JPS6331015B2 - - Google Patents

Info

Publication number
JPS6331015B2
JPS6331015B2 JP177581A JP177581A JPS6331015B2 JP S6331015 B2 JPS6331015 B2 JP S6331015B2 JP 177581 A JP177581 A JP 177581A JP 177581 A JP177581 A JP 177581A JP S6331015 B2 JPS6331015 B2 JP S6331015B2
Authority
JP
Japan
Prior art keywords
chamber
oil
spool
pressure
hydraulic
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
JP177581A
Other languages
Japanese (ja)
Other versions
JPS57116946A (en
Inventor
Mitsuhiro Kashima
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.)
KYB Corp
Original Assignee
Kayaba Industry 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 Kayaba Industry Co Ltd filed Critical Kayaba Industry Co Ltd
Priority to JP177581A priority Critical patent/JPS57116946A/en
Publication of JPS57116946A publication Critical patent/JPS57116946A/en
Publication of JPS6331015B2 publication Critical patent/JPS6331015B2/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
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/52—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics in case of change of temperature

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Safety Valves (AREA)
  • Fluid-Damping Devices (AREA)

Description

【発明の詳細な説明】 本発明は車両用の油圧緩衝器に関する。[Detailed description of the invention] The present invention relates to a hydraulic shock absorber for a vehicle.

従来の油圧緩衝器は、一般的にその内部に気体
室と油溜室を有し、ピストンロツドの侵入体積分
を気体室の収縮で補償するようにしている。この
場合、圧側伸側作動時の減衰力は、ピストン速度
に応じて発生し、速度が上昇するほど高い減衰力
が得られるようになつているが、ピストン位置、
つまりストローク位置によつて減衰力は変化する
ことはなかつた。 A conventional hydraulic shock absorber generally has a gas chamber and an oil reservoir chamber therein, and the intrusion volume of the piston rod is compensated for by contraction of the gas chamber. In this case, the damping force during the compression side and expansion side operation is generated according to the piston speed, and as the speed increases, a higher damping force is obtained, but the piston position,
In other words, the damping force did not change depending on the stroke position.

このため、例えば次のような問題があつた。す
なわち、ストリート系車両の油圧緩衝器では、路
面の起伏が小さいので減衰力を比較的小さく設定
し、応答性を良くしている。しかしコーナリング
時にあつては、車体が沈み込むことから、この沈
み込んだ状態で減衰力が小さいと、操安性が非常
に悪くなる。従つてフロントフオークやリヤフオ
ークの減衰力は1G近辺では小さくする一方、コ
ーナリング時には大きくして車体の接地性を良く
することが要求されている。 For this reason, the following problems arose, for example. That is, in hydraulic shock absorbers for street vehicles, the damping force is set relatively small because the road surface has small undulations, and the response is improved. However, when cornering, the vehicle body sinks, and if the damping force is small in this sunken state, handling becomes extremely poor. Therefore, while the damping force of the front fork and rear fork should be small around 1G, it is required to increase it during cornering to improve the ground contact of the vehicle body.

オフロード系車両の油圧緩衝器では、そのスト
ローク量も大きく、路面の起伏も大きいから、通
常走行での減衰力も比較的大きく設定されてい
る。しかしこの減衰力は最圧縮近辺からの伸び作
動にも抵抗を与えるため、伸び作動の途中で、路
面の突起を捨つて底突きを招くことにもなる。 Hydraulic shock absorbers for off-road vehicles have a large stroke and have large undulations on the road surface, so the damping force during normal driving is also set to be relatively large. However, this damping force also provides resistance to the extension operation from the vicinity of the maximum compression, so during the extension operation, the bumps on the road surface are discarded, resulting in bottoming out.

さらに積載車等では空荷と積荷の場合における
減衰力の調整が必要となる。 Furthermore, in the case of a loaded vehicle, it is necessary to adjust the damping force between empty and loaded vehicles.

これらの対策手段として、本出願人により第１
図ならびに第２図に示すような減衰力の位置依存
特性をもつ油圧緩衝器が既に提案されている。 As a countermeasure against these problems, the applicant has proposed the first
A hydraulic shock absorber having position-dependent damping force characteristics as shown in FIG. 2 and FIG. 2 has already been proposed.

１は油圧シリンダ、２はピストンロツドであ
り、油圧シリンダ１は摺動自由なピストン３によ
つて上部室Ａと下部室Ｂとに画成される。４はピ
ストンロツド２を伸側に付勢するスプリングであ
る。 1 is a hydraulic cylinder, 2 is a piston rod, and the hydraulic cylinder 1 is defined into an upper chamber A and a lower chamber B by a freely sliding piston 3. 4 is a spring that biases the piston rod 2 toward the expansion side.

この油圧シリンダ１の下部室Ｂは下端部に開け
た通口５と連絡用油送管６を通して第２図に示す
タンク７に連続される。 The lower chamber B of the hydraulic cylinder 1 is connected to a tank 7 shown in FIG. 2 through a port 5 opened at the lower end and a communication oil pipe 6.

タンク７はその内部がフリーピストン８によつ
て気体室９と油溜室１０とに画成され、下部室Ｂ
の作動油は圧縮作動時に後述のリリーフバルブ２
４を経て油溜室１０に導入される。 The inside of the tank 7 is divided into a gas chamber 9 and an oil reservoir chamber 10 by a free piston 8, and a lower chamber B.
During compression operation, the hydraulic oil is released into relief valve 2 (described later)
4 and is introduced into the oil reservoir chamber 10.

リリーブバルブ２４はタンク７に取付けたボデ
イ１２の軸孔１１に摺動自由にスプール１３を挿
入し、このスプール１３の一端は油溜室１０、他
端は大気室２０にそれぞれ臨ませる。大気室２０
にはリリーフスプリング２８が介装され、スプー
ル１３を油溜室１０の方向に付勢している。この
スプール１３は外径が途中で２段に変化し、その
小径部１４はボデイ１２に固定されたバルブケー
ス１５を貫通して油溜室１０に突出させるととも
に、段部１８を油室１９に位置させる一方、大径
部１６が前記軸孔１１を摺動自由に貫通して大気
室２０に突出している。 In the relief valve 24, the spool 13 is slidably inserted into the shaft hole 11 of the body 12 attached to the tank 7, and one end of the spool 13 faces the oil reservoir chamber 10 and the other end faces the atmospheric chamber 20. Atmospheric chamber 20
A relief spring 28 is interposed therein to urge the spool 13 toward the oil reservoir chamber 10. The outer diameter of this spool 13 changes into two stages in the middle, and the small diameter part 14 penetrates the valve case 15 fixed to the body 12 and projects into the oil reservoir chamber 10, and the stepped part 18 is inserted into the oil chamber 19. On the other hand, the large diameter portion 16 freely slides through the shaft hole 11 and projects into the atmospheric chamber 20.

油溜室１０と油室１９とはスプール１３に設け
たオリフイス２１を介して常時連通する。そして
油溜室１０に位置する小径部１４の先端には、ス
ナツプリング２５で外れないようにバルブ板２６
が嵌められ、このバルブ板２６がバルブケース１
５の端面に接した位置でスプール１３はそれ以上
大気室２０側への移動を阻止される。 The oil reservoir chamber 10 and the oil chamber 19 are always in communication via an orifice 21 provided in the spool 13. A valve plate 26 is attached to the tip of the small diameter portion 14 located in the oil reservoir chamber 10 to prevent it from coming off with a snap spring 25.
is fitted, and this valve plate 26 is attached to the valve case 1.
The spool 13 is prevented from moving any further toward the atmospheric chamber 20 at the position where it touches the end surface of the spool 5 .

バルブケース１５には伸側作動時に開くチエツ
ク弁２７が収められ、この実施例では圧側作動時
にバルブケース１５のフランジ部２９で保持され
るチエツク弁２７の弁板３０が、前記リリーフバ
ルブ２４のバルブ板２６に対する弁座を形成して
いる。なお３２は連絡用油送管６が接続される開
口で、油室１９と連通する。 The valve case 15 houses a check valve 27 that opens when operating on the compression side. In this embodiment, the valve plate 30 of the check valve 27, which is held by the flange 29 of the valve case 15 when operating on the compression side, is connected to the valve of the relief valve 24. It forms a valve seat for plate 26. Note that 32 is an opening to which the communication oil feed pipe 6 is connected, and communicates with the oil chamber 19 .

したがつて、リリーフバルブ２４のスプール１
３は一端を大気に臨ませてあるため、定常状態で
はスプール１３は下記式で示すように釣合つてい
る。 Therefore, spool 1 of relief valve 24
3 has one end facing the atmosphere, so in a steady state, the spool 13 is balanced as shown by the following equation.

P2B＝（Ｂ−Ａ）P1＋Ｆ ただし、 P1：油室１９の圧力 P2：油溜室１０の圧力 Ａ：スプールの大径部１６の直径 Ｂ：バルブ板２６の直径 Ｆ：スプリングのセツト荷重 そして、ピストンロツド２の最伸長時にこのバ
ランス位置がスプール１３の右方への移動限（第
２図の状態）に達しているように、予めバルブス
プリング２８の弾性力、バルブ板２６や大径部１
３の有効受圧面積が設定してある。 P 2 B=(B-A) P 1 +F However, P 1 : Pressure in oil chamber 19 P 2 : Pressure in oil reservoir chamber 10 A : Diameter of large diameter part 16 of spool B : Diameter of valve plate 26 F : Setting Load of the Spring Then, the elastic force of the valve spring 28 and the elastic force of the valve plate 26 are set in advance so that this balance position reaches the rightward movement limit of the spool 13 (the state shown in Fig. 2) when the piston rod 2 is fully extended. and large diameter part 1
An effective pressure receiving area of 3 is set.

このバランス状態からピストンロツド２が圧縮
作動すると、ピストンロツド２の侵入分の作動油
が連絡用油送管６を通して下部室Ｂから油室１９
に流入する。油室１９に流入した作動油の一部は
オリフイス２１を通して油溜室１０に流入する
が、油溜室１０は油室１９に比べてオリフイス２
１の絞りによつて圧力の上昇がゆるやかであり、
したがつて両室の圧力P1とP2との間に差圧が生
じる。この差圧によつて前記の釣合い状態が崩れ
てスプール１３が油溜室１０の方向に移動して、
リリーフバルブ２４は開弁する。このリリーフバ
ルブ２４が油室１９から油溜室１０へ流れようと
する作動油に抵抗を与えて適度な減衰力を生じる
のである。 When the piston rod 2 is compressed from this balanced state, the hydraulic oil entering the piston rod 2 flows from the lower chamber B to the oil chamber 19 through the communication oil pipe 6.
flows into. A part of the hydraulic oil that has flowed into the oil chamber 19 flows into the oil reservoir chamber 10 through the orifice 21.
Due to the restriction of 1, the pressure rises slowly,
Therefore, a pressure difference occurs between the pressures P 1 and P 2 in both chambers. Due to this differential pressure, the above-mentioned balanced state is disrupted, and the spool 13 moves toward the oil reservoir chamber 10.
The relief valve 24 is opened. This relief valve 24 provides resistance to the hydraulic oil flowing from the oil chamber 19 to the oil reservoir chamber 10, thereby producing an appropriate damping force.

ところで油溜室１０の圧力P2はその油量、つ
まり、ピストンロツド２のストローク位置によつ
て変化する。したがつてリリーフバルブ２４は、
ピストンロツド２のストローク位置に比例して変
化する油溜室１０の圧力P2を受けてその設定圧
力が変化する。つまり、ピストンロツド２がある
ストローク位置にあるときの油溜室１０の圧力
P2と、スプリング２８との差圧力がスプール１
３に作用し、圧力P2が高くなるほどスプール１
３を大気室２０側へと強く押し、開弁圧力（クラ
ツキング圧力）が高まるのである。その結果、第
３図で示すような位置依存型の減衰力特性が得ら
れる。 By the way, the pressure P2 in the oil reservoir chamber 10 changes depending on the amount of oil, that is, the stroke position of the piston rod 2. Therefore, the relief valve 24 is
The set pressure changes in response to the pressure P2 in the oil reservoir chamber 10, which changes in proportion to the stroke position of the piston rod 2 . In other words, the pressure in the oil reservoir chamber 10 when the piston rod 2 is at a certain stroke position
The differential pressure between P 2 and spring 28 is spool 1
3, and the higher the pressure P 2 , the more the spool 1
3 is strongly pushed toward the atmospheric chamber 20 side, and the valve opening pressure (cracking pressure) increases. As a result, a position-dependent damping force characteristic as shown in FIG. 3 is obtained.

すなわち第３図は縦軸を減衰力Ａとし、横軸を
ピストン速度Ｂとした特性図であり、オリフイス
２１による絞り抵抗曲線Ｃがピストンストローク
位置に応じて変化するリリーフバルブ２４の設定
圧力に達した時点でそれぞれリリーフバルブ２４
が開き、直線的な特性D1，D2……Dxによる減衰
力が得られる。 That is, FIG. 3 is a characteristic diagram in which the vertical axis is the damping force A and the horizontal axis is the piston speed B, and the throttle resistance curve C by the orifice 21 reaches the set pressure of the relief valve 24, which changes depending on the piston stroke position. At that point, the relief valve 24
opens, and a damping force due to linear characteristics D 1 , D 2 . . . Dx is obtained.

ところで、このような油圧緩衝器では、油圧シ
リンダ１の伸縮作動の反復により発生する摩擦熱
でしだいに作動油の温度が上昇してしまう。この
ため、作動油の膨張とともに気体室９のガス圧の
上昇によつて、リリーフバルブ２４を閉じ方向に
押圧する油溜室１０の圧力P2が増大しその結果
リリーフ設定圧力が高まり、設定減衰力が変化す
るという問題がある。 By the way, in such a hydraulic shock absorber, the temperature of the hydraulic oil gradually rises due to frictional heat generated by repeated expansion and contraction operations of the hydraulic cylinder 1. Therefore, as the hydraulic oil expands and the gas pressure in the gas chamber 9 increases, the pressure P 2 in the oil reservoir chamber 10 that presses the relief valve 24 in the closing direction increases, resulting in an increase in the relief setting pressure and the setting damping. The problem is that power changes.

そこで、本発明は、作動油の温度に応じて押圧
力が高まる補償手段によりリリーフバルブを開き
方向に押圧し、油溜室の作動油温の上昇にともな
うリリーフ設定圧力の高まり分をキヤンセルする
ようにした油圧緩衝器を提供することを目的とす
る。 Therefore, the present invention is designed to press the relief valve in the opening direction using a compensating means that increases the pressing force in accordance with the temperature of the hydraulic oil, thereby canceling the increase in the relief setting pressure caused by the rise in the temperature of the hydraulic oil in the oil reservoir chamber. The purpose of the present invention is to provide a hydraulic shock absorber.

以下、本発明の実施例を図面にしたがつて説明
する。なお、第１図、第２図と同一部位は同一符
号を使用する。 Embodiments of the present invention will be described below with reference to the drawings. Note that the same parts as in FIGS. 1 and 2 are designated by the same reference numerals.

１２がタンク７に取付けたボデイ、１１がバル
ブケース１５に摺動自由に支持されたスプールで
あり、２４が油室１６から油溜室１０へと流れる
作動油に所定の減衰力を附与するリリーフバル
ブ、２６がそのバルブ板、２７が閉じ位置のバル
ブ板２６に接するチエツク弁である。なおスプー
ル１１とバルブケース１５の摺接部における間隙
を介して油室１９と油溜室１０とが連通される。 12 is a body attached to the tank 7, 11 is a spool slidably supported by the valve case 15, and 24 applies a predetermined damping force to the hydraulic oil flowing from the oil chamber 16 to the oil reservoir chamber 10. The relief valve 26 is its valve plate, and 27 is a check valve in contact with the valve plate 26 in the closed position. Note that the oil chamber 19 and the oil reservoir chamber 10 are communicated with each other through a gap at the sliding contact portion of the spool 11 and the valve case 15.

円筒状のボデイ１２にはスプール１１と同軸上
にシリンダ４０が挿入され、このシリンダ４０の
内部に密閉状のガス室４１が形成される。シリン
ダ４０の外周とボデイ１２の内周との間には油室
１９と開口３２とを連通する環状通路４２が形成
される。そして、シリンダ４０の一端からは前記
スプール１１の大径部１３が気密的に摺動自由に
挿入される。 A cylinder 40 is inserted into the cylindrical body 12 coaxially with the spool 11, and a sealed gas chamber 41 is formed inside the cylinder 40. An annular passage 42 is formed between the outer periphery of the cylinder 40 and the inner periphery of the body 12, which communicates the oil chamber 19 with the opening 32. The large diameter portion 13 of the spool 11 is slidably inserted into the cylinder 40 from one end in an airtight manner.

ガス室４１は封入したガス（例えば大気）が通
路４２の作動油から熱を受けて圧力が上昇する
と、スプール１１を開弁方向へと押圧する力を増
す。また、ガス室４１にはスプール１１を同じく
油溜室１０側へと付勢するリリーフスプリング２
８が介装される。 When the gas sealed in the gas chamber 41 (for example, the atmosphere) receives heat from the hydraulic oil in the passage 42 and its pressure increases, the force that presses the spool 11 in the valve opening direction increases. Also, in the gas chamber 41, a relief spring 2 is provided which also urges the spool 11 toward the oil reservoir chamber 10.
8 is interposed.

通路４２に面するシリンダ４０の外周には、伝
熱面積を大きくとるのと、ボデイ１２に螺着した
セツトスクリユ４４とによりシリンダ４０の位置
決めするため、リードの大きなネジ部４３が形成
される。 A threaded portion 43 with a large lead is formed on the outer periphery of the cylinder 40 facing the passage 42 in order to provide a large heat transfer area and to position the cylinder 40 by means of a set screw 44 screwed onto the body 12.

つまり、ボデイ１２に対しシリンダ４０を移動
させることにより、スプール１１の侵入度合（ガ
ス室４１の容積）及びスプリング２８の初期荷重
を変化させ、圧力補償特性の調整を行えるように
なつている。なお、ガス室４１の容積調整を行う
ときにシリンダ４０の内部圧力を調整するため
に、シリンダ４０の突出端には気密栓４６を設け
る。４８はボデイ１２の外周に形成した冷却フイ
ンである。 That is, by moving the cylinder 40 with respect to the body 12, the degree of penetration of the spool 11 (volume of the gas chamber 41) and the initial load of the spring 28 can be changed, and the pressure compensation characteristics can be adjusted. Note that in order to adjust the internal pressure of the cylinder 40 when adjusting the volume of the gas chamber 41, an airtight plug 46 is provided at the protruding end of the cylinder 40. 48 is a cooling fin formed on the outer periphery of the body 12.

このように構成したため、圧側作動時に油圧シ
リンダ１からタンク７へ逃げる作動油に減衰力を
附与するリリーフバルブ２４は、既に述べたよう
に、ピストンロツド２のストローク位置に比例し
て変化する油溜室１０の圧力P2、つまり、作動
油圧を受けてその設定圧力が変化し、作動油圧が
高くなるほどスプール１１がガス室４１側へ強く
押されて、クラツキング圧力が高められ、その結
果位置依存型の減衰力特性が得られる。 With this structure, the relief valve 24, which applies a damping force to the hydraulic oil escaping from the hydraulic cylinder 1 to the tank 7 during pressure side operation, is configured to act as an oil reservoir that changes in proportion to the stroke position of the piston rod 2, as already mentioned. The pressure P 2 in the chamber 10, that is, the set pressure changes in response to the working oil pressure, and the higher the working oil pressure is, the more the spool 11 is pushed toward the gas chamber 41 side, increasing the cracking pressure, and as a result, the position-dependent type damping force characteristics are obtained.

ところで、作動油は油圧シリンダの反復作動で
発する摩擦熱などによる温度上昇にともなつて膨
張するとともにその熱で気体室９の圧力も高まる
ために油圧が上昇し、その分スプール１１をガス
室４１側へ強く押すようになる。 By the way, the hydraulic oil expands as the temperature rises due to frictional heat generated by repeated operation of the hydraulic cylinder, and the pressure in the gas chamber 9 also increases due to the heat. Begins to push hard to the side.

しかし、これと同時にガス室４１の封入気体が
通路４２を通る作動油の熱を受けて膨張し、その
上昇圧力でスプール１１を油溜室１０側へと押し
戻す。この結果スプール１１の両端に作用する温
度上昇により互に高まつた圧力がキヤンセルさ
れ、したがつて、リリーフバルブ２４の設定圧力
は作動油の温度上昇に影響されず、常に適正に保
たれる。 However, at the same time, the gas sealed in the gas chamber 41 expands due to the heat of the hydraulic oil passing through the passage 42, and the increased pressure pushes the spool 11 back toward the oil reservoir chamber 10. As a result, the pressures that have increased due to the temperature rise acting on both ends of the spool 11 are canceled, and therefore the set pressure of the relief valve 24 is not affected by the temperature rise of the hydraulic oil and is always maintained at an appropriate level.

また、本実施例では、シリンダ４０がボデイ１
２に対し、移動可能に形成されているためセツト
スクリユ４４を緩めてシリンダ４０を移動するこ
とにより、ガス室４１の体積が変えられ、圧力を
調整することができるとともに、リリーフスプリ
ング２８の初期荷重を加減することもできる。 Further, in this embodiment, the cylinder 40 is connected to the body 1.
In contrast to No. 2, it is movable, so by loosening the set screw 44 and moving the cylinder 40, the volume of the gas chamber 41 can be changed, the pressure can be adjusted, and the initial load of the relief spring 28 can be reduced. You can also adjust it.

第５図は、他の実施例を示すもので、スプール
１１を油溜室１０側へ付勢するリリーフスプリン
グ２８が取り除かれており、その代り、ガス室４
１の封入圧力としてリリーフスプリング２８の初
期荷重に相当する圧力が予め附与されている。ま
た、気体室９は通孔４５を介して大気に開放さ
れ、スプリング４７の付勢力によりフリーピスト
ン８が押されるようになつており、この場合、気
体室９の圧力変化のない分だけ温度上昇による作
動油圧の高まりを低く抑えることができる。 FIG. 5 shows another embodiment in which the relief spring 28 that biases the spool 11 toward the oil reservoir chamber 10 is removed, and instead, the relief spring 28 is replaced by a gas chamber 4.
A pressure corresponding to the initial load of the relief spring 28 is applied in advance as the sealing pressure of 1. Further, the gas chamber 9 is opened to the atmosphere through the through hole 45, and the free piston 8 is pushed by the biasing force of the spring 47. In this case, the temperature increases by the amount that the pressure in the gas chamber 9 does not change. It is possible to suppress the increase in hydraulic pressure due to

なお前記のガス室４１を組込んだリリーフバル
ブ２４は必ずしもタンク７に設けなければならな
いものではなく、これをタンク７に比べて油量が
多く、作動油温も高い油圧シリンダ１の通口５に
設けてもよい。 Note that the relief valve 24 incorporating the gas chamber 41 does not necessarily have to be provided in the tank 7, and may be installed in the port 5 of the hydraulic cylinder 1, which has a larger oil volume and a higher working oil temperature than the tank 7. may be provided.

また、密閉シリンダ４０にはガスを封入するか
わりに熱膨張率の比較的大きな液体を注入しても
よい。 Further, instead of filling the sealed cylinder 40 with gas, a liquid having a relatively large coefficient of thermal expansion may be injected into the sealed cylinder 40.

以上説明したように、本発明は、作動油の温度
上昇により高まるリリーフ設定圧力の増加分を、
作動油熱を受けて圧力が上昇する補償手段の押圧
力によつてキヤンセルするようにしたので、作動
油の温度上昇に影響されてリリーフ設定値が変化
することがなく、常に適正な減衰力を保つて良好
な緩衝作用を行なうことができる。 As explained above, the present invention reduces the increase in the relief setting pressure that increases due to the rise in the temperature of the hydraulic oil.
Since the pressure is canceled by the pressure of the compensating means, which increases due to the heat of the hydraulic oil, the relief setting value will not change due to the temperature rise of the hydraulic oil, and the damping force will always be at the appropriate level. can be maintained to provide a good buffering effect.

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

第１図は、先行技術を示す油圧シリンダの一部
切欠断面図、第２図は同タンクの要部切欠断面
図、第３図は、減衰力特性図であり、第４図は本
発明タンクの要部切欠断面図、第５図は他の実施
例を示すタンクの縦断面図である。 １……油圧シリンダ、７……タンク、８……フ
リーピストン、９……気体室、１０……油溜室、
１１……スプール、１２……ボデイ、１５……バ
ルブケース、１９……油室、２４……リリーフバ
ルブ、４０……シリンダ、２８……リリーフスプ
リング、４１……ガス室。 Fig. 1 is a partially cutaway sectional view of a hydraulic cylinder showing the prior art, Fig. 2 is a cutaway sectional view of the main part of the same tank, Fig. 3 is a damping force characteristic diagram, and Fig. 4 is a tank of the present invention. FIG. 5 is a longitudinal sectional view of a tank showing another embodiment. 1... Hydraulic cylinder, 7... Tank, 8... Free piston, 9... Gas chamber, 10... Oil reservoir chamber,
11... Spool, 12... Body, 15... Valve case, 19... Oil chamber, 24... Relief valve, 40... Cylinder, 28... Relief spring, 41... Gas chamber.

Claims (1)

【特許請求の範囲】 １ 圧側作動時に油室から油溜室へとピストンロ
ツドの侵入体積分の作動油を逃がす通路にリリー
フバルブを設け、このリリーフバルブは弁板を有
するスプールの一端を油溜室に、他端を所定圧力
ガスを封入した温度補償ガス室にそれぞれ臨ま
せ、かつ、このガス室を作動油の通路に面して配
設したことを特徴とする油圧緩衝器。 ２ 温度補償ガス室が、スプールに対して摺動可
能なシリンダの内部に形成されていることを特徴
とする特許請求の範囲第１項記載の油圧緩衝器。 ３ ガス室にはスプールを押圧するリリーフスプ
リングが介装されていることを特徴とする特許請
求の範囲第２項記載の油圧緩衝器。[Scope of Claims] 1. A relief valve is provided in a passage that releases hydraulic oil corresponding to the volume entered by the piston rod from the oil chamber to the oil reservoir chamber during pressure side operation, and this relief valve connects one end of the spool having a valve plate to the oil reservoir chamber. A hydraulic shock absorber characterized in that the other end thereof faces a temperature compensating gas chamber filled with gas at a predetermined pressure, and the gas chamber is disposed facing a hydraulic oil passage. 2. The hydraulic shock absorber according to claim 1, wherein the temperature compensation gas chamber is formed inside a cylinder that is slidable with respect to the spool. 3. The hydraulic shock absorber according to claim 2, wherein the gas chamber is provided with a relief spring that presses the spool.
JP177581A 1981-01-09 1981-01-09 Hydraulic shock absorber Granted JPS57116946A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP177581A JPS57116946A (en) 1981-01-09 1981-01-09 Hydraulic shock absorber

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP177581A JPS57116946A (en) 1981-01-09 1981-01-09 Hydraulic shock absorber

Publications (2)

Publication Number Publication Date
JPS57116946A JPS57116946A (en) 1982-07-21
JPS6331015B2 true JPS6331015B2 (en) 1988-06-22

Family

ID=11510942

Family Applications (1)

Application Number Title Priority Date Filing Date
JP177581A Granted JPS57116946A (en) 1981-01-09 1981-01-09 Hydraulic shock absorber

Country Status (1)

Country Link
JP (1) JPS57116946A (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5930946U (en) * 1982-08-23 1984-02-25 カヤバ工業株式会社 Vehicle hydraulic shock absorber
JPS62179444U (en) * 1986-05-02 1987-11-14
JPH0433477Y2 (en) * 1986-05-02 1992-08-11
JP5639870B2 (en) * 2010-12-10 2014-12-10 カヤバ工業株式会社 Hydraulic shock absorber for vehicles
JP6047035B2 (en) * 2012-03-27 2016-12-21 Ｋｙｂ株式会社 Hydraulic shock absorber for vehicles

Also Published As

Publication number Publication date
JPS57116946A (en) 1982-07-21

Similar Documents

Publication Publication Date Title
US11041537B2 (en) Vehicle suspension damper
JPS6132197B2 (en)
US6332622B1 (en) Suspension apparatus having two interconnected shock absorbers
EP0807767B1 (en) Hydraulic shock absorber
US20030094341A1 (en) Shock absorber with a gas chamber on the rebound side of a piston
JPS6331015B2 (en)
EP2148112B1 (en) Vehicle suspension damper
JPH023052B2 (en)
JPS6230603Y2 (en)
JP3357993B2 (en) Damping force generator for vehicle hydraulic shock absorbers
JPH0810705Y2 (en) Front fork valve device
JPH07197975A (en) Damping force generator for vehicle hydraulic shock absorber
JPS6357273B2 (en)
JPS5926817B2 (en) Vehicle shock absorber
JPS6313051B2 (en)
JPS6119224Y2 (en)
US3095214A (en) Fluid power apparatus
JPS6243160Y2 (en)
JPS6367056B2 (en)
GB2161892A (en) A hydropneumatic vehicle suspension system with height control
JPS6141458Y2 (en)
JPS6224851Y2 (en)
JPS61211547A (en) Assembling method for hydraulic shock-absorber
JPH0517469Y2 (en)
JPH08184342A (en) Hydraulic shock absorber