JPS633479Y2 - - Google Patents
Info
- Publication number
- JPS633479Y2 JPS633479Y2 JP1982155562U JP15556282U JPS633479Y2 JP S633479 Y2 JPS633479 Y2 JP S633479Y2 JP 1982155562 U JP1982155562 U JP 1982155562U JP 15556282 U JP15556282 U JP 15556282U JP S633479 Y2 JPS633479 Y2 JP S633479Y2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- piston
- valve body
- valve
- 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
Links
- 239000003921 oil Substances 0.000 claims description 93
- 239000006096 absorbing agent Substances 0.000 claims description 20
- 230000035939 shock Effects 0.000 claims description 20
- 239000010720 hydraulic oil Substances 0.000 claims description 10
- 238000005192 partition Methods 0.000 claims description 8
- 238000013016 damping Methods 0.000 description 15
- 230000006835 compression Effects 0.000 description 11
- 238000007906 compression Methods 0.000 description 11
- 230000004048 modification Effects 0.000 description 7
- 238000012986 modification Methods 0.000 description 7
- 239000002184 metal Substances 0.000 description 3
- 239000004033 plastic Substances 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 230000002940 repellent Effects 0.000 description 1
- 239000005871 repellent Substances 0.000 description 1
Landscapes
- Fluid-Damping Devices (AREA)
Description
【考案の詳細な説明】
本考案は、車両用油圧式シヨツクアブソーバに
関する。[Detailed Description of the Invention] The present invention relates to a hydraulic shock absorber for a vehicle.
一般に、油圧式シヨツクアブソーバは、作動油
を封入したシリンダと、このシリンダの開口端部
を液密的かつ摺動可能に貫通するピストンロツド
と、このピストンロツドの一端部に組付けられ前
記シリンダ内に摺動可能に嵌挿されて同シリンダ
内を２つの油室に区画するピストンと、このピス
トンに設けられ前記両油室を連通させる通油孔と
この通油孔をその一端開口部側から弾撥的に閉じ
る弁体を有するバルブ機構を具備していて、伸張
行程時又は圧縮行程時一方の油室に生じる油圧に
より前記バルブ機構の弁体を押し開き、一方の油
室内の作動油を他方の油室内へ流動させることに
より減衰力を発生するようになつている。このた
め、車両が大きな凹凸を有する悪路等を走行する
時等シヨツクアブソーバに大きな衝撃力が付与さ
れた場合には、一方の油室に生じる油圧が極めて
大きくて弁体を過度に押し開くきらいがあり、か
かる衝撃力に対する充分な減衰力が得られにく
い。 In general, a hydraulic shock absorber includes a cylinder filled with hydraulic oil, a piston rod that fluidly and slidably penetrates the open end of the cylinder, and a piston rod that is assembled to one end of the piston rod and slides into the cylinder. A piston that is movably inserted and partitions the inside of the cylinder into two oil chambers, an oil passage hole provided in the piston that communicates the two oil chambers, and an elastic repellent from one end opening side of the oil passage hole. The valve mechanism is equipped with a valve mechanism that has a valve body that closes automatically, and the valve body of the valve mechanism is pushed open by the hydraulic pressure generated in one oil chamber during the extension stroke or compression stroke, and the hydraulic oil in one oil chamber is transferred to the other oil chamber. Damping force is generated by flowing the oil into the oil chamber. For this reason, when a large impact force is applied to the shock absorber, such as when the vehicle is traveling on a rough road with large irregularities, the hydraulic pressure generated in one oil chamber is extremely large and tends to push the valve body open excessively. Therefore, it is difficult to obtain sufficient damping force against such impact force.
本考案は、このような実状に着目してなされた
もので、その主たる目的はこの種油圧式シヨツク
アブソーバにおいて、かかる衝撃力に対する充分
な減衰力を得るようにすることにある。しかし
て、本考案は上記目的を達成すべく、前記バルブ
機構を構成する弁体に前記通油孔又はこれとは独
立して前記ピストンに設けた通油孔に連通する連
通路を設け、かつ前記ピストンロツドの一端部に
て前記弁体に対向して所定間隔を保つて固定した
リテーナと前記弁体間に軸方向に可撓性の筒状又
は環状の隔壁部材を介在してその内部に圧力室を
形成し、この圧力室を前記連通路及び通油孔を通
して前記両油室の一方の油室に連通させて前記弁
体を閉じる方向へ付勢する圧力室に構成したこと
にその特徴がある。これにより、本考案において
は、一方の油室に生じる油圧に応じて圧力室内の
油圧が増加し、この油圧に応じて弁体が通油孔の
一端開口部へ押圧される。従つて、本考案によれ
ば、一方の油室に極めて大きな油圧が生じても、
圧力室の油圧もこれに応じて増加して弁体を通油
孔の一端開口部に押圧するため、弁体を過度に押
し開くことがなくて大きな衝撃力に対しても充分
な減衰力を得ることができる。 The present invention was devised in view of these circumstances, and its main purpose is to provide a hydraulic shock absorber of this type with a sufficient damping force against such impact force. Therefore, in order to achieve the above object, the present invention provides a communication passage that communicates with the oil passage hole or independently with the oil passage hole provided in the piston in the valve body constituting the valve mechanism, and A flexible cylindrical or annular partition member is interposed in the axial direction between the retainer, which is fixed at one end of the piston rod at a predetermined distance from the valve body, and the retainer is fixed at a predetermined distance from the valve body. The valve body is characterized by forming a pressure chamber which communicates with one of the two oil chambers through the communication passage and the oil passage to bias the valve body in the closing direction. be. As a result, in the present invention, the oil pressure in the pressure chamber increases in accordance with the oil pressure generated in one oil chamber, and the valve body is pressed toward the opening at one end of the oil passage hole in accordance with this oil pressure. Therefore, according to the present invention, even if extremely large oil pressure is generated in one oil chamber,
The oil pressure in the pressure chamber increases accordingly and presses the valve body against the opening at one end of the oil passage hole, so the valve body is not pushed open excessively and provides sufficient damping force even against large impact forces. Obtainable.
以下、本考案を図面に基づいて説明するに、第
１図には本考案に係る油圧式シヨツクアブソーバ
の一例が示されている。この油圧式シヨツクアブ
ソーバ（以下単にシヨツクアブソーバということ
がある）において、シリンダ１０は互に同心的に
配置したインナチユーブ１１とアウタチユーブ１
２とにより構成されていて、インナチユーブ１１
の底部に固定したベースバルブ２１を通してイン
ナチユーブ１１内の内側油室１３と両チユーブ１
１，１２間の外側油室１４とが連通している。
又、ピストンロツド２２はシリンダ１０の上端開
口部に固着したロツドガイド２３、オイルシール
２４及びこれを覆蓋するシールカバー２５を液密
的かつ摺動可能に貫通しており、その下端部にバ
ルブ機構を備えたピストン３０が組付けられてい
る。ピストン３０は、シリンダ１０のインナチユ
ーブ１１内に摺動可能に嵌挿されてその中間部に
位置し、内側油室１３を上下両油室R1，R2に区
画している。 Hereinafter, the present invention will be explained based on the drawings. FIG. 1 shows an example of a hydraulic shock absorber according to the present invention. In this hydraulic shock absorber (hereinafter sometimes simply referred to as a shock absorber), a cylinder 10 has an inner tube 11 and an outer tube 1 arranged concentrically with each other.
2 and an inner tube 11
The inner oil chamber 13 in the inner tube 11 and both tubes 1 are connected to each other through the base valve 21 fixed to the bottom of the inner tube 11.
The outer oil chamber 14 between 1 and 12 communicates with each other.
Further, the piston rod 22 fluid-tightly and slidably penetrates a rod guide 23 fixed to the upper end opening of the cylinder 10, an oil seal 24, and a seal cover 25 covering the same, and is equipped with a valve mechanism at its lower end. A piston 30 is assembled. The piston 30 is slidably inserted into the inner tube 11 of the cylinder 10 and located in the middle thereof, and divides the inner oil chamber 13 into upper and lower oil chambers R 1 and R 2 .
しかして、ピストン３０は第２図に拡大して示
したように、伸張行程時に作動する第１バルブ機
構３０ａと圧縮行程時に作動する第２バルブ機構
３０ｂを備えていて、この第１バルブ機構３０ａ
に本考案が実施されている。 As shown in an enlarged view in FIG. 2, the piston 30 includes a first valve mechanism 30a that operates during the extension stroke and a second valve mechanism 30b that operates during the compression stroke.
The present invention was implemented in
ピストン３０を構成するピストン本体３１は、
環状プレート３２とカラー３３とにより挾持され
た状態にてピストンロツド２２の下端部上に嵌合
されていて、ピストンロツド２２の下端に螺着し
たピストンナツト３４にて締付固定されている。
このピストン本体３１には、第１バルブ機構３０
ａを構成する複数の第１通油孔３１ａと、第２バ
ルブ機構３０ｂを構成する複数の第２通油孔３１
ｂとが形成されている。又、ピストンナツト３４
には、外周に延びる環状のリテーナ３４ａが形成
されている。 The piston body 31 that constitutes the piston 30 is
It is fitted onto the lower end of the piston rod 22 while being held between an annular plate 32 and a collar 33, and is tightened and fixed by a piston nut 34 screwed onto the lower end of the piston rod 22.
This piston body 31 includes a first valve mechanism 30.
a plurality of first oil passage holes 31a that constitute the second valve mechanism 30b, and a plurality of second oil passage holes 31 that constitute the second valve mechanism 30b.
b is formed. Also, piston nut 34
An annular retainer 34a is formed extending around the outer periphery.
第１バルブ機構３０ａは、ピストン本体３１の
第１通油孔３１ａと、カラー３３の外周に上下動
可能に組付けられて第１通油孔３１ａの下端開口
部側に位置する弁体３５と、弁体３５とピストン
ナツト３４のリテーナ３４ａ間に介装され弁体３
５をピストン本体３１に弾撥的に当接させて第１
通油孔３１ａの下端開口部を閉じる圧縮スプリン
グ３６と、リテーナ３４ａと弁体３５間に介装さ
れた筒状の隔壁部材３７とによつて構成されてい
る。隔壁部材３７は、金属性筒体３７ａとこの上
端に固着したゴム製筒体３７ｂとからなるもの
で、弁体３５の下面に弾撥的に当接してピストン
ナツト３４とによりその内部に圧力室R3を形成
し、かつ弁体３５の下動を許容している。又、弁
体３５の筒部にはその内壁に、軸方向に延びる複
数の溝部３５ａが形成されていて、ピストンロツ
ド２２の外周とにより圧力室R3を第１通油孔３
１ａに連通させる連通路を形成している。これに
より、圧力室R3は弁体３５を閉鎖する方向へ付
勢する圧力室に構成されている。 The first valve mechanism 30a includes a first oil passage hole 31a of the piston body 31, and a valve body 35 that is attached to the outer periphery of the collar 33 so as to be movable up and down and is located on the lower end opening side of the first oil passage hole 31a. , the valve body 3 is interposed between the valve body 35 and the retainer 34a of the piston nut 34.
5 in elastic contact with the piston body 31, and the first
It is composed of a compression spring 36 that closes the lower end opening of the oil passage hole 31a, and a cylindrical partition member 37 interposed between the retainer 34a and the valve body 35. The partition member 37 is composed of a metal cylinder 37a and a rubber cylinder 37b fixed to the upper end of the metal cylinder 37a. R 3 is formed, and the valve body 35 is allowed to move downward. Further, a plurality of grooves 35a extending in the axial direction are formed on the inner wall of the cylindrical portion of the valve body 35, and the pressure chamber R3 is connected to the first oil passage hole 3 by the outer circumference of the piston rod 22.
A communication path communicating with 1a is formed. Thereby, the pressure chamber R 3 is configured to be a pressure chamber that urges the valve body 35 in a direction to close it.
第２バルブ機構３０ｂは、第２通通孔３１ｂ
と、ピストン本体３１と環状プレート３２間に介
装された弁体たるバルブプレート３８と、これら
両者３２，３８間に介装されバルブプレート３８
をピストン本体３１に弾撥的に当接させて第２通
油孔３１ｂの上端開口部を閉じる圧縮スプリング
３９とにより構成されている。 The second valve mechanism 30b has a second through hole 31b.
, a valve plate 38 which is a valve body interposed between the piston body 31 and the annular plate 32, and a valve plate 38 which is interposed between both 32 and 38.
and a compression spring 39 that resiliently abuts against the piston body 31 and closes the upper end opening of the second oil passage hole 31b.
このように構成したシヨツクアブソーバにおい
ては、圧縮行程時シリンダ１０の下方油室R2に
上方油室R1の油圧より大きな油圧が生じると、
この油圧に対応して第２バルブ機構３０ｂのバル
ブプレート３８が圧縮スプリング３９に抗して押
し開かれる。このため、下方油室R2内の作動油
の一部は第２図の破線矢印で示すように、第２通
油孔３１ｂを通つて上方油室R1内へ流入して減
衰力を発生させる。なお、下方油室R2内の作動
油の他の一部は、ベースバルブ２１のバルブ機構
を通つて外側油室１４内へも流入して減衰力を発
生させる。 In the shock absorber configured in this way, when a hydraulic pressure greater than the hydraulic pressure in the upper oil chamber R1 is generated in the lower oil chamber R2 of the cylinder 10 during the compression stroke,
In response to this oil pressure, the valve plate 38 of the second valve mechanism 30b is pushed open against the compression spring 39. Therefore, a part of the hydraulic oil in the lower oil chamber R2 flows into the upper oil chamber R1 through the second oil passage hole 31b, as shown by the broken line arrow in FIG. 2, and generates a damping force. let Note that another part of the hydraulic oil in the lower oil chamber R 2 also flows into the outer oil chamber 14 through the valve mechanism of the base valve 21 to generate damping force.
一方、当該シヨツクアブソーバにおいて、伸張
行程時シリンダ１０の上方油室R1に下方油室R2
の油圧より大きな油圧が生じると、この油圧によ
り第１バルブ機構３０ａの弁体３５が圧縮スプリ
ング３６に抗して押し開かれる。このため、上方
油室R1内の作動油の一部は第２図の実線矢印で
示すように、第１通油孔３１ａを通つて下方油室
R2内へ流入して減衰力を発生させるが、同時に
２点鎖線矢印で示すように弁体３５の溝部３５ａ
を通つて圧力室R3内へ流入しようとする。この
結果、圧力室R3内には上方油室R1内の油圧が付
与され、この圧力室R3内の油圧は上方油室R1内
の油圧に対応して弁体３５を上方へ押圧する。従
つて、弁体３５は上方油室R1内の油圧の上昇に
対応して押し開かれにくくなり、このためシヨツ
クアブソーバに大きな衝撃力が付与されても弁体
３５が過度に押し開かれることがなくて、大きな
衝撃力に対しても充分な減衰力が得られる。な
お、この伸張行程時には、外側油室１４内の作動
油の一部はベースバルブ２１のバルブ機構を通つ
て下方油室R2内へ流入し、これによつても減衰
力が発生する。 On the other hand, in the shock absorber, the upper oil chamber R1 and the lower oil chamber R2 of the cylinder 10 are connected during the extension stroke.
When a hydraulic pressure larger than the hydraulic pressure is generated, the valve body 35 of the first valve mechanism 30a is pushed open against the compression spring 36 by this hydraulic pressure. Therefore, a part of the hydraulic oil in the upper oil chamber R1 passes through the first oil passage hole 31a to the lower oil chamber, as shown by the solid arrow in FIG.
It flows into R2 and generates a damping force, but at the same time, the groove 35a of the valve body 35 as shown by the two-dot chain arrow.
attempts to flow into the pressure chamber R3 through the air. As a result, the oil pressure in the upper oil chamber R1 is applied to the pressure chamber R3 , and the oil pressure in the pressure chamber R3 presses the valve body 35 upward in response to the oil pressure in the upper oil chamber R1 . do. Therefore, the valve body 35 becomes difficult to be pushed open in response to an increase in the oil pressure in the upper oil chamber R1 , and therefore, even if a large impact force is applied to the shock absorber, the valve body 35 will not be pushed open excessively. There is no damping force, and sufficient damping force can be obtained even for large impact forces. During this extension stroke, a portion of the hydraulic oil in the outer oil chamber 14 flows into the lower oil chamber R2 through the valve mechanism of the base valve 21, which also generates a damping force.
第３図には、本実施例のシヨツクアブソーバに
おけるピストンの第１変形例が示されている。こ
のピストン４０においては、伸張行程時に作動す
る第１バルブ機構４０ａは、ピストン本体４１に
複数設けた第１通油孔４１ａと、ピストンロツド
２２の下端部外周に嵌合されピストン本４１の下
面に当接して第１通油孔４１ａの下端開口部を閉
じる弁体たる可撓性の第１バルブプレート４２
と、ピストンロツド２２の下端部外周にカラー４
３を介して嵌合されピストンロツド２２の下端に
螺着したピストンナツト４４により第１バルブプ
レート４２とともに締付固定された環状のリテー
ナ４５と、第１バルブプレート４２とリテーナ４
５間に介装されたゴム製のベローズ４６とによつ
て構成されている。ベローズ４６は、第１バルブ
プレート４２の下面とリテーナ４５の上面とに弾
撥的に当接していて、その内部に前記実施例と同
様に機能する圧力室R3を形成している。又、第
１バルブプレート４２には、ピストン本体４１に
設けた第３通油孔４１ｃに対向して貫通孔４２ａ
が形成されていて、第３通油孔４１ｃとにより圧
力室R3を上方油室R1に連通させる連通路を形成
している。なお、圧縮行程時に作動する第２バル
ブ機構４０ｂは、ピストン本体４１に複数設けた
第２通油孔４１ｂと、ピストンロツド２２の下端
部外周にピストン本体４１と一体的に締付固定さ
れその上面に当接して第２通油孔４１ｂの上端開
口部を閉じる弁体たる可撓性の第２バルブプレー
ト４７とによつて構成されている。 FIG. 3 shows a first modification of the piston in the shock absorber of this embodiment. In this piston 40, the first valve mechanism 40a, which operates during the extension stroke, is fitted into a plurality of first oil holes 41a provided in the piston body 41 and the outer periphery of the lower end of the piston rod 22, and comes into contact with the lower surface of the piston main body 41. A flexible first valve plate 42 serving as a valve body that contacts and closes the lower end opening of the first oil passage hole 41a.
and a collar 4 on the outer periphery of the lower end of the piston rod 22.
an annular retainer 45 that is tightened and fixed together with the first valve plate 42 by a piston nut 44 that is fitted through the piston rod 3 and screwed to the lower end of the piston rod 22;
5 and a rubber bellows 46 interposed between them. The bellows 46 is in elastic contact with the lower surface of the first valve plate 42 and the upper surface of the retainer 45, and forms therein a pressure chamber R3 that functions similarly to the previous embodiment. The first valve plate 42 also has a through hole 42a opposite to the third oil passage hole 41c provided in the piston body 41.
is formed, and the third oil passage hole 41c forms a communication path that communicates the pressure chamber R 3 with the upper oil chamber R 1 . The second valve mechanism 40b, which operates during the compression stroke, is integrally tightened and fixed to the piston body 41 through a plurality of second oil holes 41b provided in the piston body 41 and the outer periphery of the lower end of the piston rod 22, and is attached to the upper surface of the piston body 41. It is constituted by a flexible second valve plate 47 which is a valve body that comes into contact with and closes the upper end opening of the second oil passage hole 41b.
このように構成したピストン４０を備えたシヨ
ツクアブソーバにおいては、圧縮行程時下方油室
R2内の油圧により第２バルブプレート４７が押
し開かれ、下方油室R2内の作動油の一部が破線
矢印で示すように第２通油孔４１ｂを通つて上方
油室R1内へ流入して減衰力を発生させる。一方、
伸張行程時においては、上方油室R1内の油圧に
より第１バルブプレート４２が押し開かれ、上方
油室R1内の作動油の一部が実線矢印で示すよう
に第１通油孔４１ａを通つて下方油室R2内へ流
入して減衰力を発生させるが、同時に２点鎖線矢
印で示すように第３通油孔４１ｃ及び貫通孔４２
ａを通つて圧力室R3内へ流入しようとする。こ
の結果、圧力室R3内には上方油室R1内の油圧が
付与され、この圧力室R3内の油圧は上方油室R1
内の油室に対応して第１バルブプレート４２を押
圧する。従つて、当該ピストン４０を備えたシヨ
ツクアブソーバにおいても、前記実施例のシヨツ
クアブソーバと同様の理由により、大きな衝撃力
に対しても充分な減衰力が得られる。 In the shock absorber equipped with the piston 40 configured in this way, the lower oil chamber is closed during the compression stroke.
The second valve plate 47 is pushed open by the hydraulic pressure in R2 , and a portion of the hydraulic oil in the lower oil chamber R2 passes through the second oil passage hole 41b and enters the upper oil chamber R1 as shown by the broken line arrow. and generates a damping force. on the other hand,
During the extension stroke, the first valve plate 42 is pushed open by the hydraulic pressure in the upper oil chamber R1 , and a portion of the hydraulic oil in the upper oil chamber R1 flows into the first oil passage hole 41a as shown by the solid arrow. It flows into the lower oil chamber R 2 through the oil chamber R 2 and generates a damping force, but at the same time, as shown by the two-dot chain arrow, the third oil passage hole 41c and the through hole 42
attempts to flow into the pressure chamber R3 through a. As a result, the oil pressure in the upper oil chamber R1 is applied to the pressure chamber R3 , and the oil pressure in this pressure chamber R3 is applied to the upper oil chamber R1.
Press the first valve plate 42 corresponding to the oil chamber inside. Therefore, in the shock absorber equipped with the piston 40, sufficient damping force can be obtained even for large impact forces for the same reason as in the shock absorber of the above embodiment.
なお、上記各実施例において、圧力室R3を上
方油室R1に連通させる連通路の通路抵抗、圧力
室R3の大きさ、ゴム製筒体３７ｂやベローズ４
６の硬さを適宜選定すれば、最適な減衰力が得ら
れる。 In each of the above embodiments, the passage resistance of the communication passage that communicates the pressure chamber R3 with the upper oil chamber R1 , the size of the pressure chamber R3 , the rubber cylinder 37b and the bellows 4 are
If the hardness of No. 6 is selected appropriately, the optimum damping force can be obtained.
第４図には、ピストンの第２変形例が示されて
いる。このピストン４０Ａにおいては、ピストン
本体４１に設けた第３通油孔４１ｃ内にオリフイ
スを備えた筒状の絞り部材４８を嵌着した点を除
き、第３図に示す第１変形例のピストン４０と同
様に構成されている。このため、入力周波数に対
して位相遅れが発生し、絞り部材４８のオリフイ
ス径、圧力室R3の大きさ、ベローズ４６の硬さ
を適宜選定することにより、最適な減衰力が得ら
れる。その他は、第３図に示した変形例と同じで
あるため、同一部材には同一符号を付してその説
明は省略する。 FIG. 4 shows a second modification of the piston. This piston 40A is the same as the piston 40 of the first modified example shown in FIG. It is configured in the same way. Therefore, a phase lag occurs with respect to the input frequency, and by appropriately selecting the orifice diameter of the throttle member 48, the size of the pressure chamber R3 , and the hardness of the bellows 46, an optimal damping force can be obtained. The rest is the same as the modification shown in FIG. 3, so the same members are given the same reference numerals and their explanations will be omitted.
なお、上記各変形例のピストン４０において
は、圧力室R3を形成する隔壁部材としてゴム製
のベローズ４６を採用しているが、これに換えて
金属性、プラスチツク製のベローズ、プラスチツ
ク製、ゴム製のＯリング、角リング等軸方向に可
撓性の種々の筒状又は環状の隔壁部材を採用する
ことができる。 In the piston 40 of each of the above-mentioned modifications, a rubber bellows 46 is used as the partition wall member forming the pressure chamber R3 , but instead of this, a metal bellows, a plastic bellows, a plastic bellows, a rubber bellows, etc. are used. Various axially flexible cylindrical or annular partition members can be employed, such as a manufactured O-ring or a square ring.
又、上記実施例及び変形例においては、本考案
を伸張行程時に作動するバルブ機構に実施した例
について示したが、本考案は圧縮行程時に作動す
るバルブ機構に対しても実施し得るものである。
さらに又、上記実施例においては、本考案を複筒
のシリンダを備えた油圧式シヨツクアブソーバに
実施した例について示したが、本考案は単筒のシ
リンダとその内部にガス室を形成するフリーピス
トンを備えたドカルボン式のシヨツクアブソーバ
等にも実施し得るものである。 Furthermore, in the above embodiments and modifications, examples were shown in which the present invention was applied to a valve mechanism that operates during the extension stroke, but the present invention can also be implemented to a valve mechanism that operates during the compression stroke. .
Furthermore, in the above embodiment, an example was shown in which the present invention was applied to a hydraulic shock absorber equipped with a double-cylinder cylinder, but the present invention has a single-cylinder cylinder and a free piston that forms a gas chamber inside the cylinder. It can also be implemented in a decarboxylic shock absorber, etc. equipped with
第１図は本考案に係るシヨツクアブソーバの一
例を示す一部省略縦断面図、第２図は同シヨツク
アブソーバに採用したピストンの拡大縦断面図、
第３図はピストンの第１変形例を示す拡大縦断面
図、第４図はピストンの第２変形例を示す拡大縦
断面図である。
符号の説明、１０……シリンダ、１１，１２…
…チユーブ、２２……ピストンロツド、３０……
ピストン、３０ａ，３０ｂ……バルブ機構、３１
……ピストン本体、３１ａ，３１ｂ……通油孔、
３４ａ……リテーナ、３５……弁体、３５ａ……
溝部、３６……圧縮スプリング、３７……隔壁部
材、４０，４０Ａ……ピストン、４０ａ，４０ｂ
……バルブ機構、４１……ピストン本体、４１
ａ，４１ｂ，４１ｃ……通油孔、４２……第１バ
ルブプレート、４５……リテーナ、４６……ベロ
ーズ、R1……上方油室、R2……下方油室、R3…
…圧力室。
FIG. 1 is a partially omitted vertical sectional view showing an example of a shock absorber according to the present invention, and FIG. 2 is an enlarged vertical sectional view of a piston adopted in the same shock absorber.
FIG. 3 is an enlarged longitudinal sectional view showing a first modification of the piston, and FIG. 4 is an enlarged longitudinal sectional view showing a second modification of the piston. Explanation of symbols, 10...Cylinder, 11, 12...
...Tube, 22...Piston rod, 30...
Piston, 30a, 30b...Valve mechanism, 31
... Piston body, 31a, 31b ... Oil hole,
34a...retainer, 35...valve body, 35a...
Groove portion, 36... Compression spring, 37... Partition member, 40, 40A... Piston, 40a, 40b
... Valve mechanism, 41 ... Piston body, 41
a, 41b, 41c...oil hole, 42...first valve plate, 45...retainer, 46...bellows, R1...upper oil chamber, R2 ... lower oil chamber, R3 ...
...pressure chamber.
Claims (1)
開口端部を液密的かつ摺動可能に貫通するピスト
ンロツドと、このピストンロツドの一端部に組付
けられ前記シリンダ内に摺動可能に嵌挿されて同
シリンダ内を２つの油室に区画するピストンと、
このピストンに設けられ前記両油室を連通させる
通油孔とこの通油孔をその一端開口部側から弾撥
的に閉じる弁体を有するバルブ機構を具備して、
前記ピストンの相対的摺動により前記バルブ機構
を通して前記両油室の一方の油室内の作動油を他
方の油室内へ流動させるようにした車両用油圧式
シヨツクアブソーバにおいて、前記バルブ機構を
構成する弁体に前記通油孔又はこれとは独立して
前記ピストンに設けた通油孔に連通する連通路を
設け、かつ前記ピストンロツドの一端部にて前記
弁体に対向して所定間隔を保つて固定したリテー
ナと前記弁体間に軸方向に可撓性の筒状又は環状
の隔壁部材を介在してその内部に圧力室を形成
し、この圧力室を前記連通路及び通油孔を通して
前記両油室の一方の油室に連通させて前記弁体を
閉じる方向へ付勢する圧力室に構成したことを特
徴とする車両用油圧式シヨツクアブソーバ。 A cylinder containing hydraulic oil, a piston rod that fluid-tightly and slidably penetrates the open end of the cylinder, and a piston rod that is assembled to one end of the piston rod and is slidably inserted into the cylinder. A piston that divides the inside of the cylinder into two oil chambers,
The piston is provided with a valve mechanism having an oil passage hole that communicates the two oil chambers, and a valve body that elastically closes the oil passage hole from the opening side of one end thereof,
In the hydraulic shock absorber for a vehicle, the hydraulic oil in one of the two oil chambers is caused to flow into the other oil chamber through the valve mechanism by relative sliding of the piston, and the valve forming the valve mechanism. A communication passage is provided in the body to communicate with the oil passage hole or independently of the oil passage hole provided in the piston, and the piston rod is fixed at one end thereof facing the valve body at a predetermined distance. A flexible cylindrical or annular partition member is interposed in the axial direction between the retainer and the valve body to form a pressure chamber therein. 1. A hydraulic shock absorber for a vehicle, characterized in that the pressure chamber is configured to communicate with one of the oil chambers and bias the valve body in a closing direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15556282U JPS5959540U (en) | 1982-10-14 | 1982-10-14 | Hydraulic shock absorber for vehicles |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15556282U JPS5959540U (en) | 1982-10-14 | 1982-10-14 | Hydraulic shock absorber for vehicles |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5959540U JPS5959540U (en) | 1984-04-18 |
| JPS633479Y2 true JPS633479Y2 (en) | 1988-01-28 |
Family
ID=30343536
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15556282U Granted JPS5959540U (en) | 1982-10-14 | 1982-10-14 | Hydraulic shock absorber for vehicles |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5959540U (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100505126B1 (en) * | 2001-01-16 | 2005-08-03 | 주식회사 만도 | Body valve use in a shock absorber |
| JP2002357236A (en) * | 2001-06-01 | 2002-12-13 | Showa Corp | Check valve structure of hydraulic absorber |
| KR100757808B1 (en) | 2002-12-16 | 2007-09-11 | 주식회사 만도 | Body valve use in a shock absorber |
| JP2010230065A (en) * | 2009-03-26 | 2010-10-14 | Kayaba Ind Co Ltd | Valve seat body |
| JP5568146B2 (en) * | 2013-01-22 | 2014-08-06 | カヤバ工業株式会社 | Valve seat body |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5214182A (en) * | 1975-07-24 | 1977-02-02 | Showa Mfg Co Ltd | Attenuation force generating valve device of an oil pressure shock abs orber |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5921283Y2 (en) * | 1979-04-23 | 1984-06-22 | 株式会社 昭和製作所 | Hydraulic cylinder for inboard and outboard motors |
-
1982
- 1982-10-14 JP JP15556282U patent/JPS5959540U/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5214182A (en) * | 1975-07-24 | 1977-02-02 | Showa Mfg Co Ltd | Attenuation force generating valve device of an oil pressure shock abs orber |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5959540U (en) | 1984-04-18 |
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