JPS6246917Y2 - - Google Patents
Info
- Publication number
- JPS6246917Y2 JPS6246917Y2 JP1981175873U JP17587381U JPS6246917Y2 JP S6246917 Y2 JPS6246917 Y2 JP S6246917Y2 JP 1981175873 U JP1981175873 U JP 1981175873U JP 17587381 U JP17587381 U JP 17587381U JP S6246917 Y2 JPS6246917 Y2 JP S6246917Y2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- pressure
- cylinder
- piston
- chamber
- 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
- 238000013016 damping Methods 0.000 claims description 32
- 238000007906 compression Methods 0.000 claims description 21
- 239000006096 absorbing agent Substances 0.000 claims description 20
- 230000035939 shock Effects 0.000 claims description 20
- 230000006835 compression Effects 0.000 claims description 19
- 239000010720 hydraulic oil Substances 0.000 claims description 9
- 230000001902 propagating effect Effects 0.000 claims 2
- 230000003111 delayed effect Effects 0.000 claims 1
- 230000007246 mechanism Effects 0.000 description 4
- 239000003921 oil Substances 0.000 description 4
- 238000004891 communication Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000003780 insertion Methods 0.000 description 1
- 230000037431 insertion Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Landscapes
- Fluid-Damping Devices (AREA)
Description
【考案の詳細な説明】
本考案はガス入り油圧緩衝器の改良に関するも
ので、低圧複筒式シヨツクアブソーバにおいて、
ベースバルブの形状を内周固定で外径寸法がバル
ブシートの内径寸法よりもバルブシート面幅相当
量大径となる寸法関係に限定して圧縮工程におけ
るリザーバ室のガス圧の上昇圧を有効に圧側リリ
ーフバルブの背圧として利用し減衰力特性を改良
したものである。[Detailed description of the invention] This invention relates to the improvement of a gas-filled hydraulic shock absorber.
The shape of the base valve is limited to a dimension relationship in which the inner circumference is fixed and the outer diameter is larger than the inner diameter of the valve seat by an amount equivalent to the valve seat surface width to effectively increase the gas pressure in the reservoir chamber during the compression process. This is used as back pressure for the pressure side relief valve to improve damping force characteristics.
従来一般に使用されている車輌用シヨツクアブ
ソーバは、第１図にその減衰力特性を示すよう
に、特に圧側減衰力の立上り特性が悪くて圧側作
動初期において圧側減衰力が低く、この影響によ
り第２図に示すように連続加振時においても圧側
減衰力の立上り特性が悪くなることが知られてい
る。従つて車輌特性の接地性、操縦安定性及び乗
心地が損なわれるものである。 As shown in Figure 1, the shock absorber for vehicles that has been commonly used in the past has particularly poor rise characteristics of the compression side damping force, and the compression side damping force is low at the beginning of the compression side operation. As shown in the figure, it is known that the rise characteristics of the compression damping force deteriorate even during continuous vibration. Therefore, the characteristics of the vehicle, such as ground contact, steering stability, and ride comfort, are impaired.
本考案はこの圧側減衰力の立上り遅れ（圧側初
期波形の乱れ）を改善することにより前記車輌特
性を改善することを目的とするものである。 The present invention aims to improve the vehicle characteristics by improving the rise delay of the compression damping force (disturbance of the initial compression waveform).
以下、本考案ガス入り油圧緩衝器の一実施例を
図面に従つて説明するに第３図はシヨツクアブソ
ーバの正断面図である。 Hereinafter, one embodiment of the gas-filled hydraulic shock absorber of the present invention will be described with reference to the drawings. FIG. 3 is a front sectional view of the shock absorber.
アウタチユーブ１に内挿したシリンダ２は上端
をアウタチユーブ１の上端に内挿固着したベアリ
ング３の下端に固設し、一方下端をアウタチユー
ブ１の下端に設けたベースバルブ機構４のバルブ
基板５に固設すると共に、アウタチユーブ１との
間に円筒状室Ａを構成する。 The cylinder 2 inserted into the outer tube 1 has its upper end fixed to the lower end of the bearing 3 inserted and fixed to the upper end of the outer tube 1, and its lower end fixed to the valve board 5 of the base valve mechanism 4 provided at the lower end of the outer tube 1. At the same time, a cylindrical chamber A is formed between the outer tube 1 and the outer tube 1.
上記ベアリング３の軸芯に穿設された軸孔３ａ
には前記シリンダ２に対し気密的且つ摺動自在に
内挿されたピストン７に突設したピストンロツド
８を摺動自在に貫挿するもので、両者間は80μの
小間〓ｄを形成すると共に、リツプ端をピストン
ロツド８に摺接したシール部材９により軸封し、
且つ内側のベアリング３内段部に嵌着したチエツ
クシール１０を介して流体をｘ方向にのみ流通す
るように封緘してピストン７の上部室Ｂと下部室
Ｃを構成する。 Shaft hole 3a drilled in the shaft center of the bearing 3
A piston rod 8 protruding from a piston 7 is slidably inserted into the cylinder 2 airtightly and slidably, and a space d of 80μ is formed between the two. The lip end is shaft-sealed with a sealing member 9 that is in sliding contact with the piston rod 8,
An upper chamber B and a lower chamber C of the piston 7 are formed by sealing the piston 7 through a check seal 10 fitted to the inner stage of the inner bearing 3 so that fluid can flow only in the x direction.
また１１は前記シール部材９とチエツクシール
１０間の環状室Ｄと円筒状室Ａを連通する如くベ
アリング３に穿設した連通孔であり、チエツクシ
ール１０及び小間隙ｄを介して円筒状室Ａと上側
空間Ｂの上端を連通するように成る。 Reference numeral 11 denotes a communication hole bored in the bearing 3 so as to communicate the annular chamber D and the cylindrical chamber A between the seal member 9 and the check seal 10, and the cylindrical chamber A through the check seal 10 and the small gap d. and the upper end of the upper space B are communicated with each other.
前記ベースバルブ機構４はアウタチユーブ１の
端盤６に固着したバルブ基板５の中央に貫挿固着
した固定ピン１２に対して、バルブ基板５の下面
に内周固定した外周撓みの圧縮側減衰力発生用リ
ーフバルブ１３と、上面に伸長側吸込チエツク弁
１４を枢着したものであり、リーフバルブ１３は
バルブ基板５の内周に穿設した通孔の弁座５ａに
離接すると共に、ストツプリング１５により弁座
５ａに近接保持される。 The base valve mechanism 4 is fixed to the lower surface of the valve board 5 on the inner periphery and generates a compression-side damping force on the compression side when the outer periphery is bent with respect to a fixing pin 12 that is inserted and fixed in the center of the valve board 5 that is fixed to the end plate 6 of the outer tube 1. The leaf valve 13 is pivoted to the upper surface of the extension side suction check valve 14. It is held close to the valve seat 5a.
またチエツク弁１４はバルブ基板５の外周に穿
設した通孔の弁座５ｂに圧接する如くスプリング
１６により弾性付勢せしめられるもので上記バル
ブ基板５の底部にはオリフイス１７を穿設して成
る。また前記ピストン７には圧縮側の吸込チエツ
ク弁１８と伸張側減衰力発生弁機構１９からなる
ピストンバルブ２０が構成され、それぞれ、絞り
構造を持つようになる。 The check valve 14 is elastically biased by a spring 16 so as to come into pressure contact with a valve seat 5b of a through hole formed on the outer periphery of the valve base plate 5, and an orifice 17 is formed at the bottom of the valve base plate 5. . Further, the piston 7 is provided with a piston valve 20 consisting of a suction check valve 18 on the compression side and a damping force generating valve mechanism 19 on the expansion side, each of which has a throttle structure.
上記構成の複筒式ガス入り油圧緩衝器は、圧縮
工程においてシリンダ下部室ｃの作動油がピスト
ンバルブ２０によつて若干絞られて上部室Ｂに、
また同時にベースバルブ４によつて絞られて円筒
状室Ａに分流して流入する。 In the double-tube gas-filled hydraulic shock absorber having the above configuration, during the compression process, the hydraulic oil in the cylinder lower chamber C is slightly throttled by the piston valve 20 and flows into the upper chamber B.
At the same time, the water is throttled by the base valve 4 and flows into the cylindrical chamber A in a branched manner.
このときピストンロツド８の挿入体積分だけ円
筒状室Ａ内の油面が上昇して上方のリザーバ室Ｅ
の体積が減少しその内圧が増大するようになる。 At this time, the oil level in the cylindrical chamber A rises by the insertion volume of the piston rod 8, and the oil level in the upper reservoir chamber E rises.
Its volume decreases and its internal pressure increases.
伸張工程においては上部室Ｂの作動油がピスト
ンバルブ２０によつて絞られて下部室Ｃに流入す
ると共に、ピストンロツド８がシリンダ２から抜
け出た体積分の作動油がチエツク弁１４を介して
円筒状室Ａから下部室Ｃに流入する。 In the extension process, the hydraulic oil in the upper chamber B is throttled by the piston valve 20 and flows into the lower chamber C, and at the same time, the hydraulic oil in the volume that the piston rod 8 escapes from the cylinder 2 passes through the check valve 14 into the cylindrical shape. It flows from chamber A into lower chamber C.
しかし、円筒状室Ａの上部に低圧ガスを封入し
リザーバ室Ｅを構成すると共に、ベアリング３部
にチエツクシール１０を設置している為、この伸
張工程においては円筒状室Ａの作動油が下部室Ｃ
に流入する際の遅れがなく、シリンダ２内は常時
作動油で充満されており、同時にリザーバ室Ｅが
低圧ガスにより圧力付勢されリーフバルブ１５の
背面に作用している為、圧側減衰力の立上り遅れ
がなくなる。 However, since the upper part of the cylindrical chamber A is filled with low-pressure gas to form the reservoir chamber E, and the check seal 10 is installed at the 3rd part of the bearing, during this extension process, the hydraulic oil in the cylindrical chamber A is transferred to the lower part. Room C
There is no delay when the oil flows into the cylinder 2, and the inside of the cylinder 2 is always filled with hydraulic oil.At the same time, the reservoir chamber E is pressure-energized by low-pressure gas and acts on the back of the leaf valve 15, so that the damping force on the pressure side is reduced. There is no start-up delay.
また圧縮行程におけるリザーバ室Ｅへの油面上
昇による圧縮作用に伴ない内圧が上昇し、この圧
力上昇分が更にベースバルブ４のリーフバルブ１
３への背圧作用となつて圧側の減衰力を増大させ
るようになる。 In addition, the internal pressure increases due to the compression action due to the rise in the oil level in the reservoir chamber E during the compression stroke, and this pressure increase is further applied to the leaf valve 1 of the base valve 4.
3 and increases the damping force on the compression side.
即ち、リーフバルブ１３の背圧が高くなると、
下部室Ｃ側圧力の作用するバルブシート内径受圧
面積よりも大きな受圧面関係によつて第４図乃至
第６図に示すように背圧P0を増すとリーフバルブ
の撓みが次第に小さく同一作動圧力に対して撓み
難くなり、背圧P0を変化させた場合のリーブバル
ブの撓み（mm）と作動圧力Ｐとの関係は第６図の
グラフの如くになる。 That is, when the back pressure of the leaf valve 13 increases,
Due to the pressure-receiving surface area being larger than the pressure-receiving area of the inner diameter of the valve seat where the lower chamber C side pressure acts, as shown in Figs. The relationship between the deflection (mm) of the reve valve and the operating pressure P when the back pressure P 0 is changed is as shown in the graph of FIG.
ここで、圧側ベース部のリリーフバルブ１３で
発生する減衰力Ｆを求めてみると、一般に、
Ｆ＝A1×ΔＰ ………(1) で表わされる。 Here, when the damping force F generated in the relief valve 13 of the pressure side base portion is determined, it is generally expressed as F=A 1 ×ΔP (1).
但し、A1：ピストンロツド８の断面積
ΔＰ＝Ｐ−P0
Ｐ：リーフバルブ上面（下部室Ｃ内）の圧力
P0：リーフバルブ下面（リザーバ室Ｅ内）の
圧力とする。 However, A 1 : Cross-sectional area of the piston rod 8 ΔP=P-P 0 P : Pressure on the top surface of the leaf valve (inside the lower chamber C) P 0 : Pressure in the bottom surface of the leaf valve (inside the reservoir chamber E).
即ち、ピストンロツドに加わる荷重P0を求める
と、ピストン上部の受圧面積A2、同上部室Ｂの
圧力をP1、ピストン下部の受圧面積をA0とする
と、内圧とピストン受圧面積との関係より、
F0＝A0P−A2P1 ………(2)
又、力の均合いの関係より、減衰力F1と反発
力F2＝A1P0であるので、
F0＝F1＋F2 ………(3)
とも表現され、これ等(2)(3)式より減衰力は
F1＝F0−F2
＝（A0P−A2P1）−A1P0 ここで面積
A0＝A1＋A2故
＝（A0＋A2）Ｐ−A2P1−A1P0
＝A2（Ｐ−P1）＋A1（Ｐ−P0）となり、
第１項のA2（Ｐ−P1）がピストン部で発生する
減衰力であり、第２項がベース部で発生する減衰
力であり、前記(1)式のＦ＝A1（Ｐ−P0）＝A1ΔＰ
を得る。 That is, when calculating the load P 0 applied to the piston rod, if the pressure receiving area at the top of the piston is A 2 , the pressure in the upper chamber B is P 1 , and the pressure receiving area at the bottom of the piston is A 0 , then from the relationship between the internal pressure and the pressure receiving area of the piston, F 0 = A 0 P−A 2 P 1 ………(2) Also, from the relationship of force balance, the damping force F 1 and the repulsive force F 2 = A 1 P 0 , so F 0 = F 1 It is also expressed as +F 2 ......(3), and from equations (2) and (3), the damping force is F 1 = F 0 - F 2 = (A 0 P - A 2 P 1 ) - A 1 P 0 Here Therefore, the area A 0 = A 1 + A 2 = (A 0 + A 2 ) P - A 2 P 1 - A 1 P 0 = A 2 (P - P 1 ) + A 1 (P - P 0 ), and the first term is A 2 (P-P 1 ) is the damping force generated at the piston, the second term is the damping force generated at the base, and F=A 1 (P-P 0 ) in equation (1) above. =A 1 ΔP
get.
又ベース部を流れる作動油の流量は、
Vp：ピストン速度
Ｃ ：流量係数
δ ：作動油の密度
Ａ ：バルブシート５ａらリーフバルブ１３
が撓んで得られる開口部面積であり、
Ａ＝２πｒ×ｙで求められる。Also, the flow rate of hydraulic oil flowing through the base is Vp: Piston speed C: Flow coefficient δ: Hydraulic oil density A: From valve seat 5a to leaf valve 13
is the opening area obtained by bending, and is determined by A=2πr×y.
この時ｒ：上部室Ｂ圧力のかかるバルブシート５
ａの内径半径
ｙ：リーフバルブ１３の撓みで、第５図よ
り圧力と半径の関数として求められる。At this time r: Valve seat 5 under pressure in upper chamber B
Inner diameter radius of a y: Deflection of the leaf valve 13, determined as a function of pressure and radius from FIG.
ｙ＝ｆ（Ｐ，P0，ｒ，ａ） ………(5)
(4)式よりΔＰ＝δＱ２／２Ｃ２Ａ２＝δＱ２／２Ｃ２
（２πｒｙ）２
＝δＱ２／４πｒ２Ｃ２ｙ２ ………(6)
前記(1)式へ(5)(6)式を代入して得られる圧側減衰
力特性をグラフに示したのが第７図であり、本考
案の場合、圧側の減衰力Ｆは、リーフバルブ１３
の半径ａをバルブシート５ａの内径に対して変化
させることによつて変更することができる。 y=f(P, P 0 , r, a) ......(5) From equation (4), ΔP=δQ 2 /2C 2 A 2 = δQ 2 /2C 2
(2πry) 2 = δQ 2 /4πr 2 C 2 y 2 ......(6) The compression side damping force characteristics obtained by substituting equations (5) and (6) into equation (1) above are shown in a graph. FIG. 7 shows that in the case of the present invention, the damping force F on the pressure side is the leaf valve 13.
can be changed by changing the radius a of the valve seat 5a with respect to the inner diameter of the valve seat 5a.
即ち、リーフバルブ１３の半径ａを大きくする
と第７図中実線の上方に破線で描いたように背圧
P0の影響が減衰力の変化に大きく作用してくる。 That is, when the radius a of the leaf valve 13 is increased, the back pressure increases as shown by the broken line above the solid line in FIG.
The influence of P 0 has a large effect on the change in damping force.
従つて、本考案においてはこれに着目し、ピス
トンロツド８のストロークによる変動する背圧P0
が、その圧縮行程において増大することを利用し
て、圧側減衰力の増加変化を有効に生じさせるよ
うな背圧P0を受け易いリーフバルブ１３の形状構
造としたものである。 Therefore, in the present invention, we focused on this and calculated the back pressure P 0 which fluctuates due to the stroke of the piston rod 8.
The leaf valve 13 is shaped and structured so that it can easily receive back pressure P 0 that effectively causes an increase in the compression side damping force by taking advantage of the fact that the pressure increases in the compression stroke.
この結果、ピストンに対する内圧上昇に基因し
た反発力の増大をもたらすが、本考案の構造によ
れば第８図に示すようにピストンロツド８が圧縮
側へ移動すると、リザーバ室Ｅ内への作動油流入
によつてリザーバ室体積が圧縮され、その内圧が
更に上昇する為、これが背圧P0としてリーフバル
ブ１３の半径ａによる受圧面側に作用して減衰力
をも同時に増大させることになり、バネ反発力の
増大に伴なつて減衰力もともに増大するので、常
時最適な車輌のサスペンシヨン状態を維持するこ
とができるのである。 As a result, the repulsion force against the piston increases due to the increase in internal pressure. However, according to the structure of the present invention, when the piston rod 8 moves toward the compression side as shown in FIG. 8, the hydraulic oil flows into the reservoir chamber E. As a result, the volume of the reservoir chamber is compressed and its internal pressure further increases, which acts as back pressure P 0 on the pressure receiving surface side of the leaf valve 13 due to the radius a, simultaneously increasing the damping force. As the repulsion force increases, the damping force also increases, making it possible to maintain the optimal suspension state of the vehicle at all times.
次に本考案の構造について実験結果を説明す
る。 Next, experimental results regarding the structure of the present invention will be explained.
実験 １
「従来の標準シヨツクアブソーバと本考案のシ
ヨツクアブソーバの減衰力特性」（第９図参
照）
本考案のシヨツクアブソーバが従来のものに
対し、圧側減衰力の立上り特性が大巾に改善さ
れた。Experiment 1 "Damping force characteristics of the conventional standard shock absorber and the shock absorber of the present invention" (see Figure 9) The shock absorber of the present invention has greatly improved the rise characteristics of the compression side damping force compared to the conventional shock absorber. .
実験 ２
「ベアリング３部のチエツクシール１０を廃止
し、ピストンロツド８とベアリング３の間隙ｄ
を80μ以下にした場合の減衰力特性」（第１０
図参照）
第９図に示すものよりは立上り特性が劣るが
従来のものよりは改善されている。Experiment 2 ``The check seal 10 of the bearing 3 part was abolished, and the gap d between the piston rod 8 and the bearing 3 was removed.
"Damping force characteristics when 80μ or less" (Part 10)
(See figure) Although the rise characteristic is inferior to that shown in FIG. 9, it is improved over the conventional one.
以上説明したように本考案のガス入り油圧緩衝
器の構造によれば圧側減衰力の立上りの遅れが改
善される為、車輌特性を改善し、より乗心地の良
い車輌等を提供することができる等、本考案の実
用効果は極めて大きい。 As explained above, the structure of the gas-filled hydraulic shock absorber of the present invention improves the delay in the rise of the compression side damping force, thereby improving vehicle characteristics and providing a vehicle with a more comfortable ride. The practical effects of this invention are extremely large.
図面は本考案ガス入り油圧緩衝器の一実施例を
示すもので、第１図は従来の複筒式シヨツクアブ
ソーバの減衰力特性を示すグラフ、第２図は同連
続加振時の減衰力特性を示すグラフ、第３図は本
考案シヨツクアブソーバの正断面図、第４図はベ
ースバルブ部要部拡大断面図、第５図は第４図に
おける圧力分布を示す説明図、第６図は同部のリ
ーフバルブの撓み量と圧力の関係を示すグラフ、
第７図はリーフバルブにおける圧側減衰力と背圧
の関係を示すグラフ、第８図は減衰力と反発力の
相互関係を示すグラフ、第９図は従来品と本考案
シヨツクアブソーバの減衰力特性を示すグラフ、
第１０図は本考案の他の実施例の減衰力特性を示
すグラフである。
１……アウタチユーブ、２……シリンダ、３…
…ベアリング、４……ベースパルプ機構、５……
バルブ基板、７……ピストン、８……ピストンロ
ツド、９……シール部材、１０……チエツクシー
ル、１１……連通孔、１３……リーフバルブ、１
４，１８……チエツク弁、１７……オリフイス、
１９……伸側減衰力発生弁、２０……ピストンバ
ルブ。
The drawings show an embodiment of the gas-filled hydraulic shock absorber of the present invention. Figure 1 is a graph showing the damping force characteristics of a conventional dual-tube shock absorber, and Figure 2 is a graph showing the damping force characteristics during continuous vibration. FIG. 3 is a front sectional view of the shock absorber of the present invention, FIG. 4 is an enlarged sectional view of the main part of the base valve, FIG. 5 is an explanatory diagram showing the pressure distribution in FIG. 4, and FIG. 6 is the same. A graph showing the relationship between the amount of deflection and pressure of the leaf valve in
Figure 7 is a graph showing the relationship between compression side damping force and back pressure in a leaf valve, Figure 8 is a graph showing the correlation between damping force and repulsion force, and Figure 9 is the damping force characteristics of the conventional shock absorber and the invented shock absorber. A graph showing,
FIG. 10 is a graph showing the damping force characteristics of another embodiment of the present invention. 1... Outer tube, 2... Cylinder, 3...
...Bearing, 4...Base pulp mechanism, 5...
Valve board, 7... Piston, 8... Piston rod, 9... Seal member, 10... Check seal, 11... Communication hole, 13... Leaf valve, 1
4, 18...check valve, 17...orifice,
19... Rebound damping force generation valve, 20... Piston valve.
Claims (1)
筒式シヨツクアブソーバにおいて、上記シリン
ダに内挿したピストンロツド内端に固設したピ
ストンに対し伸側減衰弁と圧側吸込チエツク弁
とよりなるピストンバルブを設け、上記アウタ
ーチユーブとシリンダとの間に形成された円筒
状室とシリンダ内の下部室との間にバルブ基板
を設けて、その下部室側上面には伸側吸込チエ
ツク弁を、また下面には内周固定の圧側リーフ
バルブを設け、当該リーフバルブの外径をバル
ブシートの内径よりもバルブシート面幅相当量
大径に形成して背圧側受圧面積を増すと共に、
上記シリンダの上下部室及び円筒状室の下部に
作動油を充填し且つ円筒状室の上部リザーバ室
には低圧ガスを封入して当該リザーバ室の圧力
上昇を上記リーフバルブの背圧として作用せし
める様構成したことを特徴とするガス入り油圧
緩衝器。 (2) 上記リザーバ室とシリンダの上部空間をチエ
ツクシールを介して連通し、リザーバ室の圧力
がピストンの背圧に伝播することを阻止せしめ
てなることを特徴とする実用新案登録請求の範
囲第１項記載のガス入り油圧緩衝器。 (3) 上記リザーバ室とシリンダの上部空間を連通
するシリンダに設けたピストンロツド摺動用ベ
アリングと該ピストンロツド間に100μ以下の
小間隙を形成し、リザーバ室の圧力がピストン
の背圧に伝播することを遅延せしめてなること
を特徴とする実用新案登録請求の範囲第１項及
び第２項記載のガス入り油圧緩衝器。[Scope of Claim for Utility Model Registration] (1) In a dual-tube shock absorber in which a cylinder is inserted into the outer tube, a rebound damping valve and a compression side suction check are provided for the piston fixed to the inner end of the piston rod inserted in the cylinder. A piston valve consisting of a valve is provided, a valve board is provided between a cylindrical chamber formed between the outer tube and the cylinder and a lower chamber in the cylinder, and an expansion side suction is provided on the upper surface of the lower chamber side. A check valve is provided, and a pressure side leaf valve with a fixed inner circumference is provided on the bottom surface, and the outer diameter of the leaf valve is made larger than the inner diameter of the valve seat by an amount equivalent to the valve seat surface width to increase the pressure receiving area on the back pressure side. ,
The upper and lower chambers of the cylinder and the lower part of the cylindrical chamber are filled with hydraulic oil, and the upper reservoir chamber of the cylindrical chamber is filled with low-pressure gas so that the pressure increase in the reservoir chamber acts as back pressure for the leaf valve. A gas-filled hydraulic shock absorber characterized by comprising: (2) The above-mentioned reservoir chamber and the upper space of the cylinder are communicated through a check seal to prevent the pressure in the reservoir chamber from propagating to the back pressure of the piston. The gas-filled hydraulic shock absorber according to item 1. (3) A small gap of 100μ or less is formed between the piston rod and the piston rod sliding bearing provided in the cylinder that communicates the reservoir chamber with the upper space of the cylinder, to prevent the pressure in the reservoir chamber from propagating to the back pressure of the piston. A gas-filled hydraulic shock absorber as set forth in claims 1 and 2 of the utility model registration claim, characterized in that the gas-filled hydraulic shock absorber is delayed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17587381U JPS5879152U (en) | 1981-11-25 | 1981-11-25 | gas-filled hydraulic shock absorber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17587381U JPS5879152U (en) | 1981-11-25 | 1981-11-25 | gas-filled hydraulic shock absorber |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5879152U JPS5879152U (en) | 1983-05-28 |
| JPS6246917Y2 true JPS6246917Y2 (en) | 1987-12-22 |
Family
ID=29968455
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17587381U Granted JPS5879152U (en) | 1981-11-25 | 1981-11-25 | gas-filled hydraulic shock absorber |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5879152U (en) |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3346272A (en) * | 1965-10-14 | 1967-10-10 | Monroe Auto Equipment Co | Vehicle suspension device |
| JPS5210983A (en) * | 1975-07-15 | 1977-01-27 | Agency Of Ind Science & Technol | Test method of tenacity of cutting tool material by non-cutting |
| JPS52124585A (en) * | 1976-04-10 | 1977-10-19 | Tokico Ltd | Buffer |
| US4076276A (en) * | 1976-07-09 | 1978-02-28 | Monroe Auto Equipment Company | Base valve for independent wheel suspension strut |
| JPS53109075A (en) * | 1977-03-04 | 1978-09-22 | Kayaba Ind Co Ltd | Oil and gas isolating double cylinder type shock absorber |
| JPS53115476A (en) * | 1978-01-17 | 1978-10-07 | Honda Motor Co Ltd | Hydraulic buffer for vehicles |
| JPS5623057A (en) * | 1979-08-03 | 1981-03-04 | Fujitsu Ltd | Data highway system |
| JPS5676741A (en) * | 1979-11-26 | 1981-06-24 | Showa Mfg Co Ltd | Damping force generator for hydraulic shock absorber |
| JPS6040921A (en) * | 1984-07-02 | 1985-03-04 | Matsushita Electric Ind Co Ltd | Measuring device |
-
1981
- 1981-11-25 JP JP17587381U patent/JPS5879152U/en active Granted
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3346272A (en) * | 1965-10-14 | 1967-10-10 | Monroe Auto Equipment Co | Vehicle suspension device |
| JPS5210983A (en) * | 1975-07-15 | 1977-01-27 | Agency Of Ind Science & Technol | Test method of tenacity of cutting tool material by non-cutting |
| JPS52124585A (en) * | 1976-04-10 | 1977-10-19 | Tokico Ltd | Buffer |
| US4076276A (en) * | 1976-07-09 | 1978-02-28 | Monroe Auto Equipment Company | Base valve for independent wheel suspension strut |
| JPS53109075A (en) * | 1977-03-04 | 1978-09-22 | Kayaba Ind Co Ltd | Oil and gas isolating double cylinder type shock absorber |
| JPS53115476A (en) * | 1978-01-17 | 1978-10-07 | Honda Motor Co Ltd | Hydraulic buffer for vehicles |
| JPS5623057A (en) * | 1979-08-03 | 1981-03-04 | Fujitsu Ltd | Data highway system |
| JPS5676741A (en) * | 1979-11-26 | 1981-06-24 | Showa Mfg Co Ltd | Damping force generator for hydraulic shock absorber |
| JPS6040921A (en) * | 1984-07-02 | 1985-03-04 | Matsushita Electric Ind Co Ltd | Measuring device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5879152U (en) | 1983-05-28 |
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