Publication of JPS60139942A publication Critical patent/JPS60139942A/en
Publication of JPS6357656B2 publication Critical patent/JPS6357656B2/ja
Granted legal-status Critical Current

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
    • F16F13/14—Units of the bushing type, i.e. loaded predominantly radially
    • F16F13/16—Units of the bushing type, i.e. loaded predominantly radially specially adapted for receiving axial loads

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Vehicle Body Suspensions (AREA)

Description

【発明の詳細な説明】 産業上の利用分野 本発明は内筒、外筒およびこれら内、外筒間に
装填される弾性体とを備えた筒状ブツシユに関す
る。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a cylindrical bushing including an inner cylinder, an outer cylinder, and an elastic body loaded between the inner cylinder and the outer cylinder.

従来技術 この種筒状ブツシユは、たとえばNISSANサ
ービス周報第428号（日産自動車株式会社昭和55
年９月発行）第115頁に示され、第１図に示すよ
うにセミトレーリングアーム式のサスペンシヨン
１に用いられている。即ち、このサスペンシヨン
１はサスペンシヨンメンバ２にアーム３が上下揺
動可能に支持され、このアーム３の揺動端部に車
輪取付用のロードホイール４が回転自在に取付け
られている。５は図外のデイフアレンシヤルギヤ
を収納するキヤリツジで、前記デイフアレンシヤ
ルギヤから分岐され前記キヤリツジ５から回転可
能に突出するドライブシヤフト６が前記ロードホ
イール４に連結されている。７はストラツトであ
る。そして、前記サスペンシヨンメンバ２の車両
左右方向両端部が筒状ブツシユ８を介して図外の
車体に取付けられ、この筒状ブツシユ８によつて
サスペンシヨン１の制振機能と路面から車体に伝
達される振動の遮断機能とを行なうようになつて
いる。ところで、前記筒状ブツシユ８には特公昭
48−36151号に示されるように、内筒、外筒間に
装填される弾性体内に内筒を境にして複数の液体
室を形成し、これら各液体室を連通路を介して連
通することによつて、前記制振機能と振動遮断機
能とを効率良く行なうようにした液体入りの筒状
ブツシユがある。Prior Art This type of cylindrical bushing is known, for example, from NISSAN Service Bulletin No. 428 (Nissan Motor Co., Ltd.
It is shown on page 115 (Published September 2013) and is used in a semi-trailing arm type suspension 1 as shown in FIG. That is, in this suspension 1, an arm 3 is supported by a suspension member 2 so as to be able to swing up and down, and a road wheel 4 for mounting a wheel is rotatably attached to the swinging end of the arm 3. Reference numeral 5 denotes a carriage that houses a differential gear (not shown), and a drive shaft 6 that is branched from the differential gear and rotatably protrudes from the carriage 5 is connected to the road wheel 4. 7 is a strut. Both ends of the suspension member 2 in the left and right direction of the vehicle are attached to the vehicle body (not shown) via cylindrical bushes 8, and the vibration damping function of the suspension 1 is transmitted from the road surface to the vehicle body by the cylindrical bushes 8. It is designed to perform a vibration isolation function. By the way, the cylindrical bush 8 has a
As shown in No. 48-36151, a plurality of liquid chambers are formed in an elastic body loaded between an inner cylinder and an outer cylinder, with the inner cylinder as a boundary, and these liquid chambers are communicated via a communication path. Accordingly, there is a liquid-filled cylindrical bush that efficiently performs the vibration damping function and the vibration isolation function.

しかしながら、この液体入りの筒状ブツシユに
あつては該ブツシユの軸直角方向の外力に対して
は液体室内容積が変化してその効果が発揮される
のであるが、軸方向に作用する外力に対しては液
体室内容積の変化はほとんど生ぜず、その制振機
能および振動遮断機能を充分に行なうことができ
ない。従つて、筒状ブツシユの軸方向に入力され
るロードノイズおよびハーシユネスが車体側に伝
達されてしまい車室内こもり音が発生してしまう
という問題点があつた。 However, in the case of this liquid-filled cylindrical bush, the internal volume of the liquid chamber changes in response to an external force perpendicular to the axis of the bush, and the effect is exhibited; In this case, the internal volume of the liquid chamber hardly changes, and its vibration damping and vibration isolating functions cannot be performed satisfactorily. Therefore, there has been a problem in that road noise and harshness input in the axial direction of the cylindrical bushing are transmitted to the vehicle body, resulting in muffled noise inside the vehicle interior.

発明の目的 本発明はかかる従来の問題点に鑑みて、筒状ブ
ツシユに軸方向の外力が作用したときに、積極的
に容積が収縮および膨張される１対の液体室を設
け、これら液体室間をオリフイス効果を有する連
通路で連通することにより、軸方向の外力に対す
る筒状ブツシユのばね定数を変化させ、もつて、
かかる軸方向の振動遮断機能および制振機能両者
を満足させるようにした筒状ブツシユを提供する
ことを目的とする。Purpose of the Invention In view of such conventional problems, the present invention provides a pair of liquid chambers whose volumes are actively contracted and expanded when an external force in the axial direction is applied to the cylindrical bushing. By communicating between them through a communication path having an orifice effect, the spring constant of the cylindrical bushing against external force in the axial direction is changed, and as a result,
It is an object of the present invention to provide a cylindrical bushing that satisfies both the axial vibration isolation function and vibration damping function.

発明の構成 かかる目的を達成するために本発明の筒状ブツ
シユは、同心状に配置される内筒、外筒と、それ
ら内、外筒間に装填される弾性体とを備え、該弾
性体内にブツシユの軸方向に対峙して１対の液体
室を形成すると共に、これら液体室間の弾性体に
よる隔壁と、各液体室の外方壁との径方向長さを
異ならせ、かつ、前記１対の液体室を連通路を介
して連通させることにより構成してある。Structure of the Invention In order to achieve the above object, the cylindrical bushing of the present invention includes an inner cylinder and an outer cylinder that are arranged concentrically, and an elastic body that is loaded inside and between the outer cylinders. A pair of liquid chambers are formed facing each other in the axial direction of the bush, and the partition wall made of an elastic material between the liquid chambers and the outer wall of each liquid chamber have different radial lengths, and It is constructed by communicating a pair of liquid chambers via a communication path.

作 用 以上の構成により本発明の作用は、軸方向に対
峙した１対の液体室は、隔壁と外方壁との径方向
の長さが異なつているため、筒状ブツシユに軸方
向の外力が作用した場合に、弾性体変形に伴つて
一方の液体室内容積が収縮し、他方の液体室内容
積が膨張されることになる。従つて、一方の液体
室から他方の液体室に連通路を介して液体移動さ
れる際に抵抗が生じ、前記外力が衝撃的な一方向
入力又は低周波振動である場合は、前記連通路に
発生する液体の通過抵抗が著しく大きくなつて液
体室内液体を剛体状とし、筒状ブツシユ全体のば
ね定数を大幅に高くして制振効果を向上する。一
方、周波数が大きくなる振動が入力された場合
は、この振動が弾性体によつて吸収されるため振
動遮断効果が向上することになる。Function With the above configuration, the function of the present invention is that the pair of liquid chambers facing each other in the axial direction have different radial lengths between the partition wall and the outer wall, so that an external force in the axial direction is applied to the cylindrical bush. When this occurs, the volume of one liquid chamber contracts and the volume of the other liquid chamber expands as the elastic body deforms. Therefore, if resistance occurs when the liquid is moved from one liquid chamber to the other through the communication path, and the external force is an impactful unidirectional input or low-frequency vibration, the communication path The passage resistance of the generated liquid is significantly increased, the liquid in the liquid chamber becomes rigid, and the spring constant of the entire cylindrical bushing is greatly increased, improving the vibration damping effect. On the other hand, when a vibration with a high frequency is input, this vibration is absorbed by the elastic body, so that the vibration isolation effect is improved.

実施例 以下本発明の実施例を図に基づいて詳細に説明
する。Embodiments Hereinafter, embodiments of the present invention will be described in detail based on the drawings.

即ち、第２図は本発明の一実施例を示す筒状ブ
ツシユ１０で、内筒１１とこの内筒１１に対し同
心状に配置される外筒１２との間にゴム製の弾性
体１３が装填されている。この弾性体１３は前記
内筒１１と、前記外筒１２の内周にシールラバー
１４を介して圧入等により嵌着される補助リング
１５とに加硫接着される。前記弾性体１３内には
筒状ブツシユ１０の軸方向に対峙して、隔壁１６
によつて隔成される１対の第１、第２液体室１
７，１７ａおよびこの第１、第２液体室１７，１
７ａと内筒１１を境に対称に設けられ隔壁１６ａ
を有する第３、第４液体室１８，１８ａが形成さ
れる。前記隔壁１６，１６ａは前記弾性体１３よ
りばね定数の小さいゴム等の弾性体で形成され、
内筒１１から突設された鍔部１９外周に嵌着固定
される環状部材２０と前記補助リング１５との間
に加硫接着されている。そして、前記隔壁１６，
１６ａの径方向長さl1は前記液体室１７，１７
ａ，１８，１８ａの外側に設けられる外方壁２
１，２１ａの長さl2より小さくなつている。とこ
ろで、前記第１、第２液体室１７，１７ａおよび
第３、第４液体室１８，１８ａは鍔部１９と環状
部材２０との間に形成される第１連通路２２，２
２ａによつて連通され、この第１連通路２２，２
２ａを介して第１、第２液体室１７，１７ａ内の
液体移動および第３、第４液体室１８，１８ａ内
の液体移動がオリフイス効果をもつて行なわれる
ようになつている。更に、前記鍔部１９外周には
前記第１連通路２２，２２ａに連通する第２連通
路２３が形成され、この第２連通路２３を介して
第１、第２液体室１７，１７ａと第３、第４液体
室１８，１８ａ間の液体移動がオリフイス効果を
もつて行なわれるようになつている。 That is, FIG. 2 shows a cylindrical bushing 10 showing one embodiment of the present invention, in which a rubber elastic body 13 is disposed between an inner cylinder 11 and an outer cylinder 12 arranged concentrically with respect to the inner cylinder 11. Loaded. This elastic body 13 is vulcanized and bonded to the inner cylinder 11 and an auxiliary ring 15 that is fitted onto the inner periphery of the outer cylinder 12 through a seal rubber 14 by press fitting or the like. Inside the elastic body 13, there is a partition wall 16 facing in the axial direction of the cylindrical bushing 10.
a pair of first and second liquid chambers 1 separated by
7, 17a and the first and second liquid chambers 17, 1
A partition wall 16a is provided symmetrically with respect to the inner cylinder 11 and the partition wall 16a.
Third and fourth liquid chambers 18, 18a are formed. The partition walls 16, 16a are formed of an elastic body such as rubber having a smaller spring constant than the elastic body 13,
The auxiliary ring 15 is bonded by vulcanization between the annular member 20 that is fitted and fixed to the outer periphery of the flange 19 protruding from the inner cylinder 11 . And the partition wall 16,
The radial length l 1 of 16a is the liquid chamber 17, 17.
Outer wall 2 provided on the outside of a, 18, 18a
1,21a is smaller than the length l2 . By the way, the first and second liquid chambers 17 and 17a and the third and fourth liquid chambers 18 and 18a are connected to first communication passages 22 and 2 formed between the flange 19 and the annular member 20.
2a, and this first communication path 22, 2
The liquid movement in the first and second liquid chambers 17, 17a and the liquid movement in the third and fourth liquid chambers 18, 18a are performed through the orifice effect through the liquid chamber 2a. Further, a second communication passage 23 is formed on the outer periphery of the flange 19 and communicates with the first communication passages 22 and 22a, and the first and second liquid chambers 17 and 17a are connected to each other via this second communication passage 23. 3. Liquid movement between the fourth liquid chambers 18 and 18a is performed using an orifice effect.

かかる構成になる筒状ブツシユ１０は、前記第
１図に示したようにサスペンシヨンメンバ２を図
外の車体に取付ける際に用いられ、外筒１２がサ
スペンシヨンメンバ２の両端部に固設され、か
つ、内筒１１が図外の取付ピンを介して前記車体
に装着されるようになつている。 The cylindrical bushing 10 having such a configuration is used when the suspension member 2 is attached to a vehicle body (not shown) as shown in FIG. 1, and the outer cylinder 12 is fixed to both ends of the suspension member 2. , and the inner cylinder 11 is attached to the vehicle body via a mounting pin (not shown).

以上の構成により、本実施例の筒状ブツシユ１
０にあつては、このブツシユ１０の軸方向に連通
路２２，２２ａで連通された第１、第２液体室１
７，１７ａおよび第３、第４液体室１８，１８ａ
が形成されているため、前記筒状ブツシユ１０に
軸方向の外力が作用した時には、内筒１１、外筒
１２が軸方向に相対移動し、弾性体１３が変形さ
れる。たとえば、サスペンシヨンメンバ２の上方
変位に対し第２図中外筒１２が内筒１１に対して
上方に移動された場合、弾性体１３の変形に伴つ
て第１、第２、第３、第４液体室１７，１７ａ，
１８，１８ａ内形状も変化する。このとき、第３
図に示すように隔壁１６，１６ａに対して外方壁
２１，２１ａが径方向に長くなつているため、第
２、第４液体室１７ａ，１８ａの外方壁２１，２
１ａは前記隔壁１６，１６ａに近づこうとする
が、第１、第３液体室１７，１８の外方壁２１，
２１ａは前記隔壁１６，１６ａから遠ざかろうと
する。従つて、第２、第４液体室１７ａ，１８ａ
内容積は収縮し、第１、第３液体室１７，１８内
容積は膨張され、これら第１、第２液体室１７，
１７ａ間および第３、第４液体室１８，１８ａ間
の圧力は第１連通路２２，２２ａを介して液体移
動されることにより均衡されようとする。ところ
が、前記軸方向の外力がバウンド、リバウンド時
に生ずる衝撃的な変位荷重である場合は、第１連
通路２２，２２ａのオリフイス効果によつて流体
移動に大きな抵抗が生じ、第２、第４液体室１７
ａ，１８ａ内の液体圧力が著しく大きくなつて剛
体状となり、該第２、第４液体室１７ａ，１８ａ
内容積の収縮が阻止される。すると、弾性体１３
のそれ以上の変形は抑制され、あたかも筒状ブツ
シユ１０全体のばね定数が著しく増大したかのよ
うになり、内周１１、外周１２間の軸方向の相対
変位が阻止され、ここにサスペンシヨンメンバ２
の上方変位が阻止されて制振機能が発揮される。
尚、サスペンシヨンメンバ２が下方変位したとき
には、第１、第２液体室１７，１７ａおよび第
３、第４液体室１８，１８ａ間の収縮、膨張関係
が、前述したサスペンシヨンメンバ２の上方変位
の場合と逆になるが、同様に第１連通路２２，２
２ａのオリフイス効果によつて制振機能が発揮さ
れる。 With the above configuration, the cylindrical bush 1 of this embodiment
0, the first and second liquid chambers 1 communicate with each other in the axial direction of the bush 10 through communication passages 22 and 22a.
7, 17a and third and fourth liquid chambers 18, 18a
Because of this, when an external force in the axial direction is applied to the cylindrical bushing 10, the inner cylinder 11 and the outer cylinder 12 move relative to each other in the axial direction, and the elastic body 13 is deformed. For example, when the outer cylinder 12 is moved upward relative to the inner cylinder 11 in FIG. Liquid chambers 17, 17a,
The internal shape of 18, 18a also changes. At this time, the third
As shown in the figure, since the outer walls 21 and 21a are longer in the radial direction than the partition walls 16 and 16a, the outer walls 21 and 2 of the second and fourth liquid chambers 17a and 18a are
1a tries to approach the partition walls 16 and 16a, but the outer walls 21 and 1 of the first and third liquid chambers 17 and 18
21a tries to move away from the partition walls 16, 16a. Therefore, the second and fourth liquid chambers 17a, 18a
The internal volume contracts, and the internal volumes of the first and third liquid chambers 17, 18 expand, and these first and second liquid chambers 17,
The pressures between the liquid chambers 17a and between the third and fourth liquid chambers 18, 18a tend to be balanced by moving the liquid through the first communicating paths 22, 22a. However, if the external force in the axial direction is an impactful displacement load that occurs during bounce or rebound, large resistance to fluid movement occurs due to the orifice effect of the first communication passages 22, 22a, and the second and fourth liquids Room 17
The liquid pressure in a, 18a increases significantly and becomes a rigid body, and the second and fourth liquid chambers 17a, 18a
Deflation of internal volume is prevented. Then, the elastic body 13
Further deformation of the cylindrical bushing 10 is suppressed, and it becomes as if the spring constant of the entire cylindrical bushing 10 has been significantly increased, and relative displacement in the axial direction between the inner circumference 11 and the outer circumference 12 is prevented, and the suspension member 2
The upward displacement of is prevented and the vibration damping function is exhibited.
Incidentally, when the suspension member 2 is displaced downward, the contraction and expansion relationship between the first and second liquid chambers 17, 17a and the third and fourth liquid chambers 18, 18a is caused by the above-mentioned upward displacement of the suspension member 2. Although it is opposite to the case of , the first communication path 22, 2
The vibration damping function is exhibited by the orifice effect of 2a.

次に、サスペンシヨンメンバ２に伝達されるロ
ードノイズとかハーシユネス等の振動に対して
は、この振動が筒状ブツシユ１０の軸方向に入力
された場合、かかる振動による変位は著しく小さ
いため、弾性体１３の変形はほとんど伴わず、第
１、第２液体室１７，１７ａ内および第３、第４
液体室１８，１８ａ内の収縮、膨張に関係なく弾
性体１３自体の振動吸収能力により前記振動が車
体側に伝達されるのを遮断する。従つて、弾性体
１３のばね定数を小さく設定しておくとによつ
て、前記振動遮断機能が向上し、ロードノイズ、
ハーシユネス等によつて生ずる車室内騒音を防止
し、室内の静斉性を向上することができる。 Next, regarding vibrations such as road noise and harshness transmitted to the suspension member 2, when this vibration is input in the axial direction of the cylindrical bushing 10, the displacement due to such vibration is extremely small, so the elastic body 13 is hardly deformed, and the inside of the first and second liquid chambers 17 and 17a and the third and fourth liquid chambers
Regardless of contraction or expansion in the liquid chambers 18, 18a, the vibration absorption ability of the elastic body 13 itself blocks the vibrations from being transmitted to the vehicle body. Therefore, by setting the spring constant of the elastic body 13 to be small, the vibration isolation function is improved, and road noise and
It is possible to prevent vehicle interior noise caused by harshness and the like, and improve interior static uniformity.

尚、本実施例にあつては、前記第１、第２液体
室１７，１７ａの１組と前記第３、第４液体室１
８，１８ａの１組とが内筒１１を境にして対向配
置され、かつ、この対向される夫々の組が第２連
通路２３を介して連通されているため、これら互
いに１組となつた第１、第２液体室１７，１７ａ
と第３、第４液体室１８，１８ａとを外力の作用
方向、つまり車両前後方向に配置しておくことに
よつて、かかる外力の作用方向に対する制振機能
および振動遮断機能を効率良く行なうことができ
る。即ち、車両の急加、減速時等に発生する慣性
力が筒状ブツシユ１０に軸直角方向の外力として
作用した場合、前記第１、第２液体室１７，１７
ａおよび第３、第４液体室１８，１８ａの一方の
１組が潰されると共に、他方の１組が膨張され
て、第２連通路２３を介して液体移動が行なわれ
る。従つて、この液体移動時に第２連通路２３内
に発生するオリフイス効果により前記各液体室内
容積の変化が阻止され、ここに筒状ブツシユ１０
の軸直角方向つまり車両前後方向のサスペンシヨ
ンメンバ２の変位が阻止され制振機能が効果的に
発揮される。また、車両前後方向に作用する振
動、たとえばロードノイズ等の振動に対してもば
ね定数を小さくした弾性体１３によつて振動吸収
されることになる。 In this embodiment, one set of the first and second liquid chambers 17 and 17a and the third and fourth liquid chambers 1
8 and 18a are disposed opposite to each other with the inner cylinder 11 as a boundary, and each of the opposing pairs is communicated with each other via the second communication passage 23, so that they form one pair with each other. First and second liquid chambers 17, 17a
By arranging the third and fourth liquid chambers 18, 18a in the direction in which external force is applied, that is, in the longitudinal direction of the vehicle, a damping function and a vibration isolation function in the direction in which such external force is applied can be efficiently performed. Can be done. That is, when the inertia force generated when the vehicle suddenly accelerates or decelerates acts on the cylindrical bushing 10 as an external force in the direction perpendicular to the axis, the first and second liquid chambers 17, 17
One set of the third and fourth liquid chambers 18 and 18a is collapsed, and the other set is expanded, and liquid is transferred through the second communication path 23. Therefore, due to the orifice effect generated in the second communicating path 23 during this liquid movement, changes in the internal volumes of the liquid chambers are prevented, and the cylindrical bush 10
Displacement of the suspension member 2 in the direction perpendicular to the axis of the vehicle, that is, in the longitudinal direction of the vehicle, is prevented, and the vibration damping function is effectively exhibited. Furthermore, vibrations acting in the longitudinal direction of the vehicle, such as vibrations caused by road noise, are also absorbed by the elastic body 13 having a small spring constant.

第４図、第５図は本発明の他の実施例を夫々示
す筒状ブツシユ３０，３０ａで、内筒３１，３１
ａと外筒３２，３２ａ間に装填される弾性体３
３，３３ａには前記実施例と同様に軸方向に対峙
して１対の液体室３４，３５および３４ａ，３５
ａが形成され、これら液体室３４，３５および３
４ａ，３５ａは連通路３６，３６ａを介して連通
されている。ここで、第４図に示す実施例にあつ
ては前記内筒３１の外側形状が両端から中央部に
行くに従つて徐々に拡径される謂わゆる太鼓状に
形成されることによつて、隔壁３７に対して外方
壁３８の径方向長さが大きくなるように設定され
ている。また、第５図に示す実施例にあつては、
前記内筒３１ａの外側形状が両端から中央部に行
くに従つて徐々に縮径される謂わゆるつづみ状に
形成されることによつて、隔壁３７ａに対して外
方壁３８ａの径方向長さが小さくなるように設定
されている。従つて、かかる第４図、第５図に示
す実施例にあつては、隔壁３７，３７ａと外方壁
３８，３８ａの長さが異なるために、軸方向の外
力が作用した際に液体室３４，３５および液体室
３４ａ，３５ａ内容積の一方が収縮し、他方が膨
張するため前記第２図に示す実施例と同様に軸方
向の外力に対する制振機能および振動遮断機能を
夫々向上することができる。 FIGS. 4 and 5 show cylindrical bushes 30 and 30a showing other embodiments of the present invention, respectively, and inner cylinders 31 and 31.
an elastic body 3 loaded between a and the outer cylinders 32, 32a
3, 33a have a pair of liquid chambers 34, 35 and 34a, 35 facing each other in the axial direction, as in the previous embodiment.
a is formed, and these liquid chambers 34, 35 and 3
4a and 35a are communicated via communication paths 36 and 36a. Here, in the embodiment shown in FIG. 4, the outer shape of the inner cylinder 31 is formed into a so-called drum shape whose diameter gradually increases from both ends toward the center. The outer wall 38 is set to have a larger radial length than the partition wall 37 . Furthermore, in the embodiment shown in FIG.
By forming the outer shape of the inner cylinder 31a into a so-called tsume shape whose diameter gradually decreases from both ends toward the center, the radial length of the outer wall 38a with respect to the partition wall 37a is reduced. is set to be small. Therefore, in the embodiment shown in FIGS. 4 and 5, since the partition walls 37, 37a and the outer walls 38, 38a have different lengths, when an external force in the axial direction is applied, the liquid chamber Since one of the internal volumes of the liquid chambers 34, 35 and the liquid chambers 34a, 35a contracts and the other expands, the damping function and vibration isolation function against external forces in the axial direction are improved, respectively, similarly to the embodiment shown in FIG. 2. Can be done.

尚、前記第４図、第５図に示す筒状ブツシユ３
０，３０ａは、軸方向の外力のみを考慮して、各
液体室３４，３５および３４ａ，３５ａは環状に
形成されたものを図示したが、これに限ることな
く前記第２図の実施例で述べたように前記液体室
３４，３５および３４ａ，３５ａを、内筒３１，
３１ａを境にして対向されるように独立させ、そ
して、このように独立されて対向する液体室同志
を連通路を介して連通することにより、第２図の
実施例と同様に軸直角方向の外力に対する制振機
能および振動遮断機能を向上することができる。 Incidentally, the cylindrical bush 3 shown in FIGS. 4 and 5 above
0 and 30a, each of the liquid chambers 34, 35 and 34a, 35a is shown to be formed in an annular shape in consideration of only the external force in the axial direction, but the present invention is not limited to this. As mentioned above, the liquid chambers 34, 35 and 34a, 35a are connected to the inner cylinder 31,
31a as a boundary, and by communicating the independent and opposing liquid chambers through the communication path, the liquid chambers are separated in the direction perpendicular to the axis, as in the embodiment shown in FIG. It is possible to improve the vibration damping function and vibration isolation function against external forces.

ところで、前述した各実施例であつては、サス
ペンシヨンメンバ２を車体に取付ける際に用いら
れる筒状ブツシユ１０，３０，３０ａを例にとつ
て述べたが、これに限ることなく、トレーリング
アーム式のサスペンシヨンにあつてアームとサス
ペンシヨンメンバを連結する筒状ブツシユとし
て、また、４リンク式のサスペンシヨンにあつて
リンクの連結部として夫々用いることができ、更
にはサスペンシヨンに限ることなく、一般に存在
する振動体を固定体に装着する際に用いられる筒
状ブツシユに本発明を適用することができること
は勿論である。 By the way, in each of the above-mentioned embodiments, the cylindrical bushes 10, 30, 30a used when attaching the suspension member 2 to the vehicle body were described as an example, but the trailing arm is not limited to this. It can be used as a cylindrical bush that connects the arm and the suspension member in a type suspension, and as a link connecting part in a four-link type suspension, and is not limited to the suspension. Of course, the present invention can be applied to a cylindrical bushing that is used when a generally existing vibrating body is attached to a fixed body.

発明の効果 以上説明したように本発明の筒状ブツシユにあ
つては、弾性体内に、連通路を介して連通される
１対の液体室をブツシユの軸方向に対峙して形成
し、かつ、液体室間の隔壁と外壁との径方向長さ
を異ならせたので、筒状ブツシユに軸方向の衝撃
的な外力が作用した場合は、１対の液体室の一方
が収縮し他方が膨張されることに伴つて前記連通
路を介しての液体移動に大きな抵抗が生じ、弾性
体のそれ以上の変形が阻止される。従つて、内
筒、外筒間の相対的な軸方向移動が抑制され、こ
こにブツシユ軸方向における制振機能の向上が図
られる。また、軸方向の振動に対しては液体室の
容積変化はほとんど生ぜず、従つて、弾性体のば
ね定数を小さく設定しておくことによつて前記振
動が弾性体に効率良く吸収され、ここにブツシユ
軸方向における振動遮断機の向上が図られる。こ
のように、本発明は筒状ブツシユの軸方向におけ
る制振機能および振動遮断機能の両者を向上する
ようにしたので、従来果し得なかつた振動伝達特
性の著しい向上を達成できるという優れた効果を
奏する。Effects of the Invention As explained above, in the cylindrical bush of the present invention, a pair of liquid chambers are formed in the elastic body and communicated with each other via a communication path, facing each other in the axial direction of the bush, and Since the radial lengths of the partition wall between the liquid chambers and the outer wall are made different, when an impactful external force in the axial direction is applied to the cylindrical bushing, one of the pair of liquid chambers contracts and the other expands. As a result, a large resistance is generated to the movement of liquid through the communication path, and further deformation of the elastic body is prevented. Therefore, relative axial movement between the inner cylinder and the outer cylinder is suppressed, thereby improving the vibration damping function in the bush axial direction. In addition, vibrations in the axial direction cause almost no change in the volume of the liquid chamber, so by setting the spring constant of the elastic body to a small value, the vibrations can be efficiently absorbed by the elastic body. The vibration isolator in the direction of the bush axis was improved. As described above, the present invention improves both the vibration damping function and the vibration isolation function in the axial direction of the cylindrical bushing, and has the excellent effect of achieving a remarkable improvement in vibration transmission characteristics that was previously unattainable. play.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は従来の筒状ブツシユを用いたサスペン
シヨンの斜視図、第２図は本発明の一実施例を示
す筒状ブツシユの断面図、第３図は第２図に示す
筒状ブツシユの作動状態を示す要部断面図、第４
図、第５図は本発明の他の実施例を夫々示す断面
図である。 １０，３０，３０ａ……筒状ブツシユ、１１，
３１，３１ａ……内筒、１２，３２，３２ａ……
外筒、１３，３３，３３ａ……弾性体、１６，３
７，３７ａ……隔壁、１７，１７ａ，１８，１８
ａ，３４，３４ａ，３５，３５ａ……流体室、２
１，２１ａ，３８，３８ａ……外方壁、２２，３
６，３６ａ……連通路。 Fig. 1 is a perspective view of a suspension using a conventional cylindrical bushing, Fig. 2 is a sectional view of a cylindrical bushing showing an embodiment of the present invention, and Fig. 3 is a cross-sectional view of a cylindrical bushing shown in Fig. 2. Main part sectional view showing the operating state, No. 4
5 are sectional views showing other embodiments of the present invention. 10, 30, 30a... cylindrical bushing, 11,
31, 31a... Inner cylinder, 12, 32, 32a...
Outer cylinder, 13, 33, 33a...Elastic body, 16, 3
7, 37a... partition wall, 17, 17a, 18, 18
a, 34, 34a, 35, 35a...Fluid chamber, 2
1, 21a, 38, 38a...Outer wall, 22, 3
6, 36a...Communication path.

Claims (1)

【特許請求の範囲】[Claims] １ 同心状に配置される内筒、外筒と、これら
内、外筒間に装填される弾性体とを備え、該弾性
体内にブツシユの軸方向に対峙して１対の液体室
を形成すると共に、これら液体室間の弾性体によ
る隔壁と、各液体室の外方壁との径方向長さを異
ならせ、かつ、前記１対の液体室を連通路を介し
て連通させたことを特徴とする筒状ブツシユ。1.Equipped with an inner cylinder and an outer cylinder arranged concentrically, and an elastic body loaded between these inner and outer cylinders, forming a pair of liquid chambers facing each other in the axial direction of the bushing within the elastic body. In addition, the radial lengths of the elastic partition walls between the liquid chambers and the outer walls of each liquid chamber are different, and the pair of liquid chambers are communicated with each other via a communication path. A cylindrical bush.
JP25155183A 1983-12-27 1983-12-27 Tubular bush Granted JPS60139942A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP25155183A JPS60139942A (en) 1983-12-27 1983-12-27 Tubular bush

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP25155183A JPS60139942A (en) 1983-12-27 1983-12-27 Tubular bush

Publications (2)

Publication Number Publication Date
JPS60139942A JPS60139942A (en) 1985-07-24
JPS6357656B2 true JPS6357656B2 (en) 1988-11-11

Family

ID=17224507

Family Applications (1)

Application Number Title Priority Date Filing Date
JP25155183A Granted JPS60139942A (en) 1983-12-27 1983-12-27 Tubular bush

Country Status (1)

Country Link
JP (1) JPS60139942A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0262555U (en) * 1988-10-28 1990-05-10

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0225947Y2 (en) * 1985-09-26 1990-07-16
JPH0430442Y2 (en) * 1986-06-30 1992-07-22
FR2605693B1 (en) * 1986-10-27 1989-04-28 Hutchinson IMPROVEMENTS ON ANTI-VIBRATION HYDRAULIC SUPPORTS
JPS63266240A (en) * 1987-04-23 1988-11-02 Mazda Motor Corp Fluid-filled bush
DE3722132A1 (en) * 1987-07-04 1989-01-12 Daimler Benz Ag HYDRAULIC DAMPING BEARING
DE3730582A1 (en) * 1987-09-11 1989-03-23 Opel Adam Ag BEARING FOR THE ELASTIC, VIBRATION-DAMPING STORAGE OF COMPONENTS
EP0325714A3 (en) * 1988-01-26 1990-09-12 Dr.Ing.h.c. F. Porsche Aktiengesellschaft Elastic mounting
JPH0650135B2 (en) * 1988-07-28 1994-06-29 東洋ゴム工業株式会社 Liquid-filled body mount
DE3831644C2 (en) * 1988-09-17 1998-08-27 Pahl Gummi Asbest Hydraulically damping bearing
JPH02117450U (en) * 1989-03-09 1990-09-20
DE4031495A1 (en) * 1990-10-05 1992-04-09 Freudenberg Carl Fa HYDRAULIC DAMPING BEARING
DE4438932C2 (en) * 1994-10-31 1998-07-02 Daimler Benz Ag Hydro bearing
DE19526750C2 (en) * 1995-07-21 1998-07-02 Metzeler Gimetall Ag Axial damping hydraulic bushing
GB2342978B (en) * 1998-10-22 2002-08-21 Draftex Ind Ltd Hydroelastic articulating joints
DE10223303A1 (en) * 2002-05-24 2003-12-18 Freudenberg Carl Kg Hydraulically damping rubber bearing
JP4948068B2 (en) * 2006-07-24 2012-06-06 本田技研工業株式会社 Liquid-filled bush
WO2009100205A1 (en) * 2008-02-05 2009-08-13 Cooper-Standard Automotive Inc. Axially damped hydraulic mount assembly
JP2018204774A (en) 2017-06-09 2018-12-27 株式会社ブリヂストン Vibration controller

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0262555U (en) * 1988-10-28 1990-05-10

Also Published As

Publication number Publication date
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