JPS5923666Y2 - hydraulic shock absorber - Google Patents
hydraulic shock absorberInfo
- Publication number
- JPS5923666Y2 JPS5923666Y2 JP1978010468U JP1046878U JPS5923666Y2 JP S5923666 Y2 JPS5923666 Y2 JP S5923666Y2 JP 1978010468 U JP1978010468 U JP 1978010468U JP 1046878 U JP1046878 U JP 1046878U JP S5923666 Y2 JPS5923666 Y2 JP S5923666Y2
- Authority
- JP
- Japan
- Prior art keywords
- poppet
- valve
- oil
- oil chamber
- type valve
- 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
Landscapes
- Axle Suspensions And Sidecars For Cycles (AREA)
- Fluid-Damping Devices (AREA)
Description
【考案の詳細な説明】
本考案は二輪車および四輪車等に装着する油圧緩衝器に
関し、更に詳しくは圧縮行程に於て比例型の減衰力が発
生できるようにした二輪車等の油圧緩衝器における減衰
力発生装置に関する。[Detailed description of the invention] The present invention relates to a hydraulic shock absorber installed on two-wheeled vehicles, four-wheeled vehicles, etc., and more specifically, a hydraulic shock absorber for two-wheeled vehicles that can generate a proportional damping force during the compression stroke. This invention relates to a damping force generator.
例えば、二輪車用フロントフォーク又はリャクッション
ユニッＩ−として構成した油圧緩衝器では圧縮工程時の
減衰力を発生させるにはシリンダチューブにオリフィス
を穿設し、このオリフィスを通過する作動油に抵抗を与
えることにより行なっているが、圧縮ストロークのスピ
ードが早くなってくるとオリフィスの入口と出口の圧力
差が大きくなり、二乗特性の減衰力とはならず、この為
フロントフォーク等が棒状体になりがちで乗心地が非常
に悪いという欠点がある。For example, in a hydraulic shock absorber configured as a front fork or rear cushion unit for a motorcycle, an orifice is bored in the cylinder tube to generate damping force during the compression process, and this provides resistance to the hydraulic oil passing through the orifice. However, as the speed of the compression stroke increases, the pressure difference between the entrance and exit of the orifice increases, and the damping force does not have a square law characteristic, so the front fork etc. tend to become rod-shaped. The drawback is that the ride comfort is very poor.
この為圧縮行程のストロークに応じてピストンスピード
が上昇しても作動油の流れがこれに追随できるような比
例式の減衰力を得られるようにするには、オリフィスと
バルブの組合せによって減衰力を効がせるようにすれば
よいことになる。Therefore, in order to obtain a proportional damping force that allows the flow of hydraulic oil to follow even if the piston speed increases according to the stroke of the compression stroke, the damping force can be increased by a combination of an orifice and a valve. All you have to do is make it work.
しかし油圧緩衝器はその使用状態に於て、種々の周波数
成分を含む加振力が作用し一般に高周波域、例えば２０
Ｈ２以上の振動に対しては緩衝器の減衰力は大きく発
生しない方が車の乗心地面がら考えて良好である事が広
く知られているが、上記のようにバルブを組込むとこの
バルブに加振力が作用してしまうおそれが゛ある。However, when a hydraulic shock absorber is in use, excitation forces containing various frequency components act on it, and it generally operates in a high frequency range, e.g.
It is widely known that for vibrations of H2 or higher, it is better if the shock absorber does not generate a large damping force, considering the riding surface of the car. However, when a valve is installed as described above, There is a risk that an excitation force may be applied.
従って本考案の目的はポペット型のバルブのオーバライ
ド特性を利用して減衰力を発生させるようにしたもので
、そのためにポペット型弁の背面の密閉型背部油室を形
成すると共にポペット型弁の頂部に絞りオリフィスを設
け、ポペット型弁の動的安定性をこのオリフィスと背部
油室とによるダツシュボード効果を利用すると同時に油
圧緩衝器に入るピストン運動速度の高周波成分に対しポ
ペット型弁自体のオリフィスによるダンパー効果によっ
てポペット型弁の応答性を鈍くする事により緩衝器の圧
縮側減衰力の高周波成分に対する発生を低下することに
より車輌の乗心地を計った油圧緩衝器を提供することで
ある。Therefore, the purpose of the present invention is to generate a damping force by utilizing the override characteristics of a poppet-type valve.For this purpose, a sealed back oil chamber is formed on the back of the poppet-type valve, and the top of the poppet-type valve is A throttle orifice is provided at the top of the valve, and the dynamic stability of the poppet type valve is improved by utilizing the dash board effect created by this orifice and the back oil chamber.At the same time, the orifice of the poppet type valve itself provides a damper against the high frequency component of the piston movement speed that enters the hydraulic shock absorber. It is an object of the present invention to provide a hydraulic shock absorber which improves the ride comfort of a vehicle by reducing the responsiveness of a poppet type valve and thereby reducing the generation of compression side damping force of the shock absorber for high frequency components.
以下本考案の実施の一態様を図面について説明する。An embodiment of the present invention will be described below with reference to the drawings.
アウターチューブ１内にピストン２を介してインナーチ
ューブ３を摺動自在に挿入され、ピストン２はインナー
チューブ３の上端に設けてその外周がアウターチューブ
１の内周を摺接し、又、アウターチューブ１の下端に設
けた軸受９内周をインナーチューブ３が貫通してその外
周が摺接するようになっている。An inner tube 3 is slidably inserted into the outer tube 1 via a piston 2, and the piston 2 is provided at the upper end of the inner tube 3 so that its outer circumference slides against the inner circumference of the outer tube 1. The inner tube 3 passes through the inner periphery of a bearing 9 provided at the lower end of the bearing 9, and its outer periphery comes into sliding contact.
そしてこれらアウターチューブ１、軸受９およびピスト
ン２、インナーチューブ３によってアウターチューブ１
およびインナーチューブ３内に亘って形成されたピスト
ン作動室たる油室４，１６と分離した油室５が構成され
ている。The outer tube 1, the bearing 9, the piston 2, and the inner tube 3 are connected to the outer tube 1.
Further, an oil chamber 5 is configured, which is separated from oil chambers 4 and 16, which are piston operating chambers, formed across the inner tube 3.
前記油室４，１６と油室５は、インナーチューブ３に穿
った通路８とピストン２に設けた通路６およびバルブ７
を介し連絡している。The oil chambers 4 and 16 and the oil chamber 5 are connected to a passage 8 bored in the inner tube 3, a passage 6 provided in the piston 2, and a valve 7.
We are in contact via.
前記バルブ７はオリフィスが形成され、油圧緩衝器の伸
長行程で油室５から油室４，１６への油流れに抵抗を与
えて減衰力を発生するもので圧縮行程に於て抵抗なく開
口して油室４，１６、油室５へと油を導くチェック機能
を含む構造を有する。The valve 7 has an orifice formed therein and generates a damping force by providing resistance to the flow of oil from the oil chamber 5 to the oil chambers 4 and 16 during the extension stroke of the hydraulic shock absorber, and opens without resistance during the compression stroke. It has a structure including a check function that guides oil to the oil chambers 4, 16 and 5.
軸受９の内側にはダストシール１０とバッキング１１が
取り付けられて油室５内へのダストの侵入と、油室５か
らの油の漏れをそれぞれ防止している。A dust seal 10 and a backing 11 are attached to the inside of the bearing 9 to prevent dust from entering the oil chamber 5 and oil from leaking from the oil chamber 5, respectively.
アウターチューブ１の上部にはこのアウターチューブ１
より径が大きく横方向に膨出したタンク１２が連結され
、このタンク１２の上端中央にはブラケット１３を介し
て取り付はアイ１４が設けられ、このアイ１４は車体側
に連結されるようになっている。At the top of outer tube 1 is this outer tube 1.
A tank 12 which has a larger diameter and bulges laterally is connected, and an eye 14 is provided at the center of the upper end of this tank 12 via a bracket 13, and this eye 14 is connected to the vehicle body side. It has become.
又インナーチューブ３の下端には取り付はアイ１５が設
けられ、このアイ１５は車輪側に取り付けられるように
してフロントフォークもしくはリヤークッションユニッ
トとして使用される。Further, an eye 15 is provided at the lower end of the inner tube 3, and this eye 15 is used as a front fork or a rear cushion unit by being attached to the wheel side.
アウターチューブ１の上端内側には隔壁部材１７が取り
付けられてアウターチューブ１内の油室４とタンク１２
内のりザーバ油室１８を分離している。A partition member 17 is attached to the inner side of the upper end of the outer tube 1 to separate the oil chamber 4 and the tank 12 inside the outer tube 1.
The inner reservoir oil chamber 18 is separated.
タンク１２に於てリザーバ油室１８の上方にはエアー室
を形成し、このエアー室にはタンク１２に直結させたエ
アーバルブ２０から所定のエアーを封入するようになっ
ている。An air chamber is formed above the reservoir oil chamber 18 in the tank 12, and a predetermined amount of air is sealed into this air chamber from an air valve 20 directly connected to the tank 12.
エアー室内のエアーとリザーバ油室１８内の油は直接接
触しているが、緩衝器の伸縮作動時にリザーバ油室１８
の油面ば上下に変化する。The air in the air chamber and the oil in the reservoir oil chamber 18 are in direct contact, but when the shock absorber expands and contracts, the reservoir oil chamber 18
The oil level changes up and down.
従ってこの油面の高さは常にタンク１２内に位置し隔壁
部材１７より下方にはこないようにあらかじめ設定され
ている。Therefore, the height of this oil level is set in advance so that it is always located within the tank 12 and does not go below the partition wall member 17.
隔壁部材１７には上下の油室４，１８を通じさせる通路
２１と下方に垂設した隔壁たるパイプ３０を取り付け、
このパイプ３０には内部にリザーバ油室１８と通じる通
路３１を設け、この通路３１の下端には後述する本考案
のバルブ装置３２を設けて圧縮行程に於ける比例特性の
減衰力を発生させ、通路２１の下端には伸長行程で開口
してリザーバ油室１８から油室４へ油を導き、又圧縮行
程では減衰力を発生させるオリフィスを形成したチェッ
ク弁２３が配設される。A passage 21 for communicating the upper and lower oil chambers 4 and 18 and a pipe 30 serving as a partition wall hanging downward are attached to the partition wall member 17.
This pipe 30 is provided with a passage 31 communicating with the reservoir oil chamber 18 inside, and a valve device 32 of the present invention, which will be described later, is provided at the lower end of this passage 31 to generate a proportional damping force in the compression stroke. A check valve 23 is disposed at the lower end of the passage 21 and has an orifice that opens during the extension stroke to guide oil from the reservoir oil chamber 18 to the oil chamber 4 and generates a damping force during the compression stroke.
パイプ３０の上部口端には邪魔板３４を設け、通路２１
からの油の吹き上げを防止し、エアーレーションの発生
をふせいている。A baffle plate 34 is provided at the upper end of the pipe 30, and the passage 21
This prevents oil from blowing up and prevents aeration from occurring.
隔壁部材１７下端とインナ−チューブ３下端間には隔壁
部材１７をばね受けとしてコイル径の小さい上部スプリ
ング２４とコイル径の大きい下部スプリング２５が介在
され、これらのコイルスプリング２４．２５とタンク１
２内のエアー室のガス圧で懸架ばね特性を出すようにな
っている。An upper spring 24 with a small coil diameter and a lower spring 25 with a large coil diameter are interposed between the lower end of the partition member 17 and the lower end of the inner tube 3, using the partition member 17 as a spring receiver.
Suspension spring characteristics are created by the gas pressure in the air chamber inside 2.
上下コイルスプリング２４．２５はコイル径に差を持た
させることの他にコイルの中央からの直径は同じくしそ
の線径を異なるようにしたものも使用できるものである
。The upper and lower coil springs 24 and 25 may have different coil diameters, or may have the same diameter from the center but different wire diameters.
上側のコイルスプリング２４はパイプ３０の外周に案内
されて上下に伸縮でき、又下側のコイルスプリング２５
はその外周が伸縮時にインナーチューブ３の内周に案内
され、又最大伸長時でもその上端はインナーチューブ３
の通路８の目端より下方に位置して通路８の油の流出入
を隋書しないようになっている。The upper coil spring 24 is guided by the outer circumference of the pipe 30 and can expand and contract up and down, and the lower coil spring 25
Its outer periphery is guided by the inner periphery of the inner tube 3 when it expands and contracts, and its upper end is guided by the inner periphery of the inner tube 3 even when it is fully expanded.
It is located below the end of the passage 8 to prevent oil from flowing in and out of the passage 8.
上方のコイルスプリング２４においてもそのコイル径も
しくは線径が小さいことからその外周とオリフィス８の
目端との間に間隙が形成されることによって通路８の目
端を封じるのが防止されている。Since the coil diameter or wire diameter of the upper coil spring 24 is small, a gap is formed between its outer periphery and the end of the orifice 8, thereby preventing the end of the passage 8 from being closed.
上下二つのコイルスプリング２４．２５は直接直列に当
接してもよく、又は図示のように上側のコイルスプリン
グ２４と下側のコイルスプリング２５間に継手２７を介
在させ、この継手２７をスプリング受けとしてそれぞれ
使用してもよい、継手２７を使用する場合には、この継
手２７の外径を小さくし、継手２７とインナーチューブ
３間に空間を形成し、この空間によりオリフィス８に油
が自由に流出入できるようにされている。The two upper and lower coil springs 24 and 25 may contact each other directly in series, or, as shown in the figure, a joint 27 may be interposed between the upper coil spring 24 and the lower coil spring 25, and this joint 27 may be used as a spring receiver. If a joint 27 is used, the outer diameter of the joint 27 is made small to form a space between the joint 27 and the inner tube 3, and this space allows oil to flow freely into the orifice 8. It is possible to enter.
又継手２７には半径方向に切欠き２９を形成し、この切
欠き２９を介して油室４と１６が自由に連通ずるように
なっている。Further, a cutout 29 is formed in the joint 27 in the radial direction so that the oil chambers 4 and 16 can freely communicate with each other through the cutout 29.
次にバルブ装置３２の構造について述べる。Next, the structure of the valve device 32 will be described.
パイプ３０の下端３５をかしめてその内側に断面Ｕ字状
のガイド３６を嵌合して閉塞端面を形成させ、このガイ
ド３６内には断面や・Ｕ字状の減衰力発生用ポペット型
弁３７を摺動自在に挿入させ、このポペット型弁３７の
背面とガイド３６上面との間には密閉型背部油室４２を
形成し、この油室４２内にはスプリング３８を介装して
ポペット型弁３７を常時上方に押し上げている。The lower end 35 of the pipe 30 is caulked and a guide 36 having a U-shaped cross section is fitted inside it to form a closed end surface, and within this guide 36 is a poppet valve 37 with a U-shaped cross section for generating damping force. A sealed back oil chamber 42 is formed between the back surface of the poppet type valve 37 and the upper surface of the guide 36, and a spring 38 is interposed in this oil chamber 42 to form a poppet type valve. The valve 37 is constantly pushed upward.
ガイド３６はわざ′わさ゛バイツブ３０にかしめ固定す
ることなくパイプ３０の下端を密封してポペット型弁３
７の案内とスプリング受けと兼用させてもよい。The guide 36 seals the lower end of the pipe 30 without caulking it to the bite tube 30 and closes the poppet valve 3.
It may be used both as a guide and a spring receiver.
パイプ３０には室４と３１を通しさせる孔３９を穿ち、
又パイプ３０の内側にはこの孔３９より上方に位置させ
た弁座４０を圧入させ、ポペット型弁３７がスプリング
３８で押し上げられた中立時にはこのポペット型弁３７
の上面が弁座４０に当接し孔３９と通路３１の連通を遮
断させている。A hole 39 is bored in the pipe 30 to allow the chambers 4 and 31 to pass through.
Also, a valve seat 40 positioned above this hole 39 is press-fitted inside the pipe 30, and when the poppet type valve 37 is pushed up by a spring 38 and is in the neutral state, this poppet type valve 37
The upper surface of the valve seat 40 contacts the valve seat 40 and blocks communication between the hole 39 and the passage 31.
ポペット型弁３７の上面は図示のようにテーパ付の円錐
面になっているのか好ましいが、その他の形状でも使用
可能であり、又ポペット型弁３７自体かならずしも図示
の形状のもので゛ある必要はない。The upper surface of the poppet type valve 37 is preferably a tapered conical surface as shown in the figure, but other shapes can also be used, and the poppet type valve 37 itself does not necessarily have the shape shown in the figure. do not have.
ポペット型弁３７の頂部中央にはオリフィス４１が穿た
れて通路３１とポペット型弁３７の背部油室４２を通じ
させている。An orifice 41 is bored in the center of the top of the poppet valve 37 to communicate the passage 31 with a back oil chamber 42 of the poppet valve 37.
次に第１図、第２図の実施例における作動について述べ
る。Next, the operation in the embodiment shown in FIGS. 1 and 2 will be described.
アウターチューブ１が下降して圧縮すると油室４が縮少
しすると同時に油室５が拡大し、又油室４．１６の油の
一部はチェックバルブ２３のオリフィスからリザーバ油
室１８に流出して圧縮時の減衰力を発生させる。When the outer tube 1 is lowered and compressed, the oil chamber 4 contracts and at the same time the oil chamber 5 expands, and a portion of the oil in the oil chamber 4.16 flows out from the orifice of the check valve 23 to the reservoir oil chamber 18. Generates damping force during compression.
更に圧縮スピードが上昇すると油室４，１６の油は孔３
９よりポペット型弁３７の環状受圧面に作用してスプリ
ング３８に抗してポペット型弁３７を押し開かせて通路
３１及びタンク１２側のリザーバ油室１８に流出し、こ
の時ポペット型弁３７の作用によって圧側の比例形減衰
力が発生する。When the compression speed increases further, the oil in oil chambers 4 and 16 flows into hole 3.
9 acts on the annular pressure-receiving surface of the poppet-type valve 37 to push the poppet-type valve 37 open against the spring 38 and flows into the passage 31 and the reservoir oil chamber 18 on the tank 12 side, and at this time, the poppet-type valve 37 A proportional damping force on the compression side is generated by the action of .
又タンク１２に油が導かれた時リザーバ油室１８の油面
ばエアー室の内圧に抗して最大限の位置まで上昇する。Furthermore, when the oil is introduced into the tank 12, the oil level in the reservoir oil chamber 18 rises to the maximum position against the internal pressure of the air chamber.
又アウターチューブ１の伸長作動時には油室４が拡大し
、他の油室５が縮少し、油室５の油がバルブ７より通路
６、通路８を介して油室４，１６に流出して伸長行程で
の減衰力を発生する。Also, when the outer tube 1 is extended, the oil chamber 4 expands, the other oil chamber 5 contracts, and the oil in the oil chamber 5 flows out from the valve 7 through the passages 6 and 8 into the oil chambers 4 and 16. Generates damping force during the extension stroke.
又タンク側リザーバ油室１８の油は通路２１よりチェッ
ク弁２３を開口して油室４へ供給される。Also, the oil in the tank-side reservoir oil chamber 18 is supplied to the oil chamber 4 from the passage 21 by opening the check valve 23.
ところで上記圧縮行程に於て、油室４，１６の油が孔３
９よりポペット型弁３７を開かせて通路３１に流出する
際、ポペット型弁３７はスプリング３８に抗して圧縮し
、その背部油室４２の油がオリフィス４１より通路３１
に流出する。By the way, in the above compression stroke, the oil in the oil chambers 4 and 16 flows into the hole 3.
When the poppet type valve 37 is opened from 9 to flow out into the passage 31, the poppet type valve 37 is compressed against the spring 38, and the oil in the back oil chamber 42 flows from the orifice 41 into the passage 31.
leaks to.
この為オリフィス４１の作用でポペット型弁３７の動き
に応じたダンパー効果が発生し、このダンパー効果を利
用してポペット弁の動的安定性が得られる。Therefore, the action of the orifice 41 generates a damper effect according to the movement of the poppet valve 37, and by utilizing this damper effect, dynamic stability of the poppet valve can be obtained.
又油圧緩衝器に入る圧縮側速度の高周波成分に対し、こ
のオノフイス４１のダツシュボード効果が発生し、弁体
のチャタリングが防止され、このダツシュボード効果の
利用によりポペット型弁自体３７の応答性を鈍くするこ
とによって緩衝器の圧縮側減衰力の高周波成分に対する
発生を低下する事によって車輌の乗心地が向上するもの
である。In addition, the dash board effect of this onofice 41 occurs against the high frequency component of the compression side velocity entering the hydraulic shock absorber, preventing chattering of the valve body, and by utilizing this dash board effect, the responsiveness of the poppet type valve itself 37 is slowed down. This reduces the generation of compression-side damping force of the shock absorber with respect to high-frequency components, thereby improving the ride comfort of the vehicle.
尚第４図はＸ軸に加振周波数をＹ軸に振幅比をとった時
のポペット型弁の周波数特性を示し、グラフａは共振周
波数、グラフｂはオリフィスによるダンピング効果がな
い場合の周波数、グラフＣは本考案のオリフィス４１に
よってダンピング効果を付けた時の周波数特性でこれに
よって振幅が安定していることが分るものである。Figure 4 shows the frequency characteristics of the poppet valve with the excitation frequency on the X axis and the amplitude ratio on the Y axis, graph a is the resonance frequency, graph b is the frequency when there is no damping effect by the orifice, Graph C shows the frequency characteristics when a damping effect is applied by the orifice 41 of the present invention, and it can be seen that the amplitude is stabilized by this.
又第５図のグラフｄはオリフィスのない敏感なバルブを
使用した時の減衰力特性であるが、本考案のオリフィス
４１を設けた鈍感なバルブを使用した時の減衰力特性は
第６図の太線て′示すグラフｅとなりグラフｄに比べて
なだらかとなるものである。Graph d in Figure 5 shows the damping force characteristics when a sensitive valve without an orifice is used, but the damping force characteristics when using an insensitive valve with the orifice 41 of the present invention are as shown in Figure 6. Graph e is indicated by the thick line, and is more gradual than graph d.
次に第３図は本考案のバルブ装置を伸長工程時に作用さ
せるように使用した他の実施例に係る油圧緩衝器である
。Next, FIG. 3 shows a hydraulic shock absorber according to another embodiment in which the valve device of the present invention is used to operate during the extension process.
これはインナーチューブ４５内にピストン４６を介して
ピストンロッド４７が摺動自在に挿入され、ピストン４
６はインナーチューブ４５内に二つの油室４８．４９を
区画し、又インナーチューブ４５の外側にはアウターチ
ューブ５０を同芯に設け、その間にはタンク５１が区画
され、このタンク５１はオリフィス５２を介してボトム
側油室４８と通じさせている。A piston rod 47 is slidably inserted into the inner tube 45 via a piston 46, and the piston 47 is slidably inserted into the inner tube 45 via a piston 46.
6 partitions two oil chambers 48 and 49 in the inner tube 45, and an outer tube 50 is provided concentrically outside the inner tube 45, and a tank 51 is partitioned between them, and this tank 51 has an orifice 52. It communicates with the bottom side oil chamber 48 via.
ピストン４６は通路５３を穿ち、この通路５３の下側口
端にはオリフィスを設けたチェック弁５４を開閉自在に
配設している。The piston 46 bored a passage 53, and a check valve 54 provided with an orifice is disposed at the lower end of the passage 53 so as to be openable and closable.
ピストンロッド４７の先端には中空もしくは弁孔５５を
穿ち、この弁孔５５は油室４８に開口すると共にピスト
ンロッド４７の孔５６を介して下部油室４９と通じてい
る。A hollow or valve hole 55 is bored at the tip of the piston rod 47, and the valve hole 55 opens into the oil chamber 48 and communicates with the lower oil chamber 49 via a hole 56 in the piston rod 47.
弁孔５５内にはバルブ装置が設けられている。A valve device is provided within the valve hole 55.
即ち弁孔５５内には減衰力発生用のポペット型弁３７が
摺動自在に挿入され、このポペット型弁３７の頂部には
オリフィス４１が設けられ、又その上面にはテーパ付の
円錐面が形成され、又ポペット型弁３７は弁孔５５の壁
面とポペット型弁３７の下面との間に介装されたスプリ
ング３８で常時上方に押圧され、この時上記円錐面が弁
孔５５内にスナップリング５７で固定された弁座４０に
当接されている。That is, a poppet type valve 37 for generating a damping force is slidably inserted into the valve hole 55, and an orifice 41 is provided at the top of the poppet type valve 37, and a tapered conical surface is provided on the top surface of the orifice 41. The poppet-type valve 37 is always pressed upward by a spring 38 interposed between the wall surface of the valve hole 55 and the lower surface of the poppet-type valve 37, and at this time, the conical surface snaps into the valve hole 55. It is in contact with the valve seat 40 which is fixed with a ring 57.
上記弁孔５５に於て、ポペット型弁３７の下面側に区画
された弁孔５５の一部は密閉型背部油室として構成され
ている。In the valve hole 55, a part of the valve hole 55 defined on the lower surface side of the poppet type valve 37 is configured as a sealed back oil chamber.
上記の油圧緩衝器では圧縮行程では油室４９が拡大し、
油室４８が縮少し、油室４８の油はオリフィス５２より
タンク５１に戻され、この時オリフィス５２で減衰力が
発生し、又一部の油はチェック弁５４を押し開いて通路
５３より油室４９に流出する。In the above hydraulic shock absorber, the oil chamber 49 expands during the compression stroke,
The oil chamber 48 is contracted, and the oil in the oil chamber 48 is returned to the tank 51 through the orifice 52. At this time, a damping force is generated in the orifice 52, and some of the oil pushes open the check valve 54 and flows out from the passage 53. Flows into chamber 49.
又伸長行程では第３図に於てピストン４６が左行し油室
４９が縮少され、この時チェック弁５４のオリフィスで
減衰力が発生するが、伸長速度が早くなると孔５６より
ポペット型弁３７をスプリング３８に抗して押し開き弁
孔５５より油室４８に油が流出し、しかもポペット型弁
３７の作用で減衰力が得られる。Also, during the extension stroke, the piston 46 moves to the left as shown in FIG. 37 is pushed open against the spring 38, and oil flows out from the valve hole 55 into the oil chamber 48, and damping force is obtained by the action of the poppet type valve 37.
しかもこの時ポペット型弁３７の圧縮時に背部油室の油
がオリフィス４１より流出してダンピング効果を発生さ
せる。Moreover, at this time, when the poppet valve 37 is compressed, oil in the back oil chamber flows out from the orifice 41, producing a damping effect.
この為前記と同じくポペット弁の振動安定性が計れ、バ
ルブにより発生する高周波減衰力をフィルターする如く
安定的に作用するもので“ある。Therefore, as mentioned above, the vibration stability of the poppet valve can be measured, and it acts stably as if filtering the high frequency damping force generated by the valve.
第１図は本考案の一実施例に係る油圧緩衝器の一部切欠
き縦断側面図、第２図は第１図の一部拡大断面図、第３
図は他の実施例に係る油圧緩衝器の一部切欠き縦断側面
図、第４図はポペット弁の周波数特性を示すグラフ、第
５図はオリフィスのない敏感なバルブの減衰力特性を示
すグラフ、第６図は本考案のポペット弁による減衰力特
性を示すグラフである。
４、３１．４８．４９・・・・・・油室、３７・・・・
・・ポペット型弁、３８・・・・・・スプリング、４０
・・・・・・弁座、４１・・・・・・オリフィス、４２
・・・・・・背部油室。FIG. 1 is a partially cutaway vertical side view of a hydraulic shock absorber according to an embodiment of the present invention, FIG. 2 is a partially enlarged sectional view of FIG. 1, and FIG.
The figure is a partially cutaway vertical side view of a hydraulic shock absorber according to another embodiment, Figure 4 is a graph showing the frequency characteristics of a poppet valve, and Figure 5 is a graph showing the damping force characteristics of a sensitive valve without an orifice. , FIG. 6 is a graph showing the damping force characteristics of the poppet valve of the present invention. 4, 31.48.49...Oil chamber, 37...
...Poppet type valve, 38...Spring, 40
... Valve seat, 41 ... Orifice, 42
・・・・・・Back oil chamber.
Claims (5)
用のポペット型弁を摺動自在に挿入させ、このポペット
型弁は背面の密閉型背部油室内に設けたスプリングで常
時弁座に押し付けられており、又ポペット型弁の頂部に
はオリフィスを穿ち、このオリフィスはポペット型弁背
部油室と前記油室の一方とを通じさせるようにした油圧
緩衝器。(1) A poppet-type valve for generating damping force is slidably inserted in the middle of the passage connecting the two oil chambers, and this poppet-type valve is always held against the valve seat by a spring installed in the sealed back oil chamber. The hydraulic shock absorber is pressed and has an orifice in the top of the poppet type valve, and this orifice communicates the oil chamber at the back of the poppet type valve with one of the oil chambers.
登録請求の範囲第（１）項記載の油圧緩衝器。(2) The hydraulic shock absorber according to claim (1), in which the poppet valve is formed into a slightly U-shape.
実用新案登録請求の範囲第（２）項記載の油圧緩衝器。(3) The hydraulic shock absorber according to claim (2) of the utility model registration, wherein a tapered conical surface is formed on the upper surface of the poppet valve.
りサーバ室との間の隔壁に設けられ、この通路の途中に
挿入されたポペット型弁の頂部に穿ったオリフィスはポ
ペット型弁背部油室と前記油室の一方のリザーバ室を通
じさせるようにした実用新案登録請求の範囲第（１）項
記載の油圧緩衝器。(4) A passage that allows the two oil chambers to communicate is provided in the partition between the piston operating chamber and the server chamber, and an orifice bored at the top of the poppet-type valve inserted in the middle of this passage is located in the oil chamber at the back of the poppet-type valve. The hydraulic shock absorber according to claim 1, wherein the oil chamber and one reservoir chamber of the oil chamber communicate with each other.
設けられ、この通路の途中に挿入されたポペット型弁の
頂部に穿ったオリフィスはポペット型弁背部油室と前記
油室の一方の油室とを通じさせるようにした実用新案登
録請求の範囲第（１）項記載の油圧緩衝器。(5) A passage for communicating two oil chambers is provided in the piston rod, and an orifice bored at the top of the poppet-type valve inserted in the middle of this passage connects the oil chamber at the back of the poppet-type valve and the oil chamber of one of the oil chambers. A hydraulic shock absorber according to claim (1) of the utility model registration, which is adapted to communicate with the above.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1978010468U JPS5923666Y2 (en) | 1978-01-31 | 1978-01-31 | hydraulic shock absorber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1978010468U JPS5923666Y2 (en) | 1978-01-31 | 1978-01-31 | hydraulic shock absorber |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS54115060U JPS54115060U (en) | 1979-08-13 |
| JPS5923666Y2 true JPS5923666Y2 (en) | 1984-07-13 |
Family
ID=28823117
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1978010468U Expired JPS5923666Y2 (en) | 1978-01-31 | 1978-01-31 | hydraulic shock absorber |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5923666Y2 (en) |
-
1978
- 1978-01-31 JP JP1978010468U patent/JPS5923666Y2/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS54115060U (en) | 1979-08-13 |
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