JP2002227903A - Valve structure of hydraulic shock absorber - Google Patents
Valve structure of hydraulic shock absorberInfo
- Publication number
- JP2002227903A JP2002227903A JP2001016543A JP2001016543A JP2002227903A JP 2002227903 A JP2002227903 A JP 2002227903A JP 2001016543 A JP2001016543 A JP 2001016543A JP 2001016543 A JP2001016543 A JP 2001016543A JP 2002227903 A JP2002227903 A JP 2002227903A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- sub
- leaf
- leaf valve
- opening window
- 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.)
- Granted
Links
Landscapes
- Fluid-Damping Devices (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、自動車の懸架装
置など車体の振動を抑制する油圧緩衝器に関し、特に減
衰力発生構造の改良に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic shock absorber for suppressing vibration of a vehicle body such as a suspension system of an automobile, and more particularly to an improvement in a damping force generating structure.
【０００２】[0002]
【従来の技術】この種の油圧緩衝器としては、例えば、
特開平３−１６３２３４号公報に開示された技術をピス
トンの上面側に適用した図４に示すようなものが知られ
ている。まず構造の概要を図面に基づいて説明する。油
圧緩衝器を車両に取り付けた状態では図４と上下関係が
同じであるので、以下、図４の上下関係で油圧緩衝器の
部材の位置或いは部位を説明する。2. Description of the Related Art As this type of hydraulic shock absorber, for example,
FIG. 4 shows an example in which the technique disclosed in JP-A-3-163234 is applied to the upper surface of a piston. First, an outline of the structure will be described with reference to the drawings. When the hydraulic shock absorber is attached to the vehicle, the vertical relationship is the same as that in FIG. 4. Therefore, the position or position of the member of the hydraulic shock absorber will be described below with reference to the vertical relationship in FIG. 4.
【０００３】車体と車輪との間に結合部材を介して取付
けられる油圧緩衝器は、車体側に取り付けられるピスト
ンロッド１の下端部にピストン５と伸側減衰力を制御す
るピストンバルブを組み付けそれを摺動自在に収容する
とともに、下端部に圧側減衰力を制御するベースバルブ
を装着したシリンダ２１を、車輪側に取り付けられる外
筒２２に収容し、外気を遮断するシール２４とロッドガ
イド２３とを収容したパッキンケース２５を外筒２２の
上部から嵌挿した後、外筒２２の上端部を全周溶接等に
より密封して形成されている。そして、シリンダ２１と
外筒２２の間にはタンク室Ｄが形成される。[0003] A hydraulic shock absorber mounted between a vehicle body and a wheel via a coupling member is provided with a piston 5 and a piston valve for controlling an extension side damping force which are assembled at a lower end portion of a piston rod 1 mounted on the vehicle body side. A cylinder 21, which is slidably housed and has a base valve for controlling a compression damping force at the lower end, is housed in an outer cylinder 22 attached to the wheel side, and a seal 24 and a rod guide 23 for shutting off outside air are formed. After the accommodated packing case 25 is inserted from above the outer cylinder 22, the upper end of the outer cylinder 22 is sealed by welding all around. A tank chamber D is formed between the cylinder 21 and the outer cylinder 22.
【０００４】作動油の充満したシリンダ２１内をピスト
ンロッド１が上昇する際には、密閉された上部室Ａの作
動油は、ピストンロッド１の下端部に組み付けられたピ
ストンバルブを介して下部室Ｂに流出し、この際の通路
抵抗が伸側減衰力となる。ピストンロッド１の上昇によ
って不足するピストンロッド退出体積分の作動油は、シ
リンダ２１の下端部に組み付けられたベースバルブを介
してタンク室Ｄに連なる底部室Ｃより補充される。When the piston rod 1 rises in the cylinder 21 filled with hydraulic oil, the hydraulic oil in the closed upper chamber A is supplied to the lower chamber via a piston valve attached to the lower end of the piston rod 1. B, and the passage resistance at this time becomes the extension-side damping force. Hydraulic oil corresponding to the piston rod withdrawal volume that is insufficient due to the rise of the piston rod 1 is replenished from the bottom chamber C connected to the tank chamber D via a base valve attached to the lower end of the cylinder 21.
【０００５】つぎに、伸側減衰力を制御するピストンバ
ルブについて説明する。Next, a piston valve for controlling the extension-side damping force will be described.
【０００６】ピストンロッド１の下端部には上部よりも
小径のインロー部１Ａが設けられ、ここにリーフバルブ
３からなる逆止弁ＣＶの最大撓みを規制するバルブスト
ッパ２，外周縁が逆止弁ＣＶの撓みの支持径となる環座
７，リーフバルブ３，上面がリーフバルブ３に対向する
ピストン５を順次嵌挿する。A lower end portion of the piston rod 1 is provided with a spigot portion 1A having a smaller diameter than that of the upper portion. A valve stopper 2 for restricting the maximum deflection of the check valve CV comprising the leaf valve 3 is provided at the outer peripheral edge. A ring seat 7, a leaf valve 3, and a piston 5 whose upper surface is opposed to the leaf valve 3 are sequentially inserted into the ring seat 7, which is a support diameter of the deflection of the CV.
【０００７】シリンダ２１内を上部室Ａと下部室Ｂに区
画し外周にガイド５Ｓを巻着したピストン５には、図２
（Ｂ）に示すように、その上面側に開口面積が順に小さ
くなる複数の上側開口窓５Ｄ〜５Ｇが設けられ、当該各
上側開口窓は外周ポート５Ａを介して下部室Ｂに連通す
るとともに、各上側開口窓の間に形成された凹部５Ｋは
内周ポート５Ｂを介して円環状の下側開口窓５Ｃに連通
している。上側開口窓５Ｄ〜５Ｇには、オリフィス５Ｈ
が例えば打刻により形成されている。FIG. 2 shows a piston 5 having a cylinder 21 partitioned into an upper chamber A and a lower chamber B and having a guide 5S wound around the outer periphery thereof.
As shown in (B), a plurality of upper opening windows 5D to 5G whose opening areas are sequentially reduced are provided on the upper surface side, and each of the upper opening windows communicates with the lower chamber B via the outer peripheral port 5A. The concave portion 5K formed between the upper opening windows communicates with the lower annular opening window 5C via the inner peripheral port 5B. The upper opening windows 5D to 5G have orifices 5H.
Are formed, for example, by embossing.
【０００８】続いて、下側開口窓５Ｃに対向し外径が順
に小さくなるリーフバルブ６Ａ，６Ｂ，６Ｃからなる伸
側減衰弁ＰＶ，外周縁が伸側減衰弁ＰＶの撓みの支持径
となる環座７，伸側減衰弁ＰＶの最大撓みを規制するバ
ルブストッパ８を順次組み付け、最後にピストンナット
９をインロー部１Ａのねじ部に螺着し、締付け工具によ
り締結することによりピストンバルブが構成される。[0008] Subsequently, the expansion damping valve PV comprising leaf valves 6A, 6B and 6C, which face the lower opening window 5C and whose outer diameter decreases in order, becomes the supporting diameter of the bending of the expansion damping valve PV. The piston seat is formed by sequentially assembling the ring seat 7 and the valve stopper 8 for regulating the maximum deflection of the extension side damping valve PV, and finally screwing the piston nut 9 to the threaded portion of the spigot portion 1A and fastening it with a tightening tool. Is done.
【０００９】作動油の充満したシリンダ２１内をピスト
ンロッド１が上昇する所謂伸長工程において、ピストン
速度が小さくピストン５の下側開口窓５Ｃと下部室Ｂ間
の圧力差が小さい所謂低速域においては、伸側減衰弁Ｐ
Ｖは下側開口窓５Ｃを覆窓している。このため上部室Ａ
の圧油は、ピストン５の外側開口窓５Ｄ〜５Ｇを包囲す
る窓枠に設けられたオリフィス５Ｈを通り、外周ポート
５Ａを介して下部室Ｂに流出し、この際の通路抵抗によ
り、ピストン速度のほぼ２乗に比例する低速域の伸側減
衰力を発生する。In a so-called elongation step in which the piston rod 1 rises in the cylinder 21 filled with hydraulic oil, in a so-called low-speed region where the piston speed is small and the pressure difference between the lower opening window 5C of the piston 5 and the lower chamber B is small. , Extension damping valve P
V covers the lower opening window 5C. Therefore, upper chamber A
Pressure oil flows through the orifice 5H provided in the window frame surrounding the outer opening windows 5D to 5G of the piston 5 to the lower chamber B through the outer peripheral port 5A. Generates an extension-side damping force in a low-speed range proportional to approximately the square of.
【００１０】ピストン速度が増大するのに伴い、オリフ
ィス５Ｈを通過する流量が増えオリフィス前後の圧力差
が増大するとともに、内周ポート５Ｂを介して上部室Ａ
に連通するピストン５の下側開口窓５Ｃと下部室Ｂ間の
圧力差も大きくなる。ピストン速度が中速域に近づくに
つれ、下側開口窓５Ｃに対向して配設されている伸側減
衰弁ＰＶの外周側が、その合成された撓み剛性に打ち勝
って、下側開口窓５Ｃの外側シート部から押し開かれ、
作動油が下部室Ｂに流出し、この際の通路抵抗と内周ポ
ート５Ｂの通路抵抗とにより中速域以降の伸側減衰力を
発生する。[0010] As the piston speed increases, the flow rate through the orifice 5H increases, the pressure difference before and after the orifice increases, and the upper chamber A through the inner peripheral port 5B.
The pressure difference between the lower opening window 5C of the piston 5 communicating with the lower chamber B and the lower chamber B also increases. As the piston speed approaches the middle speed range, the outer peripheral side of the extension damping valve PV disposed opposite to the lower opening window 5C overcomes the combined flexural rigidity, and becomes outside the lower opening window 5C. Pushed open from the seat,
Hydraulic oil flows out into the lower chamber B, and generates an extension damping force in the middle speed range and thereafter due to the passage resistance at this time and the passage resistance of the inner peripheral port 5B.
【００１１】リーフバルブ６Ａ，６Ｂ，６Ｃは外径が順
に小さくなつているため、その合成された撓み剛性は、
リーフバルブ６Ａの撓みの増加に伴い徐々に増加するの
で、ピストン速度に対してリニアに立ち上がる減衰力特
性を得ることができる。当該リーフバルブ６Ａ，６Ｂ，
６Ｃからなる伸側減衰弁ＰＶの撓み剛性と内周ポート５
Ｂの通路面積を適当に選択することにより、所要の減衰
力特性を得ることができる。Since the outer diameters of the leaf valves 6A, 6B, and 6C are sequentially reduced, the combined flexural rigidity is as follows.
Since it gradually increases as the deflection of the leaf valve 6A increases, it is possible to obtain a damping force characteristic that rises linearly with respect to the piston speed. The leaf valves 6A, 6B,
Flexural Rigidity of Inner Port 5 and Extension Side Damping Valve PV
By appropriately selecting the passage area of B, required damping force characteristics can be obtained.
【００１２】つぎに、圧側減衰力を制御するベースバル
ブについて説明する。まずガイド１１の軸部１１Ａに、
リーフバルブ１３と切欠きリーフバルブ１４からなる吸
込み弁ＤＶの最大撓みを規制するバルブストッパ１２，
外周縁が吸込み弁ＤＶの撓みの支持部となる環座１７，
リーフバルブ１３，当該リーフバルブ１３の下側に重畳
され外周に切欠き１４Ａを設けた切欠きリーフバルブ１
４，上面が切欠きリーフバルブ１４に対向するバルブケ
ース１５を順次嵌挿する。Next, a base valve for controlling the compression side damping force will be described. First, on the shaft 11A of the guide 11,
A valve stopper 12, which regulates the maximum deflection of the suction valve DV comprising a leaf valve 13 and a notched leaf valve 14,
A ring seat 17, the outer peripheral edge of which serves as a support for the deflection of the suction valve DV;
Leaf valve 13, a notched leaf valve 1 that is superimposed below the leaf valve 13 and has a notch 14 </ b> A on the outer periphery
4. The valve case 15 whose upper surface faces the notched leaf valve 14 is sequentially inserted.
【００１３】シリンダ２１の下端部に嵌着され下部室Ｂ
と底部室Ｃとを区画するバルブケース１５には、下部室
Ｂに連通する円環状の上側開口窓１５Ｄと円環状の下側
開口窓１５Ｃとを連通する内周ポート１５Ｂが穿孔され
るとともに、底部室Ｃと円環状の外側開口窓１５Ｅとを
連通する外周ポート１５Ａが穿孔されている。A lower chamber B fitted to the lower end of the cylinder 21
An inner peripheral port 15B communicating with an annular upper opening window 15D and an annular lower opening window 15C communicating with the lower chamber B is drilled in the valve case 15 that defines the lower chamber C and the bottom case C. An outer peripheral port 15A that communicates the bottom chamber C with the annular outer opening window 15E is drilled.
【００１４】続いて、ガイド１１の軸部１１Ａに、上記
バルブケース１５の下側開口窓１５Ｃに対向し外径が順
に小さくなるリーフバルブ１６Ａ，１６Ｂ，１６Ｃから
なる圧側減衰弁ＢＶ，更に、外周縁が圧側減衰弁ＢＶの
撓みの支持径となる環座１７，圧側減衰弁ＢＶの最大撓
みを規制するバルブストッパ１８を順次組み付け、最後
に、ガイド１１の軸部１１Ａの下端部を工具により加締
めることによりベースバルブが構成される。Subsequently, a pressure-side damping valve BV composed of leaf valves 16A, 16B and 16C whose outer diameters decrease in order in the axial portion 11A of the guide 11 is arranged opposite to the lower opening window 15C of the valve case 15, and the outer side. A ring seat 17 whose peripheral edge is the support diameter of the deflection of the compression-side damping valve BV, and a valve stopper 18 that regulates the maximum deflection of the compression-side attenuation valve BV are sequentially assembled. Finally, the lower end of the shaft 11A of the guide 11 is attached by a tool. By tightening, a base valve is configured.
【００１５】作動油の充満したシリンダ２１内をピスト
ンロッド１が下降する所謂収縮工程において、ピストン
速度が小さくバルブケース１５の下側開口窓１５Ｃと底
部室Ｃ間の圧力差が小さい所謂低速域においては、圧側
減衰弁ＢＶは下側開口窓１５Ｃを覆窓している。このた
めピストン５を介して容積の拡大する上部室Ａに補充さ
れる分を除いた下部室Ｂの圧油は、切欠きリーフバルブ
１４の切欠き１４Ａ，バルブケース１５の外側開口窓１
５Ｅ，外周ポート１５Ａを介して底部室Ｃに流出し、こ
の際の通路抵抗により、ピストン速度のほぼ２乗に比例
する低速域の圧側減衰力を発生する。In a so-called contraction step in which the piston rod 1 descends in the cylinder 21 filled with hydraulic oil, in a so-called low-speed range where the piston speed is small and the pressure difference between the lower opening window 15C of the valve case 15 and the bottom chamber C is small. , The compression side damping valve BV covers the lower opening window 15C. For this reason, the pressure oil in the lower chamber B excluding the amount replenished to the upper chamber A whose volume increases via the piston 5 is supplied to the notch 14A of the notch leaf valve 14 and the outer opening window 1 of the valve case 15.
5E, the fluid flows out to the bottom chamber C via the outer peripheral port 15A, and the passage resistance at this time generates a low-side pressure-side damping force proportional to the square of the piston speed.
【００１６】ここで、ピストン５を介して容積の拡大す
る上部室Ａに補充される下部室Ｂの圧油は、ピストン速
度が小さくピストン５の外側開口窓５Ｅと上部室Ａ間の
圧力差が小さい所謂低速域においては、リーフバルブ３
からなる逆止弁ＣＶは外側開口窓５Ｅを覆窓している。
このため、下部室Ｂの圧油はピストン５の外周ポート５
Ａを通り、オリフィス５Ｈを介して上部室Ａに補充され
る。Here, the pressure oil in the lower chamber B, which is replenished through the piston 5 to the upper chamber A whose volume is increased, has a low piston speed and a pressure difference between the outer opening window 5E of the piston 5 and the upper chamber A. In a small so-called low speed range, the leaf valve 3
The non-return valve CV of which covers the outer opening window 5E.
For this reason, the pressure oil in the lower chamber B is supplied to the outer peripheral port 5 of the piston 5.
A is supplied to the upper chamber A through the orifice 5H.
【００１７】ピストン速度が増大するのに伴い、切欠き
１４Ａを通過する流量が増え切欠き前後の圧力差が増大
するとともに、リーフバルブ１３の通孔１３Ａ，当該通
孔１３Ａと連通する切欠きリーフバルブ１４の開口部１
４Ｂ，バルブケース１５の上側開口窓１５Ｄ，内周ポー
ト１５Ｂを介して下部室Ｂに連通するバルブケース１５
の下側開口窓１５Ｃと、底部室Ｃ間との圧力差も大きく
なる。As the piston speed increases, the flow rate passing through the notch 14A increases, the pressure difference before and after the notch increases, and the through-hole 13A of the leaf valve 13 and the notch leaf communicating with the through-hole 13A. Opening 1 of valve 14
4B, the valve case 15 communicating with the lower chamber B via the upper opening window 15D of the valve case 15 and the inner peripheral port 15B.
The pressure difference between the lower opening window 15C and the bottom chamber C also increases.
【００１８】このため、ピストン速度が中速域に近づく
につれ、下側開口窓１５Ｃに対向して配設されている圧
側減衰弁ＢＶの外周側が、その合成された撓み剛性に打
ち勝って下側開口窓１５Ｃの外側シート部から押し開か
れ、作動油が底部室Ｃに流出し、この際の通路抵抗と内
周ポート１５Ｂの通路抵抗とにより中速域以降の圧側減
衰力を発生する。For this reason, as the piston speed approaches the middle speed range, the outer peripheral side of the compression side damping valve BV disposed opposite to the lower opening window 15C overcomes the combined bending rigidity and lower opening side. The hydraulic oil is pushed open from the outer sheet portion of the window 15C and flows out to the bottom chamber C, and a pressure-side damping force in the middle speed range and thereafter is generated by the passage resistance at this time and the passage resistance of the inner peripheral port 15B.
【００１９】リーフバルブ１６Ａ，１６Ｂ，１６Ｃは外
径が順に小さくなつているため、その合成された撓み剛
性は、リーフバルブ１６Ａの撓みの増加に伴い徐々に増
加するので、ピストン速度に対してリニアに立ち上がる
減衰力特性を得ることができる。当該リーフバルブ１６
Ａ，１６Ｂ，１６Ｃからなる圧側減衰弁ＢＶの撓み剛性
と内周ポート１５Ｂの通路面積を適当に選択することに
より、所要の減衰力特性を得ることができる。Since the outer diameters of the leaf valves 16A, 16B, and 16C are sequentially reduced, the combined flexural rigidity gradually increases with an increase in the flexure of the leaf valve 16A. Thus, a damping force characteristic that rises to a minimum can be obtained. The leaf valve 16
The required damping force characteristics can be obtained by appropriately selecting the flexural rigidity of the compression-side damping valve BV composed of A, 16B and 16C and the passage area of the inner peripheral port 15B.
【００２０】ここで、容積の拡大する上部室Ａには、ピ
ストン５の外周ポート５Ａを通り、リーフバルブ３から
なる逆止弁ＣＶの合成された撓み剛性に打ち勝って、逆
止弁ＣＶが、まず開口面積の最も大きい上側開口窓５Ｄ
から押し開かれ、ピストン速度が増大するに従って、開
口面積の小さくなる上側開口窓５Ｅ，５Ｆ，５Ｇの順に
押し開かれて、下部室Ｂから作動油が補充される。Here, in the upper chamber A whose volume is increased, the check valve CV passes through the outer peripheral port 5A of the piston 5 and overcomes the combined flexural rigidity of the check valve CV including the leaf valve 3, and First, the upper opening window 5D having the largest opening area
The upper opening windows 5E, 5F, and 5G are opened in the order of decreasing opening area as the piston speed increases, and hydraulic oil is replenished from the lower chamber B.
【００２１】逆に、ピストンロッド１が上昇する際に
は、底部室Ｃからバルブケース１５の外周ポート１５Ａ
を通り、リーフバルブ１３と切欠きリーフバルブ１４か
らなる吸込み弁ＤＶの撓み剛性に打ち勝って、吸込み弁
ＤＶが外側開口窓１５Ｅから押し開かれ、ピストンロッ
ド１の退出体積分の作動油が下部室Ｂに補充される。Conversely, when the piston rod 1 rises, the outer peripheral port 15A of the valve case 15
To overcome the bending rigidity of the suction valve DV composed of the leaf valve 13 and the notch leaf valve 14, the suction valve DV is pushed open from the outer opening window 15E, and the operating oil corresponding to the rejection volume of the piston rod 1 is released into the lower chamber. B is replenished.
【００２２】[0022]
【発明が解決しようとする課題】油圧緩衝器が収縮行程
から伸長行程に切り替わる際には、逆止弁ＣＶは圧力が
増大する上部室Ａと下部室Ｂ間の差圧によって速やかに
閉弁するので、上部室Ａの圧油は伸側減衰弁ＰＶを介し
て下部室Ｂに流出し、この際の通路抵抗により伸側減衰
力を発生する。一方、底部室Ｃはバルブケースの外周ポ
ート１５Ａを介して外側開口窓１５Ｅに連通している
が、当該外側開口窓１５Ｅには吸込み弁ＤＶが対向して
いるので、底部室Ｃの作動油は、まず、切欠きリーフバ
ルブ１４の切欠き１４Ａを介して、容積の拡大する下部
室Ｂに流入しようとする。When the hydraulic shock absorber switches from the contraction stroke to the extension stroke, the check valve CV closes promptly due to the differential pressure between the upper chamber A and the lower chamber B whose pressure increases. Therefore, the pressure oil in the upper chamber A flows out to the lower chamber B via the expansion-side damping valve PV, and the expansion-side damping force is generated by the passage resistance at this time. On the other hand, the bottom chamber C communicates with the outer opening window 15E via the outer peripheral port 15A of the valve case, but since the suction valve DV faces the outer opening window 15E, the hydraulic oil in the bottom chamber C is First, an attempt is made to flow through the notch 14A of the notch leaf valve 14 into the lower chamber B whose volume is increased.
【００２３】しかし、切欠き１４Ａの通路面積Ｓは、例
えば、切欠き巾＝１．５ｍｍ，切欠き数＝４，板厚＝
０．１５ｍｍの場合で、Ｓ＝１．５×４×０．１５＝
０．９ｍｍ２程度と小さい。このため、特に底部室Ｃと
下部室Ｂ間の差圧が小さいピストン速度の微低速域にお
いては、吸込み弁ＤＶを押し開くことができず下部室Ｂ
に作動油を十分補充できないため、減衰力の不連続を生
じてしまう。However, the passage area S of the notch 14A is, for example, notch width = 1.5 mm, number of notches = 4, plate thickness =
In the case of 0.15 mm, S = 1.5 × 4 × 0.15 =
0.9mm 2 is as small as about. For this reason, especially in a very low speed region of the piston speed where the pressure difference between the bottom chamber C and the lower chamber B is small, the suction valve DV cannot be pushed open, and the lower chamber B cannot be opened.
Since the hydraulic oil cannot be sufficiently replenished, the damping force becomes discontinuous.
【００２４】同様に、油圧緩衝器が伸長行程から収縮行
程に切り替わる際には、吸込み弁ＤＶは圧力が増大する
下部室Ｂと底部室Ｃ間の差圧によって速やかに閉弁する
ので、下部室Ｂの圧油は圧側減衰弁ＢＶを介して底部室
Ｃに流出し、この際の通路抵抗により圧側減衰力を発生
する。一方、下部室Ｂは外周ポート５Ａを介してピスト
ンの上側開口窓５Ｄ〜５Ｇに連通しているが、当該上側
開口窓には逆止弁ＣＶが対向しているので、下部室Ｂの
圧油は、まず、上側開口窓に設けられたオリフィス５Ｈ
を介して容積の拡大する上部室Ａに流入しようとする。Similarly, when the hydraulic shock absorber switches from the expansion stroke to the contraction stroke, the suction valve DV closes promptly due to the pressure difference between the lower chamber B and the bottom chamber C whose pressure increases. The pressure oil of B flows out to the bottom chamber C via the pressure side damping valve BV, and generates a pressure side damping force by the passage resistance at this time. On the other hand, the lower chamber B communicates with the upper opening windows 5D to 5G of the piston via the outer peripheral port 5A. However, since the check valve CV faces the upper opening window, the pressure oil in the lower chamber B is increased. First, the orifice 5H provided in the upper opening window
Through the upper chamber A whose volume increases.
【００２５】しかし、オリフィス５Ｈの通路面積Ｓは、
例えば、巾＝２ｍｍ，オリフィス数＝４，深さ＝０．１
５ｍｍの場合で、Ｓ＝２×４×０．１５＝１．２ｍｍ２
程度と小さい。このため、特に下部室Ｂと上部室Ａ間の
差圧が小さいピストン速度の微低速域においては、逆止
弁ＣＶを押し開くことができず上部室Ａに作動油を十分
補充することができないため、減衰力の不連続を生じて
しまう。However, the passage area S of the orifice 5H is
For example, width = 2 mm, number of orifices = 4, depth = 0.1
In the case of 5 mm, S = 2 × 4 × 0.15 = 1.2 mm 2
About small. For this reason, especially in a very low speed range of the piston speed where the differential pressure between the lower chamber B and the upper chamber A is small, the check valve CV cannot be pushed open, and the upper chamber A cannot be sufficiently replenished with the operating oil. Therefore, discontinuity of the damping force occurs.
【００２６】本発明は以上のような実情に鑑みてなされ
たものであり、その目的とするところは、ピストン側の
逆止弁と伸側減衰弁又はバルブケース側の吸込み弁と圧
側減衰弁を小さな差圧で遅滞なく滑らかに開弁させ、減
衰力の不連続に起因する異音の発生を防止することので
きる油圧緩衝器を提供することである。The present invention has been made in view of the above circumstances, and an object thereof is to provide a check valve and an expansion damping valve on the piston side or a suction valve and a compression damping valve on the valve case side. An object of the present invention is to provide a hydraulic shock absorber that can smoothly open a valve with a small differential pressure without delay and prevent generation of abnormal noise due to discontinuity of damping force.
【００２７】[0027]
【問題を解決するための手段】本発明は、シリンダ内に
二つの油室を区画するピストン又はバルブケースからな
る隔壁部材を設け、隔壁部材には二つの油室を連通する
ポートと、このポートの出口側開口窓を開閉する逆止弁
と伸側減衰弁又は吸込み弁と圧側減衰弁とを設けている
油圧緩衝器を前提とする。SUMMARY OF THE INVENTION According to the present invention, there is provided a partition member comprising a piston or a valve case for partitioning two oil chambers in a cylinder, wherein the partition member has a port communicating the two oil chambers, It is assumed that a hydraulic shock absorber is provided with a check valve and an extension damping valve or a suction valve and a compression damping valve for opening and closing the outlet opening window.
【００２８】課題を解決するため本発明の採った第１の
手段は、隔壁部材の上面側に開口面積が異なる複数の上
側開口窓を設け、逆止弁又は吸込み弁を、各上側開口窓
に対向するリーフバルブと、リーフバルブの背面に重ね
たリーフバルブより小径のサブリーフバルブと、サブリ
ーフバルブの背面に重ねたサブリーフバルブより小径の
環座とで構成し、上記サブリーフバルブと環座とは中央
の取付孔を偏芯させることにより円周方向に沿って剛性
を変化させ、開口面積の大きい上側開口窓から開口面積
の小さい上側開口窓に対応して、それぞれ剛性の小さい
部位から剛性の大きい部位を位置合わせしながらサブリ
ーフバルブと環座とを配置したことである。In order to solve the problem, a first means adopted by the present invention is to provide a plurality of upper opening windows having different opening areas on the upper surface side of the partition member, and to attach a check valve or a suction valve to each upper opening window. An opposing leaf valve, a sub-leaf valve smaller in diameter than the leaf valve superimposed on the back of the leaf valve, and a ring seat smaller in diameter than the sub-leaf valve superimposed on the back of the sub-leaf valve; With the seat, the rigidity is changed along the circumferential direction by eccentricizing the center mounting hole, and from the upper opening window with a larger opening area to the upper opening window with a smaller opening area, from the parts with lower rigidity, respectively. That is, the sub-leaf valve and the ring seat are arranged while positioning a portion having high rigidity.
【００２９】つぎに第２の手段は、隔壁部材の上面側に
開口面積が異なる複数の上側開口窓を設け、逆止弁又は
吸込み弁を、各上側開口窓に対向するリーフバルブと、
リーフバルブの背面に重ねられ各上側開口窓に対応する
花弁状の支持片を備えたサブリーフバルブと、サブリー
フバルブの背面に重ねたサブリーフバルブより小径の環
座とで構成し、上記サブリーフバルブは、各支持片の巾
と板厚、或いは軸芯から各支持片の外周縁に至る距離を
変えることにより各支持片の剛性を変化させるととも
に、環座は中央の取付孔を偏芯させることにより円周方
向に沿って剛性を変化させ、開口面積の大きい上側開口
窓から開口面積の小さい上側開口窓に対応して、それぞ
れ剛性の小さい部位から剛性の大きい部位を位置合わせ
しながらサブリーフバルブと環座とを配置したことであ
る。Next, a second means is to provide a plurality of upper opening windows having different opening areas on the upper surface side of the partition member, and to provide a check valve or a suction valve with a leaf valve facing each upper opening window;
A sub-leaf valve provided with petal-shaped support pieces that are stacked on the back surface of the leaf valve and correspond to the respective upper opening windows, and a ring seat having a smaller diameter than the sub-leaf valve stacked on the back surface of the sub-leaf valve; The leaf valve changes the rigidity of each support piece by changing the width and thickness of each support piece, or the distance from the axis to the outer peripheral edge of each support piece, and the ring seat decenters the center mounting hole. By changing the rigidity along the circumferential direction, the sub-positioning is performed while aligning the lower rigidity portion to the higher rigidity portion corresponding to the upper opening window having a larger opening area and the upper opening window having a smaller opening area, respectively. That is, the leaf valve and the ring seat are arranged.
【００３０】また第３の手段は、隔壁部材の下面側に下
側開口窓を設け、伸側減衰弁又は圧側減衰弁を、各下側
開口窓に対向するリーフバルブと、リーフバルブの背面
に重ねたリーフバルブより小径のサブリーフバルブと、
サブリーフバルブの背面に重ねたサブリーフバルブより
小径の環座とで構成し、上記サブリーフバルブと環座と
は中央の取付孔を偏芯させることにより円周方向に沿っ
て剛性を変化させ、それぞれ剛性の小さい部位から剛性
の大きい部位を位置合わせしながらサブリーフバルブと
環座とを配置したことである。A third means is that a lower opening window is provided on the lower surface side of the partition member, and the extension side damping valve or the compression side damping valve is provided on the leaf valve facing each lower opening window and on the back surface of the leaf valve. A sub-leaf valve with a smaller diameter than the stacked leaf valve,
It consists of a ring seat smaller than the sub-leaf valve stacked on the back of the sub-leaf valve, and the sub-leaf valve and the ring seat change the rigidity along the circumferential direction by eccentricizing the center mounting hole. In addition, the sub-leaf valve and the ring seat are arranged while aligning the portions having low rigidity with the portions having high rigidity.
【００３１】[0031]
【発明の実施の形態】本発明に係わる油圧緩衝器は、図
１に示すように、図４の従来技術と同じ基本構造を備
え、ピストンロッド１０１がその下端部に装着されたピ
ストン５を介して、シリンダ２１内に移動自在に挿入さ
れるとともに、上部室Ａと下部室Ｂを区画する。また、
シリンダ２１の下端部にはバルブケース１１５が嵌着さ
れ、同じく下部室Ｂとタンク室Ｄに連通する底部室Ｃを
区画している。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS As shown in FIG. 1, a hydraulic shock absorber according to the present invention has the same basic structure as that of the prior art shown in FIG. 4, and a piston rod 101 is provided via a piston 5 mounted on the lower end thereof. Thus, the upper chamber A and the lower chamber B are partitioned while being movably inserted into the cylinder 21. Also,
A valve case 115 is fitted to the lower end of the cylinder 21 to define a bottom chamber C communicating with the lower chamber B and the tank chamber D.
【００３２】本発明は、ピストン又はバルブケースの上
面側に下部室又は底部室に連なり開口面積の異なる複数
の上側開口窓を設けるとともに、開口面積の最も大きい
上側開口窓には逆止弁ＣＶ又は吸込み弁ＤＶの撓み剛性
の最も小さい部分を対応させ、開口面積の最も小さい上
側開口窓には撓み剛性の最も大きい部分を対応できるよ
うに位置合わせをして組み付け、逆止弁ＣＶ又は吸込み
弁ＤＶを、差圧が小さいピストン速度の微低速域から滑
らかに開弁させ、減衰力の不連続に起因する異音の発生
を防止する油圧緩衝器の構造に関するものである。According to the present invention, a plurality of upper opening windows having different opening areas are provided on the upper surface side of a piston or a valve case and connected to a lower chamber or a bottom chamber, and a check valve CV or a check valve is provided on the upper opening window having the largest opening area. The suction valve DV has a portion with the smallest flexural rigidity corresponding thereto, and the upper opening window having the smallest opening area is aligned and assembled so as to correspond to the portion with the largest flexural rigidity. The check valve CV or the suction valve DV The present invention relates to a structure of a hydraulic shock absorber which smoothly opens a valve from a very low speed range of a piston speed where a differential pressure is small and prevents generation of abnormal noise due to discontinuity of damping force.
【００３３】開弁圧力の低減効果は、特にベースバルブ
側の吸込み弁ＤＶにおいて顕著であるが、ピストンバル
ブ側の逆止弁ＣＶについても同様な効果がある。本発明
に係わる吸込み弁ＤＶと逆止弁ＣＶとは、部品の内径が
異なる程度で構造，作用，効果が類似しているため、ま
ず、本発明をピストンバルブ側に適用した第１実施形態
から説明する。The effect of reducing the valve opening pressure is particularly remarkable in the suction valve DV on the base valve side, but the same effect is also obtained in the check valve CV on the piston valve side. The suction valve DV and the check valve CV according to the present invention are similar in structure, operation and effect to the extent that the inside diameters of the components are different, and therefore, first, from the first embodiment in which the present invention is applied to the piston valve side. explain.
【００３４】ピストンロッド１０１の下端部には、図１
（Ａ）に示すように上部よりも小径のインロー部１０１
Ａが設けられ、ここに図２（Ａ）に示すサブリーフバル
ブ１０３とリーフバルブ１０４からなる逆止弁ＣＶの最
大撓みを規制するバルブストッパ１０２，外周縁１０９
Ａが逆止弁ＣＶの撓みの支持部となる環座１０９，サブ
リーフバルブ１０３，リーフバルブ１０４，図２（Ｃ）
に示す上面がリーフバルブ１０４に対向するピストン５
を、図１（Ｂ）に示すようにインロー部１０１Ａの一部
をＤ字状に切除した平坦部１０１Ｂに、各部品の内径側
の位置決め用直線部Ｗを位置合わせして順次嵌挿する。At the lower end of the piston rod 101, FIG.
(A) As shown in FIG.
2A, a valve stopper 102 for regulating the maximum deflection of a check valve CV composed of a sub-leaf valve 103 and a leaf valve 104 shown in FIG.
A is a ring seat 109, a sub-leaf valve 103, a leaf valve 104, which serves as a support portion for the deflection of the check valve CV, FIG. 2 (C).
The piston 5 whose upper surface shown in FIG.
As shown in FIG. 1B, the positioning linear portion W on the inner diameter side of each component is aligned and inserted into a flat portion 101B in which a part of the spigot portion 101A is cut out in a D-shape.
【００３５】上記環座１０９及びサブリーフバルブ１０
３は、図２（Ｄ）にサブリーフバルブで例示するよう
に、双方とも内径の軸芯Ｚからその外周縁１０９Ａ及び
１０３Ａに至る距離が、開口面積の最も大きい上側開口
窓５Ｄに対向するＲｄが最短で、上側開口窓の開口面積
が５Ｅ＞５Ｆ＞５Ｇと順に小さくなるに従って、Ｒｅ＜
Ｒｆ＜Ｒｇと順に長くなるように形成する。サブリーフ
バルブ１０３の外周縁１０３Ａは、上記環座１０９の外
周縁１０９Ａよりも大きく且つリーフバルブ１０４の外
径１０４Ａよりも小さく設定されている。The ring seat 109 and the sub-leaf valve 10
As shown in FIG. 2 (D), the distance Rd from the axis Z having the inner diameter to the outer peripheral edges 109A and 103A is opposite to the upper opening window 5D having the largest opening area. Is shorter, and as the opening area of the upper opening window becomes smaller in the order of 5E>5F> 5G, Re <
It is formed so as to become longer in order of Rf <Rg. The outer periphery 103A of the sub-leaf valve 103 is set larger than the outer periphery 109A of the ring seat 109 and smaller than the outer diameter 104A of the leaf valve 104.
【００３６】シリンダ２１内を上部室Ａと下部室Ｂに区
画し外周にガイド５Ｓを巻着したピストン５の上面側に
は、図２（Ｃ）に示すように、開口面積が順に小さくな
る複数の上側開口窓５Ｄ〜５Ｇが設けられ、当該各上側
開口窓は外周ポート５Ａを介して下部室Ｂに連通すると
ともに、各上側開口窓の間に形成された凹部５Ｋは、図
３（Ａ）に示すように、内周ポート５Ｂを介して円環状
の下側開口窓５Ｃに連通している。As shown in FIG. 2C, on the upper surface side of the piston 5 in which the inside of the cylinder 21 is divided into an upper chamber A and a lower chamber B and a guide 5S is wound around the outer periphery, a plurality of openings having a smaller opening area are sequentially formed. The upper opening windows 5D to 5G are provided, each upper opening window communicates with the lower chamber B via the outer peripheral port 5A, and the recess 5K formed between each upper opening window is shown in FIG. As shown in the figure, the inner peripheral port 5B communicates with the annular lower opening window 5C.
【００３７】続いて、ピストン５の下側開口窓５Ｃに対
向し外径１０６Ａが内径と同芯のリーフバルブ１０６と
当該リーフバルブ１０６より外周縁１０７Ａ，１０８Ａ
が順に小さくなるサブリーフバルブ１０７，１０８から
なる伸側減衰弁ＰＶ，サブリーフバルブ１０７の外径よ
りも小さく外周縁１０９Ａが伸側減衰弁ＰＶの撓みの支
持部となる環座１０９を、インロー部１０１Ａの一部を
Ｄ字状に切除した平坦部１０１Ｂに、各部品の内径側の
位置決め用直線部Ｗを位置合わせして順次嵌挿する。続
いて、伸側減衰弁ＰＶの最大撓みを規制するバルブスト
ッパ８を組み付け、最後にピストンナット９をインロー
部１０１Ａのねじ部に螺着し、締付け工具により締結す
ることによりピストンバルブが構成される。Subsequently, a leaf valve 106 facing the lower opening window 5C of the piston 5 and having an outer diameter 106A concentric with the inner diameter, and outer peripheral edges 107A, 108A from the leaf valve 106 are provided.
The expansion-side damping valve PV, which is composed of sub-leaf valves 107 and 108, in which the outer peripheral edge 109A is smaller than the outer diameter of the sub-leaf valve 107, and the ring seat 109 serving as a support portion for bending the expansion-side damping valve PV, The positioning linear portion W on the inner diameter side of each component is aligned and inserted into the flat portion 101B in which a part of the portion 101A is cut out in a D shape. Subsequently, a valve stopper 8 for restricting the maximum deflection of the extension-side damping valve PV is assembled, and finally, a piston nut 9 is screwed to the threaded portion of the spigot portion 101A and fastened by a fastening tool, thereby forming a piston valve. .
【００３８】ここでサブリーフバルブ１０７及び１０８
は、図３（Ｂ）に示すように、内径の軸芯Ｚからその外
周縁１０７Ａ及び１０８Ａに至る距離が、例えば、開口
面積の最も大きい上側開口窓５Ｄに対向するＸ側が最短
で、反対側のＹ側に向かって徐々に長くなるように形成
され、外周縁１０７Ａ及び１０８Ａが上記環座１０９の
外周縁１０９Ａよりも大きく且つリーフバルブ１０６の
外径１０６Ａよりも順に小さくなるように設定されてい
る。Here, the sub-leaf valves 107 and 108
As shown in FIG. 3B, the distance from the inner diameter axis Z to the outer peripheral edges 107A and 108A is, for example, the shortest on the X side facing the upper opening window 5D having the largest opening area, and the opposite side. The outer peripheral edges 107A and 108A are set to be larger than the outer peripheral edge 109A of the ring seat 109 and to be smaller in order than the outer diameter 106A of the leaf valve 106. I have.
【００３９】サブリーフバルブ１０３とリーフバルブ１
０４、又は、リーフバルブ１０６とサブリーフバルブ１
０７，１０８の基端側を背面から担持する環座１０９の
外周縁１０９Ａは、上記各サブリーフバルブの外周縁よ
りも小さく、内径の軸芯Ｚからその外周縁に至る距離
が、開口面積の最も大きい上側開口窓５Ｄに対向するＸ
側が最短で、開口面積が小さくなるに従って徐々に長く
なるように位置合わせして重畳する。Sub-leaf valve 103 and leaf valve 1
04 or leaf valve 106 and sub-leaf valve 1
The outer peripheral edge 109A of the ring seat 109 that carries the base end sides of the sub-leaves 07 and 108 from the back is smaller than the outer peripheral edge of each of the above-mentioned sub-leaf valves, and the distance from the inner diameter axis Z to the outer peripheral edge is smaller than the opening area. X opposing the largest upper opening window 5D
Positioning and superimposing are performed so that the side is the shortest and gradually becomes longer as the opening area becomes smaller.
【００４０】要求される減衰力によっては、図２（Ｂ）
に示すように、逆止弁ＣＶ側のサブリーフバルブ１０３
を省略してもよいし、サブリーフバルブ１０３又はリー
フバルブ１０４を複数枚重畳して使用してもよい。同様
に図３（Ｃ）に示すように、、伸側減衰弁ＰＶ側のリー
フバルブ１０６に重畳されるサブリーフバルブ１０７，
１０８のいずれか１方又は両方ともに省略してもよい
し、リーフバルブ１０６又はサブリーフバルブ１０７，
１０８を複数枚重畳して使用してもよい。Depending on the required damping force, FIG.
As shown in the figure, the sub-leaf valve 103 on the check valve CV side
May be omitted, or a plurality of sub-leaf valves 103 or leaf valves 104 may be used. Similarly, as shown in FIG. 3C, the sub-leaf valve 107, which is superimposed on the leaf valve 106 on the extension-side damping valve PV side,
108 may be omitted, or the leaf valve 106 or the sub-leaf valve 107,
108 may be used in a superimposed manner.
【００４１】上記第１実施形態の逆止弁ＣＶ側において
は、サブリーフバルブ１０３の外周縁が円形の場合につ
いて説明したが、図２（Ｅ）に示す第２実施形態のよう
に、サブリーフバルブ２０３に形成した花弁状の各支持
片２０３Ｄ，２０３Ｅ，２０３Ｆ，２０３Ｇの基端部２
０３Ｈから外周縁にかけての同心円上で測った巾Ｗを、
開口面積の最も大きい上側開口窓５Ｄに対向するＸ側の
２０３Ｄが最小で、開口面積が５Ｅ，５Ｆ，５Ｇと小さ
くなるに従って、２０３Ｅ，２０３Ｆ，２０３Ｇと段階
的に大きくなるように形成してもよい。サブリーフバル
ブ２０３の撓み剛性は、上記各支持片の巾Ｗと板厚とに
よって調整することができる。On the check valve CV side in the first embodiment, the case where the outer peripheral edge of the sub-leaf valve 103 is circular has been described. However, as in the second embodiment shown in FIG. Base end 2 of each of petal-shaped support pieces 203D, 203E, 203F, and 203G formed on valve 203
The width W measured on a concentric circle from 03H to the outer periphery is
Even if it is formed so that 203D on the X side facing the upper opening window 5D having the largest opening area is the smallest and the opening area becomes smaller as 5E, 5F, 5G, it gradually increases to 203E, 203F, 203G. Good. The bending rigidity of the sub-leaf valve 203 can be adjusted by the width W and the plate thickness of each of the support pieces.
【００４２】また、図２（Ｆ）に示す第２実施形態の他
の実施例は、サブリーフバルブ３０３の内径の軸芯Ｚか
ら各支持片３０３Ｄ，３０３Ｅ，３０３Ｆ，３０３Ｇの
外周縁に至る距離Ｒを、開口面積の最も大きい上側開口
窓５Ｄに対向するＸ側の３０３Ｄが最小で、開口面積が
５Ｅ，５Ｆ，５Ｇと小さくなるに従って、３０３Ｅ，３
０３Ｆ，３０３Ｇと段階的に大きくなるように形成した
ものである。サブリーフバルブ３０３の撓み剛性は、上
記各支持片の距離Ｒと板厚とによって調整することがで
きる。In another example of the second embodiment shown in FIG. 2F, the distance from the axis Z of the inner diameter of the sub-leaf valve 303 to the outer peripheral edge of each of the support pieces 303D, 303E, 303F, 303G is different. R is reduced as 303D on the X side facing the upper opening window 5D having the largest opening area becomes the smallest and the opening area becomes smaller as 5E, 5F, 5G.
It is formed so as to gradually increase to 03F and 303G. The flexural rigidity of the sub-leaf valve 303 can be adjusted by the distance R and the plate thickness of each support piece.
【００４３】上記サブリーフバルブ２０３，３０３とリ
ーフバルブ１０４の基端側を背面から担持する環座１０
９の外周縁１０９Ａは、上記各サブリーフバルブの基端
部２０３Ｈ（３０３Ｈ）よりも小さく、内径の軸芯Ｚか
らその外周縁に至る距離が、開口面積の最も大きい上側
開口窓５Ｄに対向するＸ側が最短で、開口面積が小さく
なるに従って徐々に長くなるように位置合わせして重畳
する。A ring seat 10 for supporting the base ends of the sub-leaf valves 203 and 303 and the leaf valve 104 from the back.
9 is smaller than the base end portion 203H (303H) of each of the sub-leaf valves, and the distance from the axis Z of the inner diameter to the outer peripheral edge thereof is opposed to the upper opening window 5D having the largest opening area. Positioning and superimposing are performed so that the X side is the shortest and gradually becomes longer as the opening area becomes smaller.
【００４４】この結果、逆止弁ＣＶの撓み剛性は、いず
れの実施形態においても開口面積の最も大きい上側開口
窓５Ｄに対向する部分が最小で、開口面積が小さくなる
に従って大きくなる一方、伸側減衰弁ＰＶの撓み剛性
は、図３（Ｂ）に示すＸ側が最小で、Ｙ側にかけて徐々
に大きくなる。As a result, the flexural rigidity of the check valve CV is minimum at the portion facing the upper opening window 5D having the largest opening area in any of the embodiments, and increases as the opening area decreases, while increasing on the extension side. The bending rigidity of the damping valve PV is minimum on the X side shown in FIG. 3B and gradually increases toward the Y side.
【００４５】上記花弁状のサブリーフバルブ２０３及び
３０３は、図３（Ｂ）に示すリーフバルブ１０６に合せ
てサイズを小さくすれば、伸側減衰弁ＰＶ側にも使用す
ることができる。この場合は、所要の減衰力に合せてリ
ーフバルブ１０６を何枚か重ねて使用し、その下側にサ
イズを小さくした花弁状のサブリーフバルブと前記環座
１０９とを位置合わせして重畳する。作用及び効果は上
述した逆止弁ＣＶ側と同様であるので、詳細な説明は省
略する。The petal-shaped sub-leaf valves 203 and 303 can be used also on the extension-side damping valve PV side if the size is reduced in accordance with the leaf valve 106 shown in FIG. In this case, a plurality of leaf valves 106 are used one upon another in accordance with the required damping force, and a petal-shaped sub-leaf valve having a reduced size and the ring seat 109 are aligned and overlapped below the leaf valves 106. . The operation and effect are the same as those of the above-described check valve CV side, and thus detailed description is omitted.
【００４６】作動油の充満したシリンダ２１内をピスト
ンロッド１が下降する収縮行程から、ピストンロッド１
が上昇する伸長行程に切り替わる際に、ピストン速度が
小さくピストン５の下側開口窓５Ｃと下部室Ｂ間の圧力
差が小さい微低速域においては、伸側減衰弁ＰＶの撓み
剛性はＸ側が最小であるため、上部室Ａに連通する下側
開口窓５Ｃの圧油は、当該下側開口窓５Ｃから伸側減衰
弁ＰＶのＸ側を小さい差圧で押し開いて下部室Ｂに流出
し、この際の通路抵抗により、ピストン速度に対してリ
ニアに立ち上がる低速域の伸側減衰力を発生する。From the contraction stroke in which the piston rod 1 descends in the cylinder 21 filled with hydraulic oil, the piston rod 1
When switching to the extension stroke in which the pressure rises, in the very low speed region where the piston speed is small and the pressure difference between the lower opening window 5C and the lower chamber B of the piston 5 is small, the flexural rigidity of the extension side damping valve PV is the smallest on the X side. Therefore, the pressure oil in the lower opening window 5C communicating with the upper chamber A pushes open the X side of the extension damping valve PV from the lower opening window 5C with a small differential pressure and flows out to the lower chamber B, Due to the passage resistance at this time, an extension-side damping force in a low-speed region rising linearly with respect to the piston speed is generated.
【００４７】従来構造の伸側減衰弁は撓み剛性が全周に
亘り一様であるため、下側開口窓５Ｃの外側シート部か
ら一気に開弁するのに対して、本発明の伸側減衰弁ＰＶ
は撓み剛性が最小であるＸ側から徐々に開弁する。伸側
減衰弁の外側シート部に対する吸着力は、一気に開弁す
るよりも徐々に開弁した方が小さいので、この点も開弁
圧力を低下させる要因となる。Since the expansion damping valve of the conventional structure has a uniform bending rigidity over the entire circumference, the expansion damping valve is opened at once from the outer seat portion of the lower opening window 5C, whereas the expansion damping valve of the present invention is opened. PV
The valve gradually opens from the X side where the flexural rigidity is minimum. The attraction force of the extension damping valve to the outer seat portion is smaller when the valve is gradually opened than when it is opened all at once, and this point also causes a reduction in the valve opening pressure.
【００４８】ピストン速度が増大するのに伴い、内周ポ
ート５Ｂを介して上部室Ａに連通するピストン５の下側
開口窓５Ｃと下部室Ｂ間の圧力差も大きくなるので、伸
側減衰弁ＰＶは、撓み剛性の小さいＸ側から撓み剛性の
大きいＹ側にかけて徐々に且つ連続的に押し開かれる。
このため、ピストン速度の低速域から中速域にかけて、
ピストン速度に対してリニアに立ち上がる減衰力特性を
得ることができる。As the piston speed increases, the pressure difference between the lower opening window 5C of the piston 5 communicating with the upper chamber A via the inner peripheral port 5B and the lower chamber B also increases. The PV is gradually and continuously pushed open from the X side having a small flexural rigidity to the Y side having a large flexural rigidity.
For this reason, from low to medium piston speed,
It is possible to obtain a damping force characteristic that rises linearly with respect to the piston speed.
【００４９】リーフバルブ１０６Ａとサブリーフバルブ
１０７，１０８からなり、ピストン速度の中速域までの
減衰力を制御する伸側減衰弁ＰＶの撓み剛性と、中速域
を越える減衰力を制御する内周ポート５Ｂの通路面積と
を適当に選択することにより、所要の減衰力特性を得る
ことができる。The flexural rigidity of the expansion-side damping valve PV, which is composed of the leaf valve 106A and the sub-leaf valves 107 and 108, controls the damping force of the piston speed up to the medium speed range, and controls the damping force exceeding the medium speed range. By appropriately selecting the passage area of the peripheral port 5B, required damping force characteristics can be obtained.
【００５０】つぎに、ピストンバルブ側の第１実施形態
と同様な構造をベースバルブ側に適用したベースバルブ
側の第１実施形態について説明する。ピストンバルブに
対する主な変更点は、ピストン５及びピストンロッド１
０１のインロー部がバルブケース１１５及びガイド１１
１に置き換わり、それに伴い各部品の内径が小さくなる
ことである。ベースバルブ側の部品はピストンバルブ側
の部品と形状が類似しているので、図２の各図面を流用
して（ ）付きで表示する。Next, a description will be given of a first embodiment on the base valve side in which a structure similar to that of the first embodiment on the piston valve side is applied to the base valve side. The main changes to the piston valve are the piston 5 and the piston rod 1
01 is the valve case 115 and the guide 11
1 and the inner diameter of each component is accordingly reduced. The parts on the base valve side are similar in shape to the parts on the piston valve side, so the figures in FIG.
【００５１】まずガイド１１１の軸部１１１Ａに、図２
（Ａ）に示すように、外径が内径と同心のリーフバルブ
１１４とサブリーフバルブ１１３とからなる吸込み弁Ｄ
Ｖの撓みの支持部となる環座１１９，サブリーフバルブ
１１３，リーフバルブ１１４，図２（Ｃ）に示す上面が
リーフバルブ１１４に対向するバルブケース１１５を、
図１（Ｂ）に示すように軸部１１１Ａの一部をＤ字状に
切除した平坦部１１１Ｂに、各部品の内径側の位置決め
用直線部Ｗを位置合わせして順次嵌挿する。First, the shaft 111A of the guide 111 is
(A), a suction valve D composed of a leaf valve 114 and a sub-leaf valve 113 whose outer diameter is concentric with the inner diameter.
The ring seat 119, the sub-leaf valve 113, the leaf valve 114, and the valve case 115 whose upper surface faces the leaf valve 114 shown in FIG.
As shown in FIG. 1B, the positioning linear portion W on the inner diameter side of each component is aligned and inserted into the flat portion 111B in which a part of the shaft portion 111A is cut out in a D-shape.
【００５２】上記環座１１９及びサブリーフバルブ１１
３は、図２（Ｄ）にサブリーフバルブで例示するよう
に、双方とも内径の軸芯Ｚからその外周縁１１９Ａ及び
１１３Ａに至る距離が、開口面積の最も大きい上側開口
窓１１５Ｄに対向するＲｄが最短で、上側開口窓の開口
面積が１１５Ｅ＞１１５Ｆ＞１１５Ｇと順に小さくなる
に従って、Ｒｅ＜Ｒｆ＜Ｒｇと順に長くなるように形成
する。サブリーフバルブ１１３の外周縁１１３Ａは、上
記環座１１９の外周縁１１９Ａよりも大きく且つリーフ
バルブ１１４の外径１１４Ａよりも小さく設定されてい
る。The ring seat 119 and the sub-leaf valve 11
As shown in FIG. 2 (D), the distance Rd from the axis Z of the inner diameter to the outer peripheral edges 119A and 113A is opposite to the upper opening window 115D having the largest opening area. Is shorter, and as the opening area of the upper opening window becomes smaller in the order of 115E>115F> 115G, it is formed to be longer in the order of Re <Rf <Rg. The outer peripheral edge 113A of the sub-leaf valve 113 is set larger than the outer peripheral edge 119A of the ring seat 119 and smaller than the outer diameter 114A of the leaf valve 114.
【００５３】要求される減衰力によっては、図２（Ｂ）
に示すように、逆止弁ＣＶ側のリーフバルブ１１４に重
畳されるサブリーフバルブ１１３を省略してもよいし、
サブリーフバルブ１１３又はリーフバルブ１１４を複数
枚重畳して使用してもよい。同様に図３（Ｃ）に示すよ
うに、伸側減衰弁ＰＶ側のリーフバルブ１１６に重畳さ
れるサブリーフバルブ１１７，１１８のいずれか１方又
は両方ともに省略してもよいし、リーフバルブ１１６又
はサブリーフバルブ１１７，１１８を複数枚重畳して使
用してもよい。Depending on the required damping force, FIG.
, The sub-leaf valve 113 superimposed on the leaf valve 114 on the check valve CV side may be omitted,
A plurality of sub-leaf valves 113 or leaf valves 114 may be used. Similarly, as shown in FIG. 3C, one or both of the sub-leaf valves 117 and 118 superimposed on the leaf valve 116 on the extension-side damping valve PV side may be omitted, or the leaf valve 116 may be omitted. Alternatively, a plurality of sub-leaf valves 117 and 118 may be used in superposition.
【００５４】シリンダ２１内を上部室Ａと下部室Ｂに区
画するバルブケース１１５には、図２（Ｃ）に示すよう
に、その上面側に開口面積が順に小さくなる複数の上側
開口窓１１５Ｄ〜１１５Ｇが設けられ、当該各上側開口
窓は外周ポート１１５Ａを介して下部室Ｂに連通すると
ともに、各上側開口窓の間に形成された凹部１１５Ｋ
は、図３（Ａ）に示すように、内周ポート１１５Ｂを介
して円環状の下側開口窓１１５Ｃに連通している。As shown in FIG. 2 (C), a plurality of upper opening windows 115D to 115c each having a smaller opening area on the upper surface side of the valve case 115 which divides the interior of the cylinder 21 into an upper chamber A and a lower chamber B. 115G are provided, each upper opening window communicates with the lower chamber B via the outer peripheral port 115A, and a concave portion 115K formed between each upper opening window.
3A, as shown in FIG. 3A, communicates with an annular lower opening window 115C via an inner peripheral port 115B.
【００５５】続いて、下側開口窓１１５Ｃに対向し外径
１１６Ａが内径と同芯のリーフバルブ１１６と当該リー
フバルブ１１６より外周縁１１７Ａ，１１８Ａが順に小
さくなるサブリーフバルブ１１７，１１８とからなる圧
側減衰弁ＢＶ，サブリーフバルブ１１８よりも小さく外
周縁１１９Ａが圧側減衰弁ＢＶの撓みの支持部となる環
座１１９を、ガイドの軸部１１１Ａの一部をＤ字状に切
除した平坦部１１１Ｂに、各部品の内径側の位置決め用
直線部Ｗを位置合わせして順次嵌挿する。更に、圧側減
衰弁ＢＶの最大撓みを規制するバルブストッパ１８を組
み付け、最後にナット１２０を軸部１１１Ａのねじ部に
螺着し、締付け工具により締結することによりベースバ
ルブが構成される。Subsequently, a leaf valve 116 facing the lower opening window 115C and having an outer diameter 116A concentric with the inner diameter, and sub-leaf valves 117 and 118 whose outer edges 117A and 118A become smaller in order than the leaf valve 116 are formed. A flat portion 111B in which a portion of a guide shaft portion 111A is cut out in a D-shape from a ring seat 119 which is smaller than the compression side damping valve BV and the sub-leaf valve 118 and whose outer peripheral edge 119A serves as a support portion for bending the compression side damping valve BV. Then, the positioning linear portion W on the inner diameter side of each component is aligned and sequentially inserted. Further, a valve stopper 18 for restricting the maximum deflection of the compression-side damping valve BV is assembled, and finally, a nut 120 is screwed to the threaded portion of the shaft portion 111A and fastened by a fastening tool, thereby forming a base valve.
【００５６】サブリーフバルブ１１３とリーフバルブ１
１４からなる吸込み弁ＤＶ、又は、リーフバルブ１１６
とサブリーフバルブ１１７，１１８からなる圧側減衰弁
ＢＶを背面から担持する環座１１９の外周縁１１９Ａ
は、上記各リーフバルブの外径よりも小さく、内径の軸
芯Ｚからその外周縁に至る距離が、開口面積の最も大き
い上側開口窓１１５Ｄに対向するＸ側が最短で、開口面
積が小さくなるに従って徐々に長くなるように位置合わ
せして重畳する。Sub-leaf valve 113 and leaf valve 1
14 or leaf valve 116
Rim 119A of a ring seat 119 that carries a pressure-side damping valve BV, which is composed of a sub-leaf valve 117 and a sub-leaf valve 118, from the back.
Is smaller than the outer diameter of each leaf valve, and the distance from the axis Z of the inner diameter to the outer peripheral edge is the shortest on the X side facing the upper opening window 115D having the largest opening area, and as the opening area becomes smaller. Positioning and superimposing are performed so as to be gradually longer.
【００５７】上記第１実施形態の吸込み弁ＤＶ側におい
ては、サブリーフバルブ１１３の外周縁が円形の場合に
ついて説明したが、図２（Ｅ）に示すベースバルブ側の
第２実施形態のように、サブリーフバルブ２１３に形成
した花弁状の各支持片２１３Ｄ，２１３Ｅ，２１３Ｆ，
２１３Ｇの基端部２１３Ｈから外周縁にかけての同心円
上で測った巾Ｗを、開口面積の最も大きい上側開口窓５
Ｄに対向するＸ側の２１３Ｄが最小で、開口面積が１５
Ｅ，１５Ｆ，１５Ｇと小さくなるに従って、２１３Ｅ，
２１３Ｆ，２１３Ｇと段階的に大きくなるように形成し
てもよい。サブリーフバルブ２１３の撓み剛性は、上記
各支持片の巾Ｗと板厚とによって調整することができ
る。Although the case where the outer peripheral edge of the sub-leaf valve 113 is circular on the suction valve DV side of the first embodiment has been described, as in the second embodiment on the base valve side shown in FIG. , Petal-shaped support pieces 213D, 213E, 213F formed on the sub-leaf valve 213,
The width W measured on a concentric circle from the base end 213H of the 213G to the outer peripheral edge is determined by the upper opening window 5 having the largest opening area.
213D on the X side facing D is the smallest and the opening area is 15
As E, 15F, and 15G become smaller, 213E,
213F and 213G may be formed so as to be gradually increased. The bending rigidity of the sub-leaf valve 213 can be adjusted by the width W and the plate thickness of each of the support pieces.
【００５８】また、図２（Ｆ）に示す第２実施形態の他
の実施例は、サブリーフバルブ３１３の内径の軸芯Ｚか
ら各支持片３１３Ｄ，３１３Ｅ，３１３Ｆ，３１３Ｇの
外周縁に至る距離Ｒを、開口面積の最も大きい上側開口
窓５Ｄに対向するＸ側の３１３Ｄが最小で、開口面積が
１５Ｅ，１５Ｆ，１５Ｇと小さくなるに従って、３１３
Ｅ，３１３Ｆ，３１３Ｇと段階的に大きくなるように形
成したものである。サブリーフバルブ３１３の撓み剛性
は、上記各支持片の距離Ｒと板厚とによって調整するこ
とができる。In another example of the second embodiment shown in FIG. 2F, the distance from the axis Z of the inner diameter of the sub-leaf valve 313 to the outer peripheral edges of the support pieces 313D, 313E, 313F, 313G is different. R is set to 313D as the X-side 313D facing the upper opening window 5D having the largest opening area becomes the smallest and the opening area becomes smaller as 15E, 15F, and 15G.
E, 313F, and 313G are formed so as to be gradually increased. The flexural rigidity of the sub-leaf valve 313 can be adjusted by the distance R and the plate thickness of each of the support pieces.
【００５９】上記サブリーフバルブ２１３，３１３とリ
ーフバルブ１１４の基端側を背面から担持する環座１１
９の外周縁１１９Ａは、上記各サブリーフバルブの基端
部２１３Ｈ（３１３Ｈ）よりも小さく、内径の軸芯Ｚか
らその外周縁に至る距離が、開口面積の最も大きい上側
開口窓５Ｄに対向するＸ側が最短で、開口面積が小さく
なるに従って徐々に長くなるように位置合わせして重畳
する。A ring seat 11 for supporting the base ends of the sub-leaf valves 213 and 313 and the leaf valve 114 from the back.
9 is smaller than the base end 213H (313H) of each of the above-mentioned sub-leaf valves, and the distance from the inner diameter axis Z to the outer peripheral edge thereof is opposed to the upper opening window 5D having the largest opening area. Positioning and superimposing are performed so that the X side is the shortest and gradually becomes longer as the opening area becomes smaller.
【００６０】この結果、吸込み弁ＤＶ又は圧側減衰弁Ｂ
Ｖの撓み剛性は、いずれの実施形態においても開口面積
の最も大きい上側開口窓１１５Ｄに対向するＸ側が最小
で、開口面積が小さくなるＹ側にかけて徐々に大きくな
る。As a result, the suction valve DV or the compression side damping valve B
In any of the embodiments, the flexural rigidity of V is minimum on the X side facing the upper opening window 115D having the largest opening area, and gradually increases toward the Y side where the opening area decreases.
【００６１】上記花弁状のサブリーフバルブ２１３及び
３１３は、図３（Ｂ）に示すリーフバルブ１１６に合せ
てサイズを小さくすれば、圧側減衰弁ＢＶ側にも使用す
ることができる。この場合は、所要の減衰力に合せてリ
ーフバルブ１１６を何枚か重ねて使用し、その下側にサ
イズを小さくした花弁状のサブリーフバルブと前記環座
１１９とを位置合わせして重畳する。作用及び効果は上
述した吸込み弁ＤＶ側と同様であるので、詳細な説明は
省略する。The petal-shaped sub-leaf valves 213 and 313 can be used also on the pressure-side damping valve BV side if the size is reduced in accordance with the leaf valve 116 shown in FIG. In this case, a plurality of leaf valves 116 are used one on top of another in accordance with the required damping force, and a petal-shaped sub-leaf valve having a reduced size and the ring seat 119 are aligned and superimposed below the leaf valves 116. . The operation and effect are the same as those of the above-described suction valve DV side, and thus detailed description is omitted.
【００６２】ここで、外周縁が内径の軸芯Ｚから偏芯し
ているピストン又はバルブケース側の環座１０９又は１
１９，逆止弁ＣＶ側のサブリーフバルブ１０３，２０
３，３０３、又は、吸込み弁ＤＶ側のサブリーフバルブ
１１３，２１３，３１３は、ピストン５又はバルブケー
ス１１５に対して周方向の位置合わせをして組み付ける
必要がある。Here, the annular seat 109 or 1 on the piston or valve case side whose outer peripheral edge is eccentric from the axis Z having the inner diameter.
19. Sub-leaf valve 103, 20 on check valve CV side
The sub-leaf valves 113, 213, and 313 on the suction valve DV side need to be assembled with the piston 5 or the valve case 115 in the circumferential direction.
【００６３】また、伸側減衰弁ＰＶ側の環座１０９とサ
ブリーフバルブ１０７，１０８、又は、圧側減衰弁ＢＶ
側の環座１１９とサブリーフバルブ１１７，１１８は、
相互に位置合わせして組み付ける必要がある。このた
め、上記各部品は内径側に位置決め用直線部Ｗを形成す
る必要があるが、これ以外の部品は外径が内径の軸芯Ｚ
と同心であり周方向の位置合わせが不要であるので、位
置決め用直線部Ｗを形成する必要はない。The ring seat 109 and the sub-leaf valves 107 and 108 on the extension side damping valve PV side, or the compression side damping valve BV
The side ring seat 119 and the sub leaf valves 117 and 118 are
They need to be aligned and assembled. For this reason, it is necessary for each of the above components to form a positioning linear portion W on the inner diameter side.
It is not necessary to form the positioning linear portion W because it is concentric with and does not need to be aligned in the circumferential direction.
【００６４】油圧緩衝器が伸長行程から収縮行程に切り
替わる際に、ピストン速度が小さくバルブケース１１５
の下側開口窓１１５Ｃと底部室Ｃ間の圧力差が小さい微
低速域においては、上述したように、圧側減衰弁ＢＶの
撓み剛性はＸ側が最小である。このため、ピストン５を
介して容積の拡大する上部室Ａに補充される分を除いた
下部室Ｂの圧油は、下部室Ｂに連通する下側開口窓１１
５Ｃから圧側減衰弁ＢＶのＸ側を小さい差圧で押し開い
て底部室Ｃに流出し、この際の通路抵抗により、ピスト
ン速度に対してリニアに立ち上がる低速域の圧側減衰力
を発生する。When the hydraulic shock absorber switches from the extension stroke to the contraction stroke, the piston speed is low and the valve case 115
As described above, the bending stiffness of the compression-side damping valve BV is minimum on the X side in a very low speed range where the pressure difference between the lower opening window 115C and the bottom chamber C is small. For this reason, the pressure oil in the lower chamber B excluding the amount replenished to the upper chamber A whose volume increases via the piston 5 is supplied to the lower opening window 11 communicating with the lower chamber B.
5C, the X side of the compression side damping valve BV is pushed open with a small differential pressure and flows out to the bottom chamber C. At this time, the passage resistance generates a compression side damping force in a low speed region rising linearly with respect to the piston speed.
【００６５】従来構造の圧側減衰弁は撓み剛性が全周に
亘り一様であるため、下側開口窓１５Ｃの外側シート部
から一気に開弁するのに対して、本発明の圧側減衰弁Ｂ
Ｖは撓み剛性が最小であるＸ側から徐々に開弁する。圧
側減衰弁の外側シート部に対する吸着力は、一気に開弁
するよりも徐々に開弁した方が小さいので、この点も開
弁圧力を低下させる要因となる。The compression damping valve of the conventional structure has a uniform bending rigidity over the entire circumference, so that it is opened at once from the outer seat portion of the lower opening window 15C, whereas the compression damping valve B of the present invention is opened.
V gradually opens from the X side where the flexural rigidity is minimum. The attraction force of the compression side damping valve to the outer seat portion is smaller when the valve is gradually opened than when it is opened all at once, and this point also causes a reduction in the valve opening pressure.
【００６６】ピストン速度が増大するのに伴い、内周ポ
ート１１５Ｂを介して下部室Ｂに連通するバルブケース
１１５の下側開口窓１１５Ｃと底部室Ｃ間の圧力差も大
きくなるので、圧側減衰弁ＢＶは、撓み剛性の小さいＸ
側から撓み剛性の大きいＹ側側にかけて徐々に且つ連続
的に押し開かれる。このため、ピストン速度の低速域か
ら中速域にかけて、ピストン速度に対してリニアに立ち
上がる減衰力特性を得ることができる。As the piston speed increases, the pressure difference between the lower opening window 115C and the bottom chamber C of the valve case 115 communicating with the lower chamber B via the inner peripheral port 115B also increases. BV is X having a small bending rigidity.
The opening is gradually and continuously pushed open from the side to the Y side having a large flexural rigidity. For this reason, it is possible to obtain a damping force characteristic that rises linearly with respect to the piston speed from a low speed range to a medium speed range of the piston speed.
【００６７】リーフバルブ１１６とサブリーフバルブ１
１７，１１８からなり、ピストン速度の中速域までの減
衰力を制御する圧側減衰弁ＢＶの撓み剛性と、中速域を
越える減衰力を制御する内周ポート１１５Ｂの通路面積
とを適当に選択することにより、所要の減衰力特性を得
ることができる。Leaf valve 116 and sub-leaf valve 1
The flexural rigidity of the compression-side damping valve BV for controlling the damping force of the piston speed up to the middle speed range and the passage area of the inner peripheral port 115B for controlling the damping force exceeding the middle speed range are appropriately selected. By doing so, required damping force characteristics can be obtained.
【００６８】この場合、上側開口窓に対向している逆止
弁ＣＶの撓み剛性は、開口面積の最も大きい上側開口窓
５Ｄに対向するＸ側が最小になっているので、油圧緩衝
器が収縮行程から伸長行程に切り替わる際に、下部室Ｂ
と上部室Ａ間の差圧の小さいピストン速度の微低速域に
おいては、ピストンの外周ポート５Ａを介して上側開口
窓５Ｄ〜５Ｇに連通している下部室Ｂの作動油は、ま
ず、開口面積の最も大きい上側開口窓５Ｄを小さい差圧
で押し開いて上部室Ａに補給される。In this case, the flexural rigidity of the check valve CV facing the upper opening window is minimum on the X side facing the upper opening window 5D having the largest opening area. When switching to the extension stroke from
In the very low speed range of the piston speed where the pressure difference between the upper chamber A and the upper chamber A is small, the hydraulic oil in the lower chamber B communicating with the upper opening windows 5D to 5G via the outer peripheral port 5A of the piston firstly has an opening area. Is opened with a small differential pressure to replenish the upper chamber A.
【００６９】ピストン速度の増大につれて、下部室Ｂと
上部室Ａ間の差圧が増加するので、開口面積の最も大き
い上側開口窓５Ｄから開口面積の小さい５Ｇにかけて順
々に押し開かれ、下部室Ｂの作動油が差圧の小さいピス
トン速度の微低速域からスムーズに上部室Ａに補充され
る。このように、下部室Ｂから小さい差圧で上部室Ａに
作動油が補充されるため、減衰力の不連続を発生しにく
く、減衰力の不連続に起因する異音の発生を防止するこ
とができる。As the piston speed increases, the pressure difference between the lower chamber B and the upper chamber A increases, so that the lower chamber B is sequentially pushed open from the upper opening window 5D having the largest opening area to 5G having the smaller opening area. The hydraulic oil B is smoothly replenished to the upper chamber A from a very low speed range of the piston speed where the differential pressure is small. As described above, since hydraulic oil is replenished to the upper chamber A with a small differential pressure from the lower chamber B, discontinuity of damping force is less likely to occur, and occurrence of abnormal noise due to discontinuity of damping force is prevented. Can be.
【００７０】同様に、バルブケース１１５の上側開口窓
に対向している吸込み弁ＤＶの撓み剛性は、開口面積の
最も大きい上側開口窓１１５Ｄに対向する部分が最小に
なっているので、油圧緩衝器が収縮行程から伸長行程に
切り替わる際に、底部室Ｃと下部室Ｂ間の差圧の小さい
ピストン速度の低速域においては、バルブケースの外周
ポート１１５Ａを介して開口面積が順に小さくなる上側
開口窓１１５Ｄ〜１１５Ｇに連通している底部室Ｃの作
動油は、まず、開口面積の最も大きい上側開口窓１１５
Ｄを小さい差圧で押し開いて下部室Ｂに補給される。Similarly, the bending rigidity of the suction valve DV facing the upper opening window of the valve case 115 is minimized at the portion facing the upper opening window 115D having the largest opening area. When the pressure is switched from the contraction stroke to the extension stroke, in the low-speed region of the piston speed where the pressure difference between the bottom chamber C and the lower chamber B is small, the opening area becomes smaller through the outer peripheral port 115A of the valve case. The hydraulic oil in the bottom chamber C communicating with 115D to 115G is first supplied to the upper opening window 115 having the largest opening area.
D is pushed open with a small differential pressure and supplied to the lower chamber B.
【００７１】ピストン速度の増大につれて、底部室Ｃと
下部室Ｂ間の差圧が増加するので、開口面積の最も大き
い上側開口窓１１５Ｄから開口面積の小さい１１５Ｇに
かけて順々に押し開かれ、底部室Ｃの作動油が差圧の小
さいピストン速度の微低速域からスムーズに下部室Ｂに
補充される。このように、底部室Ｃから小さい差圧で下
部室Ｂに作動油が補充されるため、減衰力の不連続を発
生しにくく、減衰力の不連続に起因する異音の発生を防
止することができる。As the piston speed increases, the pressure difference between the bottom chamber C and the lower chamber B increases, so that the lower chamber 115 is pushed and opened in order from the upper opening window 115D having the largest opening area to 115G having the smaller opening area. The hydraulic oil of C is smoothly replenished to the lower chamber B from a very low speed range of the piston speed where the differential pressure is small. As described above, since hydraulic oil is replenished to the lower chamber B with a small differential pressure from the bottom chamber C, discontinuity of damping force is hardly generated, and occurrence of abnormal noise due to discontinuity of damping force is prevented. Can be.
【００７２】[0072]
【発明の効果】以上詳述した通り本発明に係わるピスト
ンバルブとベースバルブは、いずれの実施形態において
も構造，作用，効果が類似しているので、まず、発明の
効果を収縮行程から伸長行程に切り替わる場合から説明
する。油圧緩衝器が収縮行程から伸長行程に切り替わる
際には、バルブケースの外周ポートを介して底部室に連
通する上側開口窓に対向している吸込み弁の撓み剛性
が、開口面積の最も大きい上側開口窓に対向する部分が
最小になっているので、底部室と下部室間の差圧の小さ
いピストン速度の微低速域においては、底部室の作動油
は、まず、開口面積の最も大きい上側開口窓を小さい差
圧で押し開いて下部室に補給される。As described above in detail, the piston valve and the base valve according to the present invention are similar in structure, operation and effect in any of the embodiments. The description will be made from the case of switching to. When the hydraulic shock absorber switches from the contraction stroke to the extension stroke, the flexural rigidity of the suction valve facing the upper opening window communicating with the bottom chamber through the outer peripheral port of the valve case has the upper opening having the largest opening area. Since the portion facing the window is minimized, in the very low piston speed region where the differential pressure between the bottom chamber and the lower chamber is small, the hydraulic oil in the bottom chamber first flows into the upper open window with the largest open area. Is pushed open with a small differential pressure to replenish the lower chamber.
【００７３】ピストン速度の増大につれて、底部室と下
部室間の差圧が増加するので、開口面積の最も大きい上
側開口窓から開口面積の小さい上側開口窓にかけて順々
に押し開かれ、底部室の作動油が差圧の小さいピストン
速度の微低速域からスムーズに下部室に補充される。こ
のため減衰力の不連続を発生しにくく、減衰力の不連続
に起因する異音の発生を防止することができる。As the piston speed increases, the pressure difference between the bottom chamber and the lower chamber increases, so that the upper chamber is gradually pushed open from the upper opening window having the largest opening area to the upper opening window having the smaller opening area. Hydraulic oil is smoothly replenished into the lower chamber from a very low piston speed range where the differential pressure is small. For this reason, discontinuity of the damping force is not easily generated, and generation of abnormal noise due to the discontinuity of the damping force can be prevented.
【００７４】同様に、油圧緩衝器が伸長行程から収縮行
程に切り替わる場合には、ピストンの外周ポートを介し
て下部室に連通する上側開口窓に対向している逆止弁の
撓み剛性が、開口面積の最も大きい上側開口窓に対向す
る部分が最小になっているので、下部室と上部室間の差
圧の小さいピストン速度の低速域においては、下部室の
作動油は、まず、開口面積の最も大きい上側開口窓を小
さい差圧で押し開いて上部室に補給される。Similarly, when the hydraulic shock absorber switches from the extension stroke to the contraction stroke, the deflection rigidity of the check valve opposed to the upper opening window communicating with the lower chamber through the outer peripheral port of the piston increases the opening rigidity. Since the portion facing the upper opening window with the largest area is minimized, in the low-speed range of the piston speed where the pressure difference between the lower chamber and the upper chamber is small, the hydraulic oil in the lower chamber firstly The largest upper opening window is pushed open with a small differential pressure to supply the upper chamber.
【００７５】ピストン速度の増大につれて、下部室と上
部室間の差圧が増加するので、開口面積の最も大きい上
側開口窓から開口面積の小さい上側開口窓にかけて順々
に押し開かれ、下部室の作動油が差圧の小さいピストン
速度の微低速域からスムーズに上部室に補充される。こ
のため減衰力の不連続を発生しにくく、減衰力の不連続
に起因する異音の発生を防止することができる。As the piston speed increases, the pressure difference between the lower chamber and the upper chamber increases, so that the lower chamber is sequentially pushed open from the upper opening window having the largest opening area to the upper opening window having the smaller opening area. Hydraulic oil is smoothly replenished into the upper chamber from a very low piston speed range where the differential pressure is small. For this reason, discontinuity of the damping force is not easily generated, and generation of abnormal noise due to the discontinuity of the damping force can be prevented.
【図１】（Ａ）本発明の第１実施形態に係わる油圧緩衝
器の要部断面図である。 （Ｂ）ピストンロッドのインロー部（ガイドの軸部）の
断面図である。FIG. 1A is a sectional view of a main part of a hydraulic shock absorber according to a first embodiment of the present invention. (B) It is sectional drawing of the spigot part (shaft part of a guide) of a piston rod.
【図２】（Ａ）本発明のピストンバルブ側（ベースバル
ブ側）の第１実施形態に係わる逆止弁（吸込み弁）を重
畳した平面図である。 （Ｂ）上記第１実施形態の他の実施例に係わる逆止弁
（吸込み弁）を重畳した平面図である。 （Ｃ）ピストン（バルブケース）の上面図である。 （Ｄ）上記第１実施形態に係わるサブリーフバルブの軸
芯から外周縁に至る距離の変化を示す説明図である。 （Ｅ）本発明のピストンバルブ側（ベースバルブ側）の
第２実施形態に係わる逆止弁（吸込み弁）を重畳した平
面図である。 （Ｆ）上記第２実施形態の他の実施例に係わる逆止弁
（吸込み弁）を重畳した平面図である。FIG. 2A is a plan view in which a check valve (suction valve) according to the first embodiment of the present invention on the piston valve side (base valve side) of the present invention is superimposed. (B) It is a top view on which the check valve (suction valve) concerning other examples of the 1st embodiment was superimposed. (C) It is a top view of a piston (valve case). (D) It is explanatory drawing which shows the change of the distance from the axis of the sub-leaf valve which concerns on the said 1st Embodiment to an outer periphery. (E) is a plan view in which a check valve (suction valve) according to a second embodiment on the piston valve side (base valve side) of the present invention is superimposed. (F) It is the top view which superimposed the check valve (suction valve) concerning other examples of the above-mentioned 2nd embodiment.
【図３】（Ａ）ピストン（バルブケース）の下面図であ
る。 （Ｂ）本発明のピストンバルブ側（ベースバルブ側）の
第１実施形態に係わる伸側減衰弁（圧側減衰弁）を重畳
した平面図である。 （Ｃ）上記第１実施形態の他の実施例に係わる伸側減衰
弁（圧側減衰弁）を重畳した平面図である。FIG. 3A is a bottom view of a piston (valve case). (B) It is a top view on which the extension side damping valve (compression side damping valve) concerning a 1st embodiment of the piston valve side (base valve side) of the present invention was superimposed. (C) It is a top view which superimposed the extension side damping valve (compression side damping valve) concerning other examples of the above-mentioned 1st embodiment.
【図４】従来技術に係る油圧緩衝器の縦断面図である。FIG. 4 is a longitudinal sectional view of a hydraulic shock absorber according to the related art.
Ａ 上部室 Ｂ 下部室 Ｃ 底部室 Ｄ タンク室 ＢＶ 圧側減衰弁 ＣＶ 逆止弁 ＤＶ 吸込み弁 ＰＶ 伸側減衰弁 Ｒ 軸芯から各支持片の外周縁に至る距離 Ｗ 各支持片の巾 Ｚ 軸芯 ２１ シリンダ １０１ ピストンロッド １０３，２０３，３０３ サブリーフバルブ（逆止弁
側） １１３，２１３，３１３ サブリーフバルブ（吸込み弁
側） １０３Ａ，１１３Ａ サブリーフバルブの外周縁（逆止
弁側，吸込み弁側） １０４，１１４ リーフバルブ（逆止弁側，吸込み弁
側） １０６，１１６ リーフバルブ（伸側減衰弁側，圧側減
衰弁側） １０７，１０８ サブリーフバルブ（伸側減衰弁側） １０７Ａ，１０８Ａ サブリーフバルブの外周縁（伸側
減衰弁側） １０９，１１９ 環座（ピストン側，バルブケース側） １０９Ａ，１１９Ａ 環座の外周縁（ピストン側，バル
ブケース側） １１５ バルブケース １１７，１１８ サブリーフバルブ（圧側減衰弁側） １１７Ａ，１１８Ａ サブリーフバルブの外周縁（圧側
減衰弁側） ２０３Ｄ〜２０３Ｇ，３０３Ｄ〜３０３Ｇ 支持片（逆
止弁側） ２１３Ｄ〜２１３Ｇ，３１３Ｄ〜３１３Ｇ 支持片（吸
込み弁側）A Upper chamber B Lower chamber C Bottom chamber D Tank chamber BV Compression side damping valve CV Check valve DV Suction valve PV Extension side damping valve R Distance from shaft center to outer periphery of each support piece W Width of each support piece Z axis core 21 Cylinder 101 Piston rod 103, 203, 303 Sub-leaf valve (check valve side) 113, 213, 313 Sub-leaf valve (suction valve side) 103A, 113A Outer edge of sub-leaf valve (check valve side, suction valve side) ) 104,114 Leaf valve (check valve side, suction valve side) 106,116 Leaf valve (extension damping valve side, compression damping valve side) 107,108 Sub leaf valve (extension damping valve side) 107A, 108A Sub Outer edge of leaf valve (extension damping valve side) 109,119 Ring seat (piston side, valve case side) 109A, 119A Outer edge of ring seat (piston Side, valve case side 115 Valve case 117, 118 Sub-leaf valve (compression side damping valve side) 117A, 118A Outer edge of sub-leaf valve (compression side damping valve side) 203D-203G, 303D-303G Supporting piece (check valve side) ) 213D to 213G, 313D to 313G Supporting piece (suction valve side)
Claims (3)
トン又はバルブケースからなる隔壁部材を設け、隔壁部
材には二つの油室を連通するポートと、このポートの出
口側開口窓を開閉する逆止弁と伸側減衰弁又は吸込み弁
と圧側減衰弁とを設けている油圧緩衝器において、隔壁
部材の上面側に開口面積が異なる複数の上側開口窓を設
け、逆止弁又は吸込み弁を、各上側開口窓に対向するリ
ーフバルブと、リーフバルブの背面に重ねたリーフバル
ブより小径のサブリーフバルブと、サブリーフバルブの
背面に重ねたサブリーフバルブより小径の環座とで構成
し、上記サブリーフバルブと環座とは中央の取付孔を偏
芯させることにより円周方向に沿って剛性を変化させ、
開口面積の大きい上側開口窓から開口面積の小さい上側
開口窓に対応して、それぞれ剛性の小さい部位から剛性
の大きい部位を位置合わせしながらサブリーフバルブと
環座とを配置したことを特徴とする油圧緩衝器のバルブ
構造。1. A partition member comprising a piston or a valve case for partitioning two oil chambers in a cylinder, wherein a port connecting the two oil chambers and an outlet opening window of the port are opened and closed. In a hydraulic shock absorber provided with a check valve and an extension damping valve or a suction valve and a compression damping valve, a plurality of upper opening windows having different opening areas are provided on the upper surface side of the partition member, and the check valve or the suction valve is provided. A leaf valve facing each upper opening window, a sub-leaf valve smaller in diameter than the leaf valve stacked on the back of the leaf valve, and a ring seat smaller in diameter than the sub-leaf valve stacked on the back of the sub-leaf valve, The sub-leaf valve and the ring seat change the rigidity along the circumferential direction by eccentricizing the center mounting hole,
The sub-leaf valve and the ring seat are arranged in such a manner that, from the upper opening window having the larger opening area to the upper opening window having the smaller opening area, the parts having the lower rigidity are aligned with the parts having the higher rigidity. Hydraulic shock absorber valve structure.
トン又はバルブケースからなる隔壁部材を設け、隔壁部
材には二つの油室を連通するポートと、このポートの出
口側開口窓を開閉する逆止弁と伸側減衰弁又は吸込み弁
と圧側減衰弁とを設けている油圧緩衝器において、隔壁
部材の上面側に開口面積が異なる複数の上側開口窓を設
け、逆止弁又は吸込み弁を、各上側開口窓に対向するリ
ーフバルブと、リーフバルブの背面に重ねられ各上側開
口窓に対応する花弁状の支持片を備えたサブリーフバル
ブと、サブリーフバルブの背面に重ねたサブリーフバル
ブより小径の環座とで構成し、上記サブリーフバルブ
は、各支持片の巾と板厚、或いは軸芯から各支持片の外
周縁に至る距離を変えることにより各支持片の剛性を変
化させるとともに、環座は中央の取付孔を偏芯させるこ
とにより円周方向に沿って剛性を変化させ、開口面積の
大きい上側開口窓から開口面積の小さい上側開口窓に対
応して、それぞれ剛性の小さい部位から剛性の大きい部
位を位置合わせしながらサブリーフバルブと環座とを配
置したことを特徴とする油圧緩衝器のバルブ構造。2. A partition member comprising a piston or a valve case for partitioning two oil chambers in a cylinder, wherein a port connecting the two oil chambers and an outlet opening window of the port are opened and closed. In a hydraulic shock absorber provided with a check valve and an extension damping valve or a suction valve and a compression damping valve, a plurality of upper opening windows having different opening areas are provided on the upper surface side of the partition member, and the check valve or the suction valve is provided. , A leaf valve facing each upper opening window, a sub-leaf valve having petal-shaped support pieces overlapped on the back surface of the leaf valve and corresponding to each upper opening window, and a sub-leaf valve stacked on the back surface of the sub-leaf valve The sub-leaf valve is configured with a smaller diameter ring seat, and the rigidity of each support piece is changed by changing the width and thickness of each support piece or the distance from the axis to the outer peripheral edge of each support piece. With the ring The seat changes its stiffness along the circumferential direction by eccentricizing the center mounting hole.From the upper opening window with a larger opening area to the upper opening window with a smaller opening area, the rigidity starts from the part with the lower rigidity. The valve structure of the hydraulic shock absorber, wherein the sub-leaf valve and the ring seat are arranged while aligning a large portion of the hydraulic shock absorber.
トン又はバルブケースからなる隔壁部材を設け、隔壁部
材には二つの油室を連通するポートと、このポートの出
口側開口窓を開閉する逆止弁と伸側減衰弁又は吸込み弁
と圧側減衰弁とを設けている油圧緩衝器において、隔壁
部材の下面側に下側開口窓を設け、伸側減衰弁又は圧側
減衰弁を、各下側開口窓に対向するリーフバルブと、リ
ーフバルブの背面に重ねたリーフバルブより小径のサブ
リーフバルブと、サブリーフバルブの背面に重ねたサブ
リーフバルブより小径の環座とで構成し、上記サブリー
フバルブと環座とは中央の取付孔を偏芯させることによ
り円周方向に沿って剛性を変化させ、それぞれ剛性の小
さい部位から剛性の大きい部位を位置合わせしながらサ
ブリーフバルブと環座とを配置したことを特徴とする油
圧緩衝器のバルブ構造。3. A partition member comprising a piston or a valve case for partitioning two oil chambers in a cylinder, wherein a port connecting the two oil chambers and an outlet opening window of the port are opened and closed. In a hydraulic shock absorber provided with a check valve and an extension damping valve or a suction valve and a compression damping valve, a lower opening window is provided on the lower surface side of the partition member, and the extension damping valve or the compression damping valve is connected to each lower side. A leaf valve opposed to the side opening window, a sub-leaf valve smaller in diameter than the leaf valve stacked on the back of the leaf valve, and a ring seat smaller in diameter than the sub-leaf valve stacked on the back of the sub-leaf valve. The leaf valve and the ring seat change the rigidity along the circumferential direction by eccentricizing the center mounting hole, and align the sub-leaf valve with the A valve structure for a hydraulic shock absorber, wherein a seat and a seat are arranged.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001016543A JP4564675B2 (en) | 2000-11-30 | 2001-01-25 | Hydraulic shock absorber valve structure |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000-363918 | 2000-11-30 | ||
| JP2000363918 | 2000-11-30 | ||
| JP2001016543A JP4564675B2 (en) | 2000-11-30 | 2001-01-25 | Hydraulic shock absorber valve structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2002227903A true JP2002227903A (en) | 2002-08-14 |
| JP4564675B2 JP4564675B2 (en) | 2010-10-20 |
Family
ID=26604875
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001016543A Expired - Fee Related JP4564675B2 (en) | 2000-11-30 | 2001-01-25 | Hydraulic shock absorber valve structure |
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| Country | Link |
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| JP (1) | JP4564675B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007071234A (en) * | 2005-09-05 | 2007-03-22 | Kayaba Ind Co Ltd | Valve structure |
| JP2007071236A (en) * | 2005-09-05 | 2007-03-22 | Kayaba Ind Co Ltd | Valve structure |
| JP2011058562A (en) * | 2009-09-10 | 2011-03-24 | Kyb Co Ltd | Valve structure |
| DE102010040458A1 (en) * | 2010-09-09 | 2012-03-15 | Zf Friedrichshafen Ag | Damping valve for a vibration damper |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03163234A (en) * | 1989-11-20 | 1991-07-15 | Kayaba Ind Co Ltd | Valve device for hydraulic damper |
| JPH09144798A (en) * | 1995-11-21 | 1997-06-03 | Showa:Kk | Valve structure of buffer |
| JPH10196703A (en) * | 1997-01-16 | 1998-07-31 | Kayaba Ind Co Ltd | Valve structure for hydraulic buffer |
-
2001
- 2001-01-25 JP JP2001016543A patent/JP4564675B2/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03163234A (en) * | 1989-11-20 | 1991-07-15 | Kayaba Ind Co Ltd | Valve device for hydraulic damper |
| JPH09144798A (en) * | 1995-11-21 | 1997-06-03 | Showa:Kk | Valve structure of buffer |
| JPH10196703A (en) * | 1997-01-16 | 1998-07-31 | Kayaba Ind Co Ltd | Valve structure for hydraulic buffer |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007071234A (en) * | 2005-09-05 | 2007-03-22 | Kayaba Ind Co Ltd | Valve structure |
| JP2007071236A (en) * | 2005-09-05 | 2007-03-22 | Kayaba Ind Co Ltd | Valve structure |
| JP2011058562A (en) * | 2009-09-10 | 2011-03-24 | Kyb Co Ltd | Valve structure |
| DE102010040458A1 (en) * | 2010-09-09 | 2012-03-15 | Zf Friedrichshafen Ag | Damping valve for a vibration damper |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4564675B2 (en) | 2010-10-20 |
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