JPS6037473Y2 - hydraulic shock absorber - Google Patents
hydraulic shock absorberInfo
- Publication number
- JPS6037473Y2 JPS6037473Y2 JP17651279U JP17651279U JPS6037473Y2 JP S6037473 Y2 JPS6037473 Y2 JP S6037473Y2 JP 17651279 U JP17651279 U JP 17651279U JP 17651279 U JP17651279 U JP 17651279U JP S6037473 Y2 JPS6037473 Y2 JP S6037473Y2
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- piston
- inner cylinder
- force
- pressure
- 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
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Description
【考案の詳細な説明】
本考案は油圧緩衝器に関し、特に内外筒を有する型の油
圧緩衝器に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic shock absorber, and more particularly to a hydraulic shock absorber having an inner and outer cylinder.
従来、内外筒を有する型の油圧緩衝器では、緩衝作用の
程度は、内筒側壁に設けられる連通孔としてのオリフィ
スの数、位置、大きさ等を所望に応じて設定することに
より調整されている。Conventionally, in a type of hydraulic shock absorber having an inner and outer cylinder, the degree of buffering effect has been adjusted by setting the number, position, size, etc. of orifices as communication holes provided in the side wall of the inner cylinder as desired. There is.
この場合、所望の衝撃力の範囲内ではＳ゛一定抵抗力を
ピストンに及ぼすようにオリフィスが形成される。In this case, the orifice is formed so as to exert a constant resistance force S on the piston within the range of the desired impact force.
しかし乍ら、特定のオリフィスの数、大きさ等を有する
一つの緩衝器では、衝撃力の大きさにより、緩衝機能を
もたらすべき抵抗力の働き方が大きく異なる。However, in a single shock absorber having a specific number, size, etc. of orifices, the way the resistance force that provides the buffer function differs greatly depending on the magnitude of the impact force.
従って、例えば、比較的小さい衝撃力に合わせてオリフ
ィスが設定された緩衝器に対して、大きい衝撃力が加え
られると、ピストンがオリフィスによる油の流れの抵抗
に帰因する抵抗によっては停止され得す、内筒中に深く
嵌入されて、油をピストン先端面と内筒とによって形成
される室内にとじ込めてしまうため、ピストンに非常に
大きな抵抗力が働いてしまう。Thus, for example, if a large impact force is applied to a shock absorber with an orifice set for relatively small impact forces, the piston may be stopped due to the resistance due to the resistance of oil flow through the orifice. However, since the piston is deeply inserted into the inner cylinder and oil is trapped in the chamber formed by the piston tip surface and the inner cylinder, a very large resistance force acts on the piston.
この結果実際上、緩衝器は緩衝作用を十分には威し得な
いのみならず、緩衝器が破損されてしまう恐れもある。As a result, in practice, not only is the buffer not able to provide a sufficient buffering effect, but there is also a risk that the buffer will be damaged.
本考案は前記諸点に鑑み威されたものでありその目的と
するところは、広い範囲の大きさの衝撃力に対して十分
安定に緩衝作用を発揮し得る油圧緩衝器を提供すること
にある。The present invention has been developed in view of the above points, and its purpose is to provide a hydraulic shock absorber that can sufficiently and stably exert a shock absorbing effect against impact forces having a wide range of magnitudes.
前記目的は、本考案によれば、両端が閉塞された内筒と
、前記内筒内部を第１及び第２の室に画成すべ前記内筒
内部に摺動自在に嵌合されており、前記第１の室を貫通
して前記内筒の一端から突出したピストンロッドを一端
に有するピストンと、前記第１及び第２の室間の圧力差
を調整すべく前記ピストンに設けられた調圧弁と、前記
内筒と共に、第３の室を形成すべく前記内筒の外周に設
けられた両端が閉塞され、且つ前記ピストンロッドが一
端から突出した外筒と、前記第１１第２及び第３の室を
連通すべく前記内筒の側面に設けられた複数の連通孔と
からなり、
前記第１１第２及び第３の室は全体として液密且つ気密
に形成されており、
前記調圧弁は、前記第２の室の前記連通孔を介する前記
第３の室への連通を許容する第１位置に前記ピストンが
もたらされた際には閉弁状態に設定されるべく、前記第
２の室の室圧によって及ぼされる力よりも大きく且つこ
れに対向する方向の力で付勢される一方、前記の第２の
室の前記連通孔を介する前記第３の室への連通を阻止す
る第２位置に前記ピストンがもたらされた際には開弁状
態に設定されるべく、前記第２の室の室圧によって及ぼ
される力よりも小さく且つこれに対向する方向の力で付
勢されるように構成されてなる油圧緩衝器によって遠戚
される。According to the present invention, the object is to include an inner cylinder whose both ends are closed, and which is slidably fitted into the inner cylinder so as to define the inside of the inner cylinder into first and second chambers. A piston having at one end a piston rod that penetrates the first chamber and protrudes from one end of the inner cylinder, and a pressure regulating valve provided on the piston to adjust the pressure difference between the first and second chambers. an outer cylinder provided on the outer periphery of the inner cylinder to form a third chamber together with the inner cylinder, both ends of which are closed, and from which the piston rod protrudes from one end; a plurality of communication holes provided on the side surface of the inner cylinder to communicate the chambers, the eleventh second and third chambers are formed as a whole to be liquid-tight and airtight, and the pressure regulating valve is , the second chamber is set to a closed state when the piston is brought to a first position that allows communication of the second chamber with the third chamber through the communication hole; a second chamber biased by a force greater than and in a direction opposite to the force exerted by the chamber pressure of the chamber, while blocking communication of the second chamber to the third chamber through the communication hole; When the piston is brought to the second position, it is biased with a force that is smaller than and in a direction opposite to the force exerted by the chamber pressure of the second chamber so that the valve is set in the open state. It is distantly related to the hydraulic shock absorber, which is configured as follows.
次に本考案の好ましい一具体例を図面に基づいて説明す
る。Next, a preferred embodiment of the present invention will be explained based on the drawings.
図中１は外筒であり、２は内筒である。In the figure, 1 is an outer cylinder, and 2 is an inner cylinder.
外筒１と内筒２とは一方の端部３で蓋４に固着されると
共に、他方の端部５で取付板６に固着されて第三の室と
しての室７を形成している。The outer cylinder 1 and the inner cylinder 2 are fixed to a lid 4 at one end 3 and fixed to a mounting plate 6 at the other end 5 to form a chamber 7 as a third chamber.
取付板６は所望の台座に取り付けられて固定される。The mounting plate 6 is attached and fixed to a desired pedestal.
内筒２内には第一の室としての室８と第二の室としての
室９とを形成してピストン１０が摺動自在に嵌合されて
おり、ピストン１０に連結されたピストンロッド１１は
室８を貫通すると共に蓋４から突出している。Inside the inner cylinder 2, a chamber 8 as a first chamber and a chamber 9 as a second chamber are formed, into which a piston 10 is slidably fitted, and a piston rod 11 connected to the piston 10. penetrates the chamber 8 and protrudes from the lid 4.
ピストンロッド１１の突出端１２には衝撃力を受けとめ
る被衝突板１３が設けられており、被衝突板１３と蓋４
との間には、被衝突板１３乃至ピストン１０を初期位置
に設定すべくバネ１４が設けられている。A collided plate 13 that receives impact force is provided on the protruding end 12 of the piston rod 11, and the collided plate 13 and the lid 4
A spring 14 is provided between the collided plate 13 and the piston 10 to set them at their initial positions.
端部３近傍の内筒２側面には、室８と室７とを連通すべ
く通路１５が設けられており、また、端部から距離１゜
離れたピストン１０の先端１６の初期位置Ａからピスト
ン１０の嵌入される方向に距離１□離れた位置Ｂまでの
間の内筒２の側面には室７と室８及び９を連通すべくｎ
個のオリフィスａ□、ａ２．・・・・・・、ａｎが設け
られている。A passage 15 is provided on the side surface of the inner cylinder 2 near the end 3 to communicate the chambers 8 and 7, and from the initial position A of the tip 16 of the piston 10 at a distance of 1° from the end. On the side surface of the inner cylinder 2 up to position B, which is a distance 1 □ away in the direction in which the piston 10 is inserted, there is a hole n to communicate the chamber 7 with the chambers 8 and 9.
orifices a□, a2. . . . and an are provided.
室８及び９は油で満たされており、油溜めとしての室７
には油と気体とが入れられている。Chambers 8 and 9 are filled with oil, with chamber 7 serving as an oil reservoir.
contains oil and gas.
内室？、 ８．９からなる室１７は液密且つ気密に形成
されている。Inner room? , 8.9 is formed to be liquid-tight and air-tight.
ピストン１０には室９と室８との間の圧力差を調整すべ
く調圧弁１８が設けられている。A pressure regulating valve 18 is provided in the piston 10 to adjust the pressure difference between the chamber 9 and the chamber 8.
調圧弁１Ｂはピストン１０内に形成された空洞１９と、
空洞１９と室８とを連通ずる通路２０と、空洞１９と室
９とを連通ずる孔２１を有する弁座２２と、孔２１と係
合される突出部２３を有する弁体２４と、一端で弁体２
４に連結されると共に他端２５でピストン１０の壁部２
６に摺動自在に嵌合されて弁体２４の位置決めを助ける
ロッド２７と、壁部２６と弁体２４との間に設けられ、
弾性力で弁体２４を弁座２２に押圧するバネ２８とから
戊る。The pressure regulating valve 1B includes a cavity 19 formed in the piston 10,
A valve seat 22 having a passage 20 communicating between the cavity 19 and the chamber 8, a hole 21 communicating the cavity 19 and the chamber 9, a valve body 24 having a protrusion 23 that is engaged with the hole 21, and a valve body 24 having one end. Valve body 2
4 and is connected to the wall 2 of the piston 10 at the other end 25.
a rod 27 that is slidably fitted into the valve body 6 and helps position the valve body 24; and a rod 27 that is provided between the wall portion 26 and the valve body 24;
The elastic force separates the valve body 24 from the spring 28 that presses it against the valve seat 22.
弁体２４は、ピストン１０がオリフィスａｎのみが室９
と室７とを連通させる第１位置にもたらされた際には、
閉弁状態に設定されるべく、室９の室圧によって及ぼさ
れる力よりも大きく且つこれに対向する方向のバネ２８
の弾性力によって弁座２２に押し付けられる一方、ピス
トン１０がオリフィスａｎを塞ぐ第２位置にもたらされ
た際には開弁状態に設定されるべく、室９の室圧によっ
て及ぼされる力よりも小さく且つこれ対向する方向のバ
ネ２８の弾性力で弁座２２に押し付けられている。The valve body 24 has only the orifice an of the piston 10 and the chamber 9.
When brought to the first position communicating with chamber 7,
The spring 28 is larger than and in a direction opposite to the force exerted by the chamber pressure in the chamber 9 to set the valve in the closed state.
is pressed against the valve seat 22 by the elastic force of It is pressed against the valve seat 22 by the elastic force of a small spring 28 in the opposite direction.
従って、ピストン１０が第１位置にもたらされた際には
、弁体２４はバネ２８の弾性力により押し付けられたま
まであり、孔２１は閉じられている。Therefore, when the piston 10 is brought to the first position, the valve body 24 remains pressed by the elastic force of the spring 28, and the hole 21 is closed.
しかし乍ら、ピストン１０が第２位置にもたらされた際
には、弁体２４はバネ２８の弾性力に抗してＥ方向に移
動され、弁体２４は弁座２２から離間される。However, when the piston 10 is brought to the second position, the valve body 24 is moved in the E direction against the elastic force of the spring 28, and the valve body 24 is separated from the valve seat 22.
その結果室９と空洞１９とは穴２１を介して連通され、
室９内の油は孔２１、空洞１９、通路２０を通って室８
に導入され、室９と室８との圧力差は低下し、ピストン
１０にＥ方向に働く抵抗力Ｇは減少する。As a result, the chamber 9 and the cavity 19 are communicated via the hole 21,
The oil in chamber 9 passes through hole 21, cavity 19, and passage 20 to chamber 8.
, the pressure difference between chambers 9 and 8 decreases, and the resistance force G acting on the piston 10 in the E direction decreases.
調圧弁１８はピストン１０が室９方向（Ｄ方向）に深く
嵌入されて、ピストン１０の先端部１６が最後のオリフ
ィスａｎを通過した際、室８が液密となり、ピストン１
０に過大なＥ方向の抵抗力Ｇが働くのを防止している。When the piston 10 is deeply inserted in the direction of the chamber 9 (direction D) and the tip 16 of the piston 10 passes through the last orifice an, the pressure regulating valve 18 becomes liquid-tight, and the piston 1
This prevents an excessive resistance force G in the E direction from acting on the zero point.
しかも調圧弁１８は、ピストン１０が過大な速度でＤ方
向に押される際ピストン１０の先端部１６が位置ＡとＢ
との間にある場合においてもピストン１０に過大な抵抗
力ＧがＥ方向に働くことを妨げる働きをし得る。Moreover, the pressure regulating valve 18 is configured such that when the piston 10 is pushed in the D direction at an excessive speed, the tip end 16 of the piston 10 is at the positions A and B.
Even if it is between , it can work to prevent excessive resistance force G from acting on the piston 10 in the E direction.
前記の如く構成された本考案の油圧緩衝器２９において
、ピストン１０が初期位置にあり、先端部１６が位置Ａ
にある際、被衝突板１３にＤ方向に衝撃力Ｆが加えられ
るとする。In the hydraulic shock absorber 29 of the present invention configured as described above, the piston 10 is at the initial position and the tip end 16 is at the position A.
It is assumed that an impact force F is applied to the collided plate 13 in the D direction when the collision occurs.
この力Ｆに応じてピストン１０はＤ方向にある速度で移
動される。In response to this force F, the piston 10 is moved in the D direction at a certain speed.
このとき室９の油はオリフィスａｎ、 ａｎｌ ｔ
ａｎ ２？・・・・・・・・・ａ□を通って室７に
入り、また室７の油は通路１５を通って室８に入る。At this time, the oil in chamber 9 flows through the orifice an, anl t
An 2? ......The oil in chamber 7 enters chamber 7 through a□, and the oil in chamber 7 enters chamber 8 through passage 15.
オリフィスａｎ、ａｏ１．・・・・・・ａ、が油の流れ
に及ぼす抵抗に帰因して、室９内の油がピストン１０に
Ｅ方向に及ぼす抵抗力及び、ロッド１１が室８に入って
室７の気体の体積が減少したことによる室？、 ８．
９の圧力増加のためにピストンにＥ方向に働く力の和
としてピストンに働く抵抗力Ｇに抗してピストンがＤ方
向に移動されるため、ピストンのＤ方向の速度は減少す
る。Orifice an, ao1. Due to the resistance exerted by a on the oil flow, the oil in the chamber 9 exerts a resistance force on the piston 10 in the E direction, and the rod 11 enters the chamber 8 and the gas in the chamber 7 chamber due to a decrease in the volume of? , 8.
Since the piston is moved in the D direction against the resistance force G acting on the piston as the sum of the forces acting on the piston in the E direction due to the pressure increase of 9, the speed of the piston in the D direction decreases.
力Ｆが比較的弱い場合ピストンがＤ方向に進むにつれて
、室９と室７とを連通ずるオリフィスの数が減少し、（
ピストンの移動速度が一定なら油の流路抵抗が増大する
が）ピストンのＤ方向の速度も徐々に減少するために油
の流路抵抗ははＳ゛一定保たれる。When the force F is relatively weak, as the piston advances in the direction D, the number of orifices communicating the chambers 9 and 7 decreases, (
If the moving speed of the piston is constant, the oil flow path resistance will increase; however, since the speed of the piston in the D direction also gradually decreases, the oil flow path resistance S is kept constant.
従ってピストン１０に働く抵抗力Ｇは（気体の圧力変化
が無視てきる程度とした場合）ピストン１０のＤ方向へ
の移動中はＳ゛一定保たれ、ピストン１０はＡＢ間の適
当な位置で実際上停止する。Therefore, the resistance force G acting on the piston 10 (assuming that the change in gas pressure is negligible) is kept constant S while the piston 10 is moving in the D direction, and the piston 10 is actually located at an appropriate position between AB. Stop above.
（尚、気体の圧力変化が大きい場合でもオリフィスａ１
゜・・・・・・、 ａｎの相互の大きさ等を適当に設
定することによりはＳ゛一定抵抗力Ｇを生じさせ得る。(Note that even if the gas pressure change is large, the orifice a1
By appropriately setting the mutual sizes of ゜..., an, it is possible to generate a constant resistance force G.
）しかし乍ら、力Ｆが大きい場合には、ピストン１０の
先端１６がＢ点に近づき、室９と室７とを連通ずるオリ
フィスの数が減少しても、極端な場合例えば最後のオリ
フィスａｎのみが室９と室７とを連通ずる状態になって
もピストン１０はまだかなりの速度でＤ方向に移動する
ため、油の流路抵抗が非常に大きくなりピストンに働く
抵抗力Ｇは増大する。) However, if the force F is large, the tip 16 of the piston 10 approaches point B, and even if the number of orifices communicating the chambers 9 and 7 decreases, in extreme cases, for example, the last orifice an Even when the piston 10 is in a state where the chambers 9 and 7 are in communication, the piston 10 still moves in the D direction at a considerable speed, so the oil flow path resistance becomes very large and the resistance force G acting on the piston increases. .
しかしながら、調圧弁１８がピストン１０に設けられて
いるため、たとえピストンが最後のオリフィスａｎを徐
々に塞ぐにつれて室９の油圧が大きくなっても、室９の
油圧と室８の油圧との差が所与の値に達すると、換言す
ればピストン１０に働く抵抗力Ｇが実際上所与の値Ｇ１
に達すると、調圧弁が作動して室９の油を室８に導くた
め、ピストン１０は実際上Ｇ１以上の抵抗力を受けるこ
となく、Ｂ−Ｃ間を進みＢ−Ｃ間の適当な位置で停止す
る。However, because the pressure regulating valve 18 is provided in the piston 10, even if the oil pressure in the chamber 9 increases as the piston gradually closes the last orifice an, the difference between the oil pressure in the chamber 9 and the oil pressure in the chamber 8 will be When a given value is reached, in other words the resistance force G acting on the piston 10 actually reaches the given value G1.
When the pressure is reached, the pressure regulating valve operates and guides the oil in chamber 9 to chamber 8, so that the piston 10 actually moves between B and C without being subjected to a resistance force greater than G1 and reaches an appropriate position between B and C. Stop at.
通常衝突後あるいはピストン速度の大きなところでは調
圧弁の弁体２４は振動を生じたり開弁状態の変動など不
安定さを伴なうが、ピストン１０のストローク終点（Ｂ
−Ｃ間）付近でのピストン１０の速度は小さく且つ弁体
２４に働く力は安定しているので弁１８の開度はピスト
ン１０の速度に追従する。Normally, after a collision or when the piston speed is high, the valve body 24 of the pressure regulating valve is unstable, such as vibrations and fluctuations in the valve opening state.
- C) is small and the force acting on the valve body 24 is stable, so the opening degree of the valve 18 follows the speed of the piston 10.
また、オリフィスａ１．ａ２．・・・・・・、ａｎと調
圧弁１８は作用位置、圧力範囲を異ならせて独立作用と
しているので各々の機能が安定している。Also, the orifice a1. a2. . . ., an and the pressure regulating valve 18 have different operating positions and pressure ranges and operate independently, so each function is stable.
さらに、本考案の油圧緩衝器においては、前述のごとく
、調圧弁が、ピストンがオリフィスａｎのみが開放され
ている第１位置にもたらされた際には閉弁状態に設定さ
れるべく、第２の室の室圧によって及ぼされる力よりも
大きく且つこれに対向する方向の力で付勢される一方、
前記ピストンがオリフィスａｎが閉塞された第２位置に
もたらされた際には開弁状態に設定されるべく、前記第
２の室の室圧によって及ぼされる力よりも小さく且つこ
れに対向する方向の力で付勢されるように構成されてい
るため、所望の衝撃力の範囲内で良好な緩衝機能を発揮
するよう構成された緩衝器に対して前述の範囲を超える
衝撃力を加えられた時にも、その大きな衝撃力によって
、第２の室が完全な液密状態にされていることによって
、緩衝機能を発揮し得ないばかり緩衝器事態が破損して
しまうことを防止し得るものである。Furthermore, in the hydraulic shock absorber of the present invention, as described above, the pressure regulating valve is set to the closed state when the piston is brought to the first position where only the orifice an is open. while being biased by a force greater than and in a direction opposite to the force exerted by the chamber pressure of the second chamber;
a force smaller than and in a direction opposite to the force exerted by the chamber pressure in the second chamber so as to be set in the open state when the piston is brought to a second position with the orifice an occluded; Because the shock absorber is configured to be biased by a force that exceeds the aforementioned range, it In some cases, by making the second chamber completely liquid-tight due to the large impact force, it is possible to prevent the shock absorber from being damaged and unable to perform its shock absorbing function. .
すなわち、本考案においては、オリフィスの設定条件に
より希望の緩衝器を提供すると共に、調圧弁によって、
更に広範囲の衝撃力に良好に対応し得、長期間の使用に
たえ得る油圧緩衝器を提供し得るのである。That is, in the present invention, the desired buffer is provided by the setting conditions of the orifice, and the pressure regulating valve is used to provide the desired buffer.
Furthermore, it is possible to provide a hydraulic shock absorber that can respond well to a wide range of impact forces and can be used for a long period of time.
以上の如く本考案の油圧緩衝器は広い範囲の衝撃力に対
して有効かつ安定な緩衝機能を発揮し得る。As described above, the hydraulic shock absorber of the present invention can exhibit an effective and stable shock absorbing function against a wide range of impact forces.
第１図は本考案の好ましい一具体例における油圧緩衝器
の説明図、第２図は本考案の具体例の油圧緩衝器のピス
トンに働く抵抗力の変化を示すグラフである。
１・・・・・・外筒、２・・・・・・内筒、？、 ８．
９． １７・・・・・・室、
１０・・・・・・ピストン、
１１・・・・・・ピストンロッ
ド、
１５・・・・・・通路、
１６・・・・・・先端部、
１８・・・・・・調
圧弁、
２９・・・・・・油圧緩衝器、ａｌ。
ａ２゜
ａ３゜
ａｎ・・・・・・オリフィス。FIG. 1 is an explanatory diagram of a hydraulic shock absorber in a preferred embodiment of the present invention, and FIG. 2 is a graph showing changes in the resistance force acting on the piston of the hydraulic shock absorber in a specific embodiment of the present invention. 1... Outer cylinder, 2... Inner cylinder? , 8.
9. 17... Chamber, 10... Piston, 11... Piston rod, 15... Passage, 16... Tip, 18... ...Pressure regulating valve, 29...Hydraulic shock absorber, al. a2゜a3゜an... Orifice.
Claims (1)
の室に画成すべく前記内筒内部に摺動自在に嵌合されて
おり、前記第１の室を貫通して前記内筒の一端から突出
したピストンロッドを一端に有するピストンと、前記第
１及び第２の室間の圧力差を調整すべく前記ピストンに
設けられた調圧弁と、前記内筒と共に、第３の室を形成
すべく前記内筒の外周に設けられた両端が閉塞され、且
つ前記ピストンロッドが一端から突出した外筒と、前記
第１、第２及び第３の室を連通すべく前記内筒の側面に
設けられた複数の連通孔とからなり、 前記第１、第２及び第３の室は全体として液密且つ気密
に形成されており、 前記調圧弁は、前記第２の室の前記連通孔を介する第３
の室への連通を許容する第１位置に前記ピストンがもた
らされた際には閉弁状態に設定されるべく、前記第２の
室の室圧によって及ぼされる力よりも大きく且つこれに
対向する方向の力で付勢される一方、前記第２の室の前
記連通孔を介する第３の室への連通を阻止をする第２位
置に前記ピストンがもたらされた際には開弁状態に設定
されるべく、前記第２の室の室圧によって及ぼされる力
よりも小さく且つこれに対向する方向の力で付勢される
ように構成されてなる油圧緩衝器。[Claims for Utility Model Registration] An inner cylinder whose both ends are closed;
a piston that is slidably fitted inside the inner cylinder to define a chamber, and has a piston rod at one end that extends through the first chamber and protrudes from one end of the inner cylinder; and a pressure regulating valve provided on the piston to adjust the pressure difference between the second chamber and both ends provided on the outer periphery of the inner cylinder to form a third chamber together with the inner cylinder, The piston rod comprises an outer cylinder from which the piston rod protrudes from one end, and a plurality of communication holes provided in the side surface of the inner cylinder to communicate the first, second and third chambers, The second and third chambers are formed to be liquid-tight and airtight as a whole, and the pressure regulating valve is configured to connect the second chamber to the third chamber through the communication hole of the second chamber.
a force greater than and opposite to the force exerted by the chamber pressure of the second chamber so that the valve is set to a closed state when the piston is brought to a first position permitting communication to the second chamber; On the other hand, when the piston is brought to a second position where the second chamber is prevented from communicating with the third chamber through the communication hole, the valve is in an open state. A hydraulic shock absorber configured to be biased by a force smaller than and in a direction opposite to the force exerted by the chamber pressure of the second chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17651279U JPS6037473Y2 (en) | 1979-12-20 | 1979-12-20 | hydraulic shock absorber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17651279U JPS6037473Y2 (en) | 1979-12-20 | 1979-12-20 | hydraulic shock absorber |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5693540U JPS5693540U (en) | 1981-07-25 |
| JPS6037473Y2 true JPS6037473Y2 (en) | 1985-11-08 |
Family
ID=29687140
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17651279U Expired JPS6037473Y2 (en) | 1979-12-20 | 1979-12-20 | hydraulic shock absorber |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6037473Y2 (en) |
-
1979
- 1979-12-20 JP JP17651279U patent/JPS6037473Y2/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5693540U (en) | 1981-07-25 |
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