JPS5850132Y2 - hydraulic shock absorber - Google Patents
hydraulic shock absorberInfo
- Publication number
- JPS5850132Y2 JPS5850132Y2 JP1975166581U JP16658175U JPS5850132Y2 JP S5850132 Y2 JPS5850132 Y2 JP S5850132Y2 JP 1975166581 U JP1975166581 U JP 1975166581U JP 16658175 U JP16658175 U JP 16658175U JP S5850132 Y2 JPS5850132 Y2 JP S5850132Y2
- Authority
- JP
- Japan
- Prior art keywords
- damping force
- pressure
- piston
- shock absorber
- force generating
- 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
- Fluid-Damping Devices (AREA)
Description
【考案の詳細な説明】
本考案は、油圧緩衝器特にオートバイや自動車などの車
輪懸架部分に用いられる油圧緩衝器の改良に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to improvements in hydraulic shock absorbers, particularly hydraulic shock absorbers used in wheel suspension parts of motorcycles, automobiles, and the like.
一般に、この種の油圧緩衝器は、シリンダ内に対して摺
動自在に挿入したピストンの部分、またはシリンダの下
端とその外周に設けた作動油溜室との間に配設したベー
スバルブの部分にオリフィスやリーフバルブなどからな
る減衰力発生機構を装着し、前記ピストンとシリンダと
の相対運動に伴いこれら減衰力発生機構を通る作動油の
流れに抵抗を与え、これを利用して衝撃緩和および制振
作用を行なうようにしている。Generally, this type of hydraulic shock absorber is a part of a piston that is slidably inserted into a cylinder, or a part of a base valve that is installed between the lower end of the cylinder and a hydraulic oil reservoir provided on its outer periphery. A damping force generating mechanism consisting of an orifice, a leaf valve, etc. is attached to the cylinder, and as the piston and cylinder move relative to each other, resistance is applied to the flow of hydraulic oil through the damping force generating mechanism, and this is used to reduce shock and It is designed to have a damping effect.
しかしこの場合、従来から用いられている油圧緩衝器に
あってはそれぞれの部分に単一の減衰力発生機構を設け
ているだけであるため、ピストンとシリンダとの相対運
動時に圧縮側となる作動室内の高圧作動油がこれら減衰
力発生機構を通して直ちに膨張側の低圧作動室内に流入
し、このとき高圧作動油中に含まれている気泡が膨張側
の低圧作動室に流入した瞬間に急激に拡大することから
これが原因になって衝撃的な振動を生じ、この振動がピ
ストンロッドやシリンダを通して外部にスイツシュ音と
して聞え、運転者に不快感や不安感を与えることになる
。However, in this case, conventionally used hydraulic shock absorbers only have a single damping force generation mechanism for each part, so when the piston and cylinder move relative to each other, the compression side The high-pressure hydraulic oil in the room immediately flows into the low-pressure working chamber on the expansion side through these damping force generation mechanisms, and at this time, the bubbles contained in the high-pressure hydraulic oil rapidly expand as soon as they flow into the low-pressure working chamber on the expansion side. This causes shocking vibrations, which can be heard externally as a swishing sound through the piston rod and cylinder, giving the driver a sense of discomfort and anxiety.
そして、上記気泡はピストン前後における圧力変化（圧
力差）が急激であればある程発生し易いものである。The bubbles are more likely to occur as the pressure change (pressure difference) before and after the piston becomes more rapid.
したがって、本考案の目的は、このようなスイツシュ音
の発生を簡単な構造によって除去することのできる改良
された減衰力発生機構を備えたこの種の油圧緩衝器を提
供することである。Therefore, an object of the present invention is to provide a hydraulic shock absorber of this type that is equipped with an improved damping force generating mechanism that can eliminate the occurrence of such swiss noise with a simple structure.
以下、本考案の実施側を添附図面にもとづいて説明する
に、この種の油圧緩衝器における発生減衰力は、ピスト
ンとシリンダとの相対運動に伴う圧縮側および膨張側の
作動室間の圧力差にピストンの有効受圧面積を乗じた値
で与えられ、しかも前記スイツシュ音の発生が作動油中
に含まれる気泡の急激な拡大によって起ることから、本
考案にあっては、たとえば第１図Ａ実施例にみられる如
く、シリンダ１内に対して摺動自在に挿入したピストン
ロッド２を担うピストン３の部分に、間隔４を置いてリ
ーフバルブからなる減衰力発生機構５を２段にして直列
的に配設し、ピストン３の上向運動時において圧縮側と
なる作動室６内の高圧作動油を実線矢印で示す如く、ま
ず通路８から上部の減衰力発生機構５におけるリーフバ
ルブの外周を下方に撓ませて中間圧力間隔又は空間室４
に流し、次でこの間隔４から今度は下部の減衰力発生機
構５におけるリーフバルブの外周を同じく下方に撓ませ
てそのとき低圧になっている膨張側の作動室Ｔ内に流出
させ、このようにして、上下部二段の減衰力発生機構５
の部分の流動抵抗を適当に設計することにより作動室６
，７間の圧力差を従来のものと同様に保って同一の減衰
特性を発生させると共に、作動室６内の高圧作動油の圧
力を上部の減衰力発生機構５により間隔４のところで＝
具申間の圧力に下げ、これをさらに下部の減衰力発生機
構５によりもう一度下げてから作動室７側に流し、かく
して、作動室６内の高圧作動油の圧力降下を二段に亘っ
て行なうことにより、この高圧作動油中に含まれる気泡
を順次に拡大させてその急激な拡大を阻止し、それに伴
うスイツシュ音の発生を防止するようにしたのである。The implementation side of the present invention will be explained below based on the attached drawings. The damping force generated in this type of hydraulic shock absorber is caused by the pressure difference between the working chambers on the compression side and the expansion side due to the relative movement between the piston and the cylinder. is multiplied by the effective pressure-receiving area of the piston, and since the swiss noise is caused by the rapid expansion of air bubbles contained in the hydraulic oil, in the present invention, for example, As seen in the embodiment, a damping force generating mechanism 5 consisting of a leaf valve is arranged in two stages in series at a distance 4 from the piston 3 that supports the piston rod 2 which is slidably inserted into the cylinder 1. The high-pressure hydraulic oil in the working chamber 6, which is placed on the compression side when the piston 3 moves upward, is first drawn from the passage 8 to the outer periphery of the leaf valve in the upper damping force generation mechanism 5, as shown by the solid arrow. Deflect downward to create an intermediate pressure interval or space chamber 4
Next, from this interval 4, the outer periphery of the leaf valve in the lower damping force generation mechanism 5 is similarly bent downward, and the flow is caused to flow into the working chamber T on the expansion side, which is at a low pressure at that time. The upper and lower two stages of damping force generation mechanism 5
By appropriately designing the flow resistance of the working chamber 6
, 7 to generate the same damping characteristics as in the conventional one, and at the same time, the pressure of the high-pressure hydraulic oil in the working chamber 6 is controlled at the interval 4 by the upper damping force generating mechanism 5.
The pressure of the high-pressure hydraulic oil in the working chamber 6 is reduced in two stages by lowering the pressure to the same level as that of the hydraulic fluid in the working chamber 7, and then lowering it again by the damping force generating mechanism 5 in the lower part, and then flowing it to the working chamber 7 side. As a result, the air bubbles contained in the high-pressure hydraulic oil are sequentially expanded to prevent their rapid expansion, thereby preventing the swishing noise that accompanies this.
更に、減衰力発生機構５に関しその発生圧力（減衰力）
に対する撓み剛性を考えるとき、個々のバルブは作動室
６側圧力と中間圧力の差及び中間圧力と作動室１側圧力
の差としてのみ考慮すればよいので、単一のバルブで両
作動室６，７間の圧力差に耐えることを考える場合に比
べて許容応力的に非常に楽になり、またこのことより更
に換言するならば、個々のバルブの許容応力を従来可能
であった単一バルブの許容応力と等しいものとした場合
には、複合減衰力発生バルブとしてはより大きなピスト
ン前後の総和的圧力差に耐えられるもの、即ち、発生減
衰力を非常に大きく設計することができるものである。Furthermore, regarding the damping force generation mechanism 5, the generated pressure (damping force)
When considering the bending stiffness for each valve, it is only necessary to consider the difference between the pressure on the working chamber 6 side and the intermediate pressure, and the difference between the intermediate pressure and the pressure on the working chamber 1 side. In other words, the allowable stress of individual valves can be reduced to the allowable stress of a single valve, which was previously possible. If the stress is equal to the stress, the composite damping force generating valve can withstand a larger total pressure difference before and after the piston, that is, it can be designed to generate a very large damping force.
また、この実施例の場合、逆にピストン３の下向運動時
にあっては、そのとき圧縮側となる作動室γ内の作動油
が点線矢印で示す如く、まず下部の減衰力発生機構５に
設けたチェックバルブ９を押開いて殆んど抵抗なく間隔
４に入り、次でここから通路１１を通って上方のチェッ
クバルブ１０を押開きつつ同じく殆んど抵抗を受けるこ
となく膨張側の作動室６内に流入し、したがって、この
場合において作動油中の気泡の急激な拡大が起らないの
は従来のものと同様である。In addition, in the case of this embodiment, when the piston 3 moves downward, the hydraulic fluid in the working chamber γ, which is on the compression side, first flows into the lower damping force generating mechanism 5, as shown by the dotted arrow. The provided check valve 9 is pushed open to enter interval 4 with almost no resistance, and then from here through the passage 11, the upper check valve 10 is pushed open and the expansion side is operated with almost no resistance. The air bubbles flow into the chamber 6, and therefore, in this case, the bubbles in the hydraulic oil do not rapidly expand, as in the conventional case.
なお、これまでは、第１図Ａに示す実施例のものについ
てのみ説明してきたが、第１図Ｂから第１図Ｆに示すも
のは単なるその変形例であり、また、第２図Ａと第２図
Ｂは上記減衰力発生機構５を多段（この例では４段）に
設け、これらでさらに高圧作動中に含まれる気泡の拡大
を細かく順次に行なわせるようにしたものであり、さら
に第３図Ａから第３図Ｃに示すものは本考案をベースバ
ルブ１２に施した場合の実施例を示すものであって、こ
れらの作用・効果は、上記した第１図Ａの実施例の説明
から当業者であれば容易に理解できることであるので、
ここではピストン３の作動時における作動油の流れのみ
を同様に実線と点線の矢印で示すだけにとどめ、その詳
細な説明は省略することにする。Up to now, only the embodiment shown in FIG. 1A has been described, but the embodiments shown in FIGS. 1B to 1F are merely variations thereof, and FIG. FIG. 2B shows a structure in which the damping force generating mechanism 5 is provided in multiple stages (four stages in this example), and these are used to finely and sequentially expand the bubbles contained during high-pressure operation. 3A to 3C show embodiments in which the present invention is applied to the base valve 12, and their functions and effects are similar to the explanation of the embodiment shown in FIG. 1A above. As this is easily understood by those skilled in the art,
Here, only the flow of hydraulic oil during operation of the piston 3 will be similarly shown by solid lines and dotted arrows, and detailed explanation thereof will be omitted.
以上のように、本考案のものは、ピストン３またはベー
スバルブ１２に間隔４を置いて減衰力発生機構５を直列
的に複数段設けてやるという簡単な改良を施してやるだ
けで、従来運転者に木快感や不安感を与えていたスイツ
シュ音を確実に除去することができると共に、個々の減
衰力発生機構における発生応力を小さくできて応力的に
有利であり、また同一許容応力条件の下では複合弁とし
て個々の弁の圧力差の総和として非常に大きな減衰力値
を得ることができるものとすることが可能である。As described above, the present invention can be achieved by simply making an improvement in that multiple stages of damping force generating mechanisms 5 are installed in series at intervals of 4 on the piston 3 or the base valve 12, thereby improving the performance of the conventional driver. It is possible to reliably eliminate the swiss sound that gives a feeling of pleasure and anxiety, and it is advantageous in terms of stress because the stress generated in each damping force generation mechanism can be reduced, and under the same allowable stress conditions As a composite valve, it is possible to obtain a very large damping force value as the sum of the pressure differences of the individual valves.
第１図は、本考案を油圧緩衝器のピストン部分に施した
場合のそれぞれの実施例を示す要部の縦断正面図、第２
図は、同じく他の実施例をそれぞれ示す要部の縦断正面
図、第３図は、本考案をベースバルブの部分に施した場
合のそれぞれの実施例を示す要部の縦断正面図である。
１〜シリンダ、３・・・ピストン、４〜間隔、５〜減衰
力発生機構、１２〜ベースバルブ。Fig. 1 is a longitudinal sectional front view of the main part showing each embodiment when the present invention is applied to the piston part of a hydraulic shock absorber;
The figures are longitudinal sectional front views of essential parts showing other embodiments, and FIG. 3 is a longitudinal sectional front view of essential parts showing respective embodiments in which the present invention is applied to the base valve portion. 1-cylinder, 3-piston, 4-interval, 5-damping force generation mechanism, 12-base valve.
Claims (1)
隔を置いて減衰力発生機構を直列的に複数段配設すると
共にこれ等減衰力発生機構相互の間に、前記ピストン又
はベースバルブ前後に発生する圧力差に基因する中間圧
力が発生される様にした油圧緩衝器。A plurality of damping force generating mechanisms are arranged in series at intervals in the oil passage of the piston or base valve in the shock absorber, and between these damping force generating mechanisms, the damping force generating mechanism is generated before and behind the piston or base valve. A hydraulic shock absorber that generates intermediate pressure due to pressure difference.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1975166581U JPS5850132Y2 (en) | 1975-12-10 | 1975-12-10 | hydraulic shock absorber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1975166581U JPS5850132Y2 (en) | 1975-12-10 | 1975-12-10 | hydraulic shock absorber |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5279487U JPS5279487U (en) | 1977-06-14 |
| JPS5850132Y2 true JPS5850132Y2 (en) | 1983-11-15 |
Family
ID=28645244
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1975166581U Expired JPS5850132Y2 (en) | 1975-12-10 | 1975-12-10 | hydraulic shock absorber |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5850132Y2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014125974A1 (en) * | 2013-02-15 | 2014-08-21 | カヤバ工業株式会社 | Solenoid valve |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5962706A (en) * | 1982-09-29 | 1984-04-10 | Showa Mfg Co Ltd | Adjustment device for damping force of oil pressure buffer |
| JP2517796Y2 (en) * | 1989-03-09 | 1996-11-20 | 株式会社 ユニシアジェックス | Hydraulic shock absorber |
| JP2537802Y2 (en) * | 1989-06-06 | 1997-06-04 | 株式会社ユニシアジェックス | Variable damping force hydraulic pressure relief device |
| JP2533356Y2 (en) * | 1989-07-13 | 1997-04-23 | 株式会社ショーワ | Shock absorber valve mechanism |
| KR101276867B1 (en) * | 2009-06-30 | 2013-06-18 | 주식회사 만도 | Piston valve assembly of shock absorber |
-
1975
- 1975-12-10 JP JP1975166581U patent/JPS5850132Y2/en not_active Expired
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014125974A1 (en) * | 2013-02-15 | 2014-08-21 | カヤバ工業株式会社 | Solenoid valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5279487U (en) | 1977-06-14 |
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