JPS60179539A - Hydraulic damper - Google Patents
Hydraulic damperInfo
- Publication number
- JPS60179539A JPS60179539A JP3695584A JP3695584A JPS60179539A JP S60179539 A JPS60179539 A JP S60179539A JP 3695584 A JP3695584 A JP 3695584A JP 3695584 A JP3695584 A JP 3695584A JP S60179539 A JPS60179539 A JP S60179539A
- Authority
- JP
- Japan
- Prior art keywords
- seal
- chamber
- piston rod
- guide member
- piston
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/362—Combination of sealing and guide arrangements for piston rods
- F16F9/364—Combination of sealing and guide arrangements for piston rods of multi-tube dampers
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、自動車等に施用される液圧緩衝器忙関する。[Detailed description of the invention] Industrial applications The present invention relates to hydraulic shock absorbers used in automobiles and the like.
従来勾、術 −
一般に、この種の液圧緩衝器にあっては、第１図及び第
２図に示すように、内部に作動液が充填されたシリンダ
ｌと、このシリンダｌを囲繞して、該シリンダ１との間
に、封入気体による加圧下に所望量の作動液が充填され
たリザーバ室２を形成する有底筒状の外筒３と、この外
筒３の一端内部に固着された。下方に面する大径部７ａ
及びこれと同軸の小径部７ｂとからなる貫通孔７を具え
たシールリテーナ４と、このシールリテーナ４とゆシリ
ンダ１の一端１ａとの間に挟設された、上方に面する大
径部８ａ及びこれと同軸の小径部８ｂとからなる貫通孔
８會具えだガイド部材５と、このガイド部材５及びシー
ルリテーナ４の貫通孔７゜８を貫通してシリンダ１の内
部に延びる、摺動可能なピストンロッド６と、このピス
トンロッド６に弾接して、作動液等が外部に漏出するこ
とを阻止するメインリップ９ａと外部から泥水等が侵入
することを阻止するダストリップ９ｂとを内周部に有す
ると共に、外周部がシー・ルリテーナの大径部７ａ内に
圧入されたロッドシール部材９と、同じく、ピスト７０
ツド６の外周部に弾接される油された外周部がガイド部
材の大径部８ａ内に圧入され九油溜シール部材１０と、
一端がロッドシール部材９と油溜シール部材１０との間
に形成されたシール室１１に開口し、他端がリザーバ室
２に開口するように前記ガイド部材５０円周方向に複数
個穿設された還流通路１２と、前記シール室１１からリ
ザ−バ室２への作動液の（至）人は許容するも、逆に、
リザーバ室２からシール室１１への加圧気体の流入は阻
止する一方向弁１３と、前記シリンダｌ内部を上部液室
１４と下部液室１５との二基に隔成すべく前記ピストン
ロッド６に固着された、減衰力発生手段１６ヲ有するピ
スト／１７と全備え・ている。なお、前記リザーバ室２
と下部液室１５とは、シリンダｌの底５部のボトムボデ
ィ１８に設けた連通孔１９によジ連通されている。また
、ガイド部材５の、ピストンロッド６と面する＋部位に
は、該ピストンロッド隙
６の外周面との間に微小な間帰Ｃｋ Ｉ＋２いて筒状ブ
ツシュ２０が圧入固着されている。さらに、外筒３の端
部には、車軸側に取付けられる取付リング２１が固着さ
れている。Conventional technology - Generally, this type of hydraulic shock absorber has a cylinder l filled with hydraulic fluid inside and a cylinder l surrounding this cylinder l, as shown in Figures 1 and 2. , a bottomed cylindrical outer cylinder 3 which forms a reservoir chamber 2 filled with a desired amount of working fluid under pressure with sealed gas between the cylinder 1; Ta. Large diameter portion 7a facing downward
A seal retainer 4 equipped with a through hole 7 consisting of a small diameter part 7b coaxial with the seal retainer 4, and a large diameter part 8a facing upward, which is sandwiched between the seal retainer 4 and one end 1a of the cylinder 1. A guide member 5 having a through hole 8 formed of a small diameter portion 8b coaxial with the guide member 5, and a slidable member that extends into the inside of the cylinder 1 through the guide member 5 and the through hole 7°8 of the seal retainer 4. A main lip 9a that comes into elastic contact with the piston rod 6 to prevent hydraulic fluid from leaking to the outside, and a dust lip 9b that prevents muddy water and the like from entering from the outside are arranged on the inner circumference. and a rod seal member 9 whose outer periphery is press-fitted into the large diameter portion 7a of the seal retainer;
An oil sump sealing member 10 is formed by press-fitting an oiled outer peripheral part that comes into elastic contact with the outer peripheral part of the tube 6 into the large diameter part 8a of the guide member;
A plurality of holes are formed in the guide member 50 in the circumferential direction so that one end opens into the seal chamber 11 formed between the rod seal member 9 and the oil sump seal member 10, and the other end opens into the reservoir chamber 2. Although the reflux passage 12 and the flow of the working fluid from the seal chamber 11 to the reservoir chamber 2 are permitted, on the contrary,
A one-way valve 13 is provided to prevent pressurized gas from flowing into the seal chamber 11 from the reservoir chamber 2, and the piston rod 6 is provided to separate the inside of the cylinder l into two parts, an upper liquid chamber 14 and a lower liquid chamber 15. It is fully equipped with a piston/17 having a damping force generating means 16 fixed thereto. Note that the reservoir chamber 2
and the lower liquid chamber 15 are in communication with each other through a communication hole 19 provided in the bottom body 18 at the bottom 5 of the cylinder l. Further, a cylindrical bushing 20 is press-fitted into a portion of the guide member 5 facing the piston rod 6 with a minute recess Ck I+2 between the outer peripheral surface of the piston rod gap 6 and the outer peripheral surface of the piston rod gap 6. Further, an attachment ring 21 is fixed to the end of the outer cylinder 3 to be attached to the axle side.
このような構成の液圧緩衝器は、次のように作（１）
ピストンロッドの伸び行程の場合ピストンロッド６が上
昇すると、それに随動するピストン１７によって、上部
液室１４は高圧となシ、逆に、下部液室１５は低圧とな
る。このとき、上部液室１４内の高圧の作動液は、ピス
トン１７に備えられた減衰力発生（４構１６を植成する
貫通孔ＩＧ ＆を通シ、その出口端に設けたゾレートバ
ルブ１６ ｂを押し開いて、オリフイヌ全形成し、該オ
リアイスを高速で通過する際に静圧全動圧に変えて圧力
降下し、下部液室１５内に流れる。かくして、ピストン
１６は、上部液室１４と下部液室１５との圧力差によっ
て下方に付勢され、このとき伸び行程全阻止しようとす
る。伸び側減衰力を発生する。これと同時に、ピストン
ロンドロの一部がシリンダ１内から退出する際に生ずる
ピストンロッド退出体積分の作動液は、リザーバ室２か
ら、ボトムボディ１８の底部に設けだ連通孔１９ヲ通っ
て、下部液室１５内に補填される。一方、高圧の上部液
室Ｊ４内の作動液の一部は、ピストンロッド６と筒状ブ
ツシュ２０との間の隙間Ｃを高速で；＋ｆ１って、油溜
シール部材１０の内周部に形成された油溜リップ１．Ｏ
ａとピストンロッド６の外周面とで形成でれたシール下
室２２内に流入した後、前記油溜リップ１０ ａを押し
開いて、核油溜リップｔｏ ａ’を効果的に潤滑しつつ
、シール室１１に流入する。その後、作動液は、シール
室１１から、ガイド部材５に形成された還流通路１２ヲ
通シ、該還流通路１２のリザーバ室２内開口端に設けら
れた一方向弁１３を容易に押し開いてリザーバ室２に還
流される。この場合、油溜シール部材１０内に埋設され
た補強環２３の上端縁は、ロッドシール部材９の内周部
に形成されたメインリップ９ａの下端縁の高さよりも若
干の寸法１０分上方に突出して形成されているので、前
記シール室１１内に貯溜されている作動液中に、前記メ
インリップ９ａ及び油溜リップ［Ｏａは、常時、浸漬さ
れることとなシ、シたがって、ピストンロンドロの外周
面に充分な液膜を形成することができ、その外周面の損
６ケ効果的に防止できるとともに、加圧気体の緩衝器外
部への漏洩を効果的に防止することができる。A hydraulic shock absorber with such a configuration is constructed as follows (1).
In the case of the extension stroke of the piston rod, when the piston rod 6 rises, the upper liquid chamber 14 becomes high pressure due to the piston 17 moving therewith, and conversely, the lower liquid chamber 15 becomes low pressure. At this time, the high-pressure hydraulic fluid in the upper fluid chamber 14 passes through the damping force generating (4-shaft 16) provided in the piston 17 through the through hole IG&, and through the solate valve 16b provided at its outlet end. The piston 16 is pushed open to completely form the orifice, and as it passes through the orifice at high speed, the static pressure is converted into a total dynamic pressure and the pressure drops and flows into the lower liquid chamber 15.Thus, the piston 16 connects the upper liquid chamber 14 and the lower liquid chamber It is urged downward by the pressure difference with the liquid chamber 15, and at this time attempts to completely block the extension stroke.It generates an extension-side damping force.At the same time, when a part of the piston rondro exits from the cylinder 1. The hydraulic fluid corresponding to the volume of the piston rod withdrawn from the reservoir chamber 2 passes through the communication hole 19 provided at the bottom of the bottom body 18 and is replenished into the lower fluid chamber 15. On the other hand, the high pressure upper fluid chamber J4 A part of the hydraulic fluid in the oil sump lip 1.O formed on the inner circumference of the oil sump sealing member 10 passes through the gap C between the piston rod 6 and the cylindrical bushing 20 at high speed;
After flowing into the seal lower chamber 22 formed by the outer peripheral surface of the piston rod 6 and the oil sump lip 10a, the oil sump lip 10a is pushed open to effectively lubricate the core oil sump lip to a'. It flows into the seal chamber 11. Thereafter, the working fluid passes from the seal chamber 11 through the reflux passage 12 formed in the guide member 5, and easily pushes open the one-way valve 13 provided at the open end of the reflux passage 12 in the reservoir chamber 2. It is refluxed to the reservoir chamber 2. In this case, the upper edge of the reinforcing ring 23 embedded in the oil sump seal member 10 is slightly 10 minutes higher than the lower edge of the main lip 9a formed on the inner circumference of the rod seal member 9. Since they are formed in a protruding manner, the main lip 9a and the oil sump lip [Oa] are not always immersed in the hydraulic fluid stored in the seal chamber 11, so that the piston A sufficient liquid film can be formed on the outer circumferential surface of the Londro, effectively preventing damage to the outer circumferential surface, and also effectively preventing pressurized gas from leaking to the outside of the shock absorber. .
（２） ピストンロッド の圧行程の場合ピストンロッ
ド６が下降すると、それに随動するピストン１７によっ
て、下部液室１５は高圧とな９゜逆に、上部液室１４は
低圧となるため、下部液室１５内の作動液は、減衰力発
生機構１６をイ（′４成する其通孔１６ Ｑ ’に通シ
、その出口端に設けたプレートバルブ１６ ｄを押し開
いて、オリフィスを形成し、該オリフィスを高速で通過
する際に静圧を動圧に変えて圧力降下し、上部液室１４
内に流れる。かくして、下部液室１５と上部液室１４と
の圧力差によって、ピストンＪ７は、上方に付勢され、
このとき、圧行程全阻止しようとする、圧側減寂力を発
生する。一方、ピストンロッド６の一部がシリンダ１内
へ侵入する際に生ずるピストンロッド侵入体積分の作動
液は、下部液室１５から、ボトムボディ１８に設けた連
通孔１９に通って、リザーバ室２内に戻り、その内部に
所定圧をもって封入されている加圧気体を更に圧縮する
。(2) In the case of the pressure stroke of the piston rod, when the piston rod 6 descends, the lower liquid chamber 15 becomes high pressure due to the piston 17 that follows it. Conversely, the upper liquid chamber 14 becomes low pressure, so the lower liquid The hydraulic fluid in the chamber 15 is passed through the through hole 16 Q' formed by the damping force generating mechanism 16 (A'4), and the plate valve 16 D provided at the outlet end thereof is pushed open to form an orifice. When passing through the orifice at high speed, the static pressure is changed to dynamic pressure, the pressure drops, and the upper liquid chamber 14
flows within. Thus, due to the pressure difference between the lower liquid chamber 15 and the upper liquid chamber 14, the piston J7 is urged upward,
At this time, a compression-side depression force is generated that attempts to completely block the compression stroke. On the other hand, the hydraulic fluid corresponding to the piston rod intrusion volume generated when a part of the piston rod 6 intrudes into the cylinder 1 passes from the lower liquid chamber 15 to the communication hole 19 provided in the bottom body 18, and is transferred to the reservoir chamber 2. The pressurized gas sealed inside at a predetermined pressure is further compressed.
この場合、リザーバ室２内の加圧気体は、ガイド部材５
に対する一方向弁１３の密着作用によって閉塞されてい
るので、シール室ｌｌ内への加圧気体の流入は確実に防
止される。In this case, the pressurized gas in the reservoir chamber 2 is
Since the seal chamber 11 is closed by the one-way valve 13 in close contact with the seal chamber 11, the pressurized gas is reliably prevented from flowing into the seal chamber 11.
ところで、このような構成を有する液圧緩衝器にあって
は、伸び行程時に、上部液室１４内が高圧となυ、この
高圧の作動液の一部は、ピストンロンドロの外周面と筒
状ブンシュ２０の内周面との間に形成、された狭小の間
隙Ｃを高速で通過する際、高温となってシール下室２２
内に噴出し、更に、このシール下室２２から油溜リップ
１０ ａ ｆ押し広げて、ロッドシール部材９のメイン
リップ９ａに衝突するものであるから、前記作動液の熱
にょｐ１メインリンプｔＯａが劣化（硬化または軟化な
ど）することがらシ、そのため、ピストンロッド６の外
周面を損傷したシ、あるいはピストンロッド６に対する
リップ川ａによるシール性を低下させたシするなどの欠
点があった。By the way, in a hydraulic shock absorber having such a configuration, during the extension stroke, the inside of the upper liquid chamber 14 is at high pressure υ, and a part of this high-pressure hydraulic fluid flows between the outer circumferential surface of the piston rod and the cylinder. When passing through the narrow gap C formed between the inner circumferential surface of the shaped bund 20 at high speed, the temperature becomes high and the seal lower chamber 22
The oil sump lip 10a f is ejected from the lower seal chamber 22 and collides with the main lip 9a of the rod seal member 9, so that the heat of the hydraulic fluid p1 main limp tOa is It tends to deteriorate (harden or soften, etc.), and as a result, there are disadvantages such as damage to the outer circumferential surface of the piston rod 6 or deterioration of the sealing performance of the piston rod 6 by the lip a.
発明の目的
本発明は、このような従来の欠点に鑑みてなされたもの
であシ、ビヌトンロンドの外周面の損傷が未然に防止で
き、かつ、ピストンロッドに対ｆるロッドシール部材に
形成されたメインリップによるシール性の向上を図るこ
とができる液圧緩衝器全書ることを目的とする。OBJECTS OF THE INVENTION The present invention has been made in view of the above-mentioned drawbacks of the prior art.The present invention has been made to provide a rod seal member that can prevent damage to the outer circumferential surface of the piston rod, and that is formed on a rod seal member that faces the piston rod. The purpose of this paper is to write a complete list of hydraulic shock absorbers that can improve the sealing performance of the main lip.
発明の構成
本発明は、このような目的を達成するために、油溜シー
ル部材内に埋設された補強環と作動液の還流通路゛のシ
ール室側開口端との間に、ピストンロッドと略同軸に前
記補強環の上端縁の高さよシも低くない高さに突出する
上端縁を有する環状部を設けるとともに、前記補強環と
環状部との間に、シール室とシール下室とを連通ずる５
作動液のバイパス通路を形成している。Composition of the Invention In order to achieve such an object, the present invention provides a piston rod, which is generally referred to as a piston rod, between the reinforcing ring embedded in the oil sump seal member and the opening end of the working fluid return passage on the seal chamber side. An annular portion having an upper edge protruding to a height not lower than the height of the upper edge of the reinforcing ring is coaxially provided, and a sealing chamber and a lower sealing chamber are connected between the reinforcing ring and the annular portion. Communicating 5
It forms a bypass passage for the hydraulic fluid.
実施列
以下、本発明の実施例を図面に基づいて説明する。なお
、従来例と同一構成部分には、同一指示符号を付してそ
の重代する説明は省略する。Embodiments Examples of the present invention will be described below based on the drawings. Components that are the same as those of the conventional example are designated by the same reference numerals, and redundant explanation thereof will be omitted.
第３図は本発明に係る液圧緩衝器の一実施例を示す要部
断面図である。FIG. 3 is a sectional view of essential parts showing an embodiment of the hydraulic shock absorber according to the present invention.
第３図に示すように、油溜シール部材ＬＯ内に埋設され
た補強環２３と作動液の還流通路１２のシール室側開口
端１２ ａとの間には、ピストンロッド６と略同軸に前
記補強環２３の上端縁よシも寸法り７分だけ若干上方に
突出する上端Ｒ’ｅ有する環状部２４が設けられている
。なお、この環状部２４の上＠緑は、前記補強環２３の
上端縁と同じ高さに形成してもよい。この環状部２４は
、ガイド部材５の大径部８ａに圧入固定されている環状
部材２４ Ａから形成されている。また、この環状部材
２４ Ａと前記補強環２３との間には、ロッドシール部
材９と油溜シール部材ＩＯとの間に形成されたシール室
１１と、油溜シール部材ＩＯの内周部に形成された油溜
リップｔＯａとピストンロッド６の外周面とで形成され
たシール下室２２とを連通ずるバイパス通路２５が複数
個形成されている。このバイパス通路２５は、ピストン
ロッド６の伸び行程時において、ピストンロッド６の外
周面とガイド部材５（具体的には、筒状ブツシュ２０）
の内周面との間の狭小の間（Ｍ Ｃｋ通って、上部液室
１４からシール下室２２内に流入する高温の作動液が油
溜リングｔｏ ａ ｋ押し広げてメインリップ９ａに向
かって噴出しないようにするために設けられたものであ
る。As shown in FIG. 3, between the reinforcing ring 23 embedded in the oil sump seal member LO and the opening end 12a on the seal chamber side of the working fluid return passage 12, there is a space located approximately coaxially with the piston rod 6. The upper edge of the reinforcing ring 23 is also provided with an annular portion 24 having an upper end R'e that slightly protrudes upward by a dimension of 7. Note that the upper part of the annular portion 24 may be formed at the same height as the upper edge of the reinforcing ring 23. The annular portion 24 is formed from an annular member 24A press-fitted into the large diameter portion 8a of the guide member 5. Further, between this annular member 24A and the reinforcing ring 23, there is a seal chamber 11 formed between the rod seal member 9 and the oil sump seal member IO, and a seal chamber 11 formed in the inner peripheral part of the oil sump seal member IO. A plurality of bypass passages 25 are formed that communicate the formed oil sump lip tOa and the lower seal chamber 22 formed by the outer peripheral surface of the piston rod 6. This bypass passage 25 connects the outer peripheral surface of the piston rod 6 and the guide member 5 (specifically, the cylindrical bush 20) during the extension stroke of the piston rod 6.
The high-temperature working fluid flowing from the upper liquid chamber 14 into the lower seal chamber 22 through the narrow gap between the inner peripheral surface of the oil sump ring and the inner circumferential surface of the oil sump ring (MCk) spreads out toward the main lip 9a. This is to prevent it from spewing out.
このように、この実施［ＦＩＪにあっては、ピストンロ
ッド６の伸び行程時に、ピストンロッド６の外周面と筒
状プンシュ２０の内片面との間の狭小の間隙Ｃを通って
、上部液室１４からシール下室２２内に流入した作・動
液を、前記バイパス通路２５を介して、該バイパス通路
２５のシール室側開口端からシール室１１内にバイパス
通路させることができるので、前記間肚Ｃからシール下
室２２内に流入しても油溜リップｔｏ ａ を押し広げ
て噴出することはなく、メインリップ９ａが高温の噴流
によって劣化するの全防止できる。したがって、ピスト
ンロッド６の外周面が損傷したシ、あるいはピストンロ
ッド６との間のシール性が悪化したシするよりな事態を
未然に防止できる。また、環状部材２４Ａの上端縁は、
補強環２３の上端縁よシも寸法ち分だけ高く形成されて
いるので、バイパス通路２５から流出する作動液を直接
に還流通路Ｉ２内に還流させないで。As described above, in this implementation [FIJ, during the extension stroke of the piston rod 6, the upper liquid chamber passes through the narrow gap C between the outer peripheral surface of the piston rod 6 and one inner surface of the cylindrical punch 20. 14 into the lower seal chamber 22 can be passed through the bypass passage 25 into the seal chamber 11 from the opening end of the bypass passage 25 on the seal chamber side. Even if the oil flows into the lower seal chamber 22 from the abdomen C, the oil sump lip toa will not be spread out and ejected, and the main lip 9a can be completely prevented from deteriorating due to the high-temperature jet stream. Therefore, it is possible to prevent a situation in which the outer circumferential surface of the piston rod 6 is damaged or the sealing performance between the piston rod 6 and the piston rod 6 is deteriorated. Moreover, the upper edge of the annular member 24A is
Since the upper edge of the reinforcing ring 23 is also formed higher by the dimension, the working fluid flowing out from the bypass passage 25 is not directly refluxed into the reflux passage I2.
優先的にシール室１１内に流入させることができる。It can be made to flow into the seal chamber 11 preferentially.
したがって、シール室１１内を作動液で充満させること
ができるので、メインリップ９ａを、作動液で、常時浸
漬することができる。Therefore, the inside of the seal chamber 11 can be filled with the hydraulic fluid, so that the main lip 9a can be constantly immersed in the hydraulic fluid.
次に、第４図は本発明の他の実施例會示す要部断面図で
、前記実施例と異なる主な点は、環状部２４ Ｂがガイ
ド部材５と一体に形成芒れている点である。このように
構成した場合でも、前記間隙Ｃ全通ってシール下室２２
内に流入した作動液を、シール室ｌｌ内にバイパス通路
２５を介して流入させることができるｔ丘か、バイパス
通路２５からの作動液を直接に還流通路１２内に還流さ
せることなく、シール室ｌｌ内に流入させることができ
る。Next, FIG. 4 is a sectional view of a main part showing another embodiment of the present invention, and the main difference from the above embodiment is that the annular portion 24B is formed integrally with the guide member 5. . Even with this configuration, the seal lower chamber 22 passes through the entire gap C.
The hydraulic fluid that has flowed into the seal chamber 11 can be made to flow into the seal chamber 11 through the bypass passage 25, or the hydraulic fluid from the bypass passage 25 can be directly recirculated into the reflux passage 12 without flowing back into the seal chamber 11. It can be made to flow into the ll.
なお、第４図中一点鎖線で示すように、ガイド部材５０
大径部８８に、一端がシール室１１に開口し、他端がシ
ール下室２２に開口するようにバイパス通路２５を設け
ても、前記各実施列の場合と同様な作用効果がイリられ
る。In addition, as shown by the dashed line in FIG. 4, the guide member 50
Even if the bypass passage 25 is provided in the large diameter portion 88 so that one end opens into the seal chamber 11 and the other end opens into the lower seal chamber 22, the same effects as in each of the above embodiments can be achieved.
発明の効果
以上の説明から明らかなように、本発明は、油溜シール
部材内に埋設された補強環と作動液の還流通路のシール
室１１１１ ｊ１口端との間に、ピストンロッドと略同
軸に、環状部を設けるとともに、前記補強環と環状部と
の間に、シール室とシール下室とを連通ずる、作動液の
バイパス通路を形成してイルので、ピストンロッドの外
周面とガイド部材の内周面との間の狭小の間隙全通って
、上部液室からシール室内に流入した高温の作動液を、
油溜リップを押し広げてメインリップに衝突させること
なく、バイパス通路を介してシール室内に流入させるこ
とができる。したがって、高温の作動液でメインリップ
が劣化するのを防止できるので、劣化したメインリップ
にてビストノロッド外周面が損傷したり、あるいはビス
トノロッドとの間のシール性が悪化したシするのを未然
に防止できる。Effects of the Invention As is clear from the above description, the present invention provides a structure in which a reinforcing ring embedded in the oil sump sealing member and a sealing chamber 1111j1 which is substantially coaxial with the piston rod is provided between the reinforcing ring embedded in the oil sump sealing member and the opening end of the seal chamber 1111j1 of the working fluid recirculation passage. In addition to providing an annular portion in the reinforcing ring and the annular portion, a bypass passage for hydraulic fluid is formed between the reinforcing ring and the annular portion to communicate the seal chamber and the lower seal chamber. The high-temperature working fluid that flows into the sealing chamber from the upper fluid chamber through the entire narrow gap between the
The oil can flow into the seal chamber via the bypass passage without spreading the oil sump lip and colliding with the main lip. Therefore, it is possible to prevent the main lip from deteriorating due to high-temperature hydraulic fluid, thereby preventing the damaged main lip from damaging the outer peripheral surface of the biston rod or deteriorating the sealing performance between it and the biston rod. can.
また、環状部の上端縁を前記補強環の上端縁の高さよシ
も著干低くない高さに突出させているので、バイパス通
路のシール室側開口端から流出する作動液を、還流通路
内に直接に還流させることなく。In addition, since the upper edge of the annular portion is made to protrude to a height that is not significantly lower than the height of the upper edge of the reinforcing ring, the working fluid flowing out from the opening end of the bypass passage on the seal chamber side is diverted into the return passage. without direct reflux.
シール室内に流入させることができる。したがって、シ
ール室内全作動液で常時充満させることができるので、
その作動液で、メインリップ及び油溜リップを常時浸漬
することができ、そのため、ビストノロッドの外周面全
効果的に潤滑することができるとともに、加圧気体の外
筒外への漏洩を防止できる。It can flow into the sealing chamber. Therefore, the seal chamber can be filled with all the working fluid at all times.
The main lip and the oil sump lip can be constantly immersed in the working fluid, so that the entire outer peripheral surface of the biston rod can be effectively lubricated and leakage of pressurized gas to the outside of the outer cylinder can be prevented.
第１図は従来の液圧緩衝器を示す一部省略縦断面図、第
２図は従来のガイド部材周辺上述す拡大断面図、第３図
は本発明に係る液圧゛緩衝器の一実施例を示す、第２図
と同様な拡大断面図、第４図は本発明の他の実施例を示
ス第３図と同様な拡大断面図である。
１・・・シリンダ、２・・・リザーバ室、３・・・外筒
、４・・・シールリテーナ、５・・・ガイド部材、６・
・・ビストノロッド、７・・・貫通孔、７ａ・・・大径
部、７ｂ・・・小径部、８・・・貫通孔、８ａ・・・大
径部、８ｂ・・・小径部、９・・・ロンドシール部材％
１０・・・油溜シール部材、１０ ａ・・・油溜リング
、 １１・・・シール室、１２・・・還流通路。
１３・・・一方向弁、１４・・・上部液室、１５・・・
下部液室、１６・・・減哀力発生手段、１７・・・ピス
トン、２２・・・シール下室、２３・・・補強環、２４
Ａ、２４Ｂ・・・環状部、２５・・・バイパス通路。Fig. 1 is a partially omitted vertical cross-sectional view showing a conventional hydraulic shock absorber, Fig. 2 is an enlarged cross-sectional view of the vicinity of a conventional guide member, and Fig. 3 is an embodiment of a hydraulic shock absorber according to the present invention. FIG. 4 is an enlarged sectional view similar to FIG. 2 showing an example, and FIG. 4 is an enlarged sectional view similar to FIG. 3 showing another embodiment of the invention. DESCRIPTION OF SYMBOLS 1... Cylinder, 2... Reservoir chamber, 3... Outer cylinder, 4... Seal retainer, 5... Guide member, 6...
...Bistonorod, 7...Through hole, 7a...Large diameter part, 7b...Small diameter part, 8...Through hole, 8a...Large diameter part, 8b...Small diameter part, 9...・Rondo seal parts%
DESCRIPTION OF SYMBOLS 10...Oil sump seal member, 10a...Oil sump ring, 11...Seal chamber, 12...Recirculation passage. 13... One-way valve, 14... Upper liquid chamber, 15...
Lower liquid chamber, 16... Reducing force generating means, 17... Piston, 22... Seal lower chamber, 23... Reinforcement ring, 24
A, 24B... Annular part, 25... Bypass passage.
Claims (3)
ンダを囲繞して、該シリンダとの間に、封入気体による
力１１圧下に所望量の作１：１ｈ液が充填されたリザー
バ室を形成する有底筒状の外筒と、この外筒の一端内部
に固着された、下方に面する大径部及びこれと同軸の小
径部とからなる貫通孔全具えたシールリテーナと、この
シールリテーナと前記シリンダの一９ｍ トの間に挟設
された。上方に面する大径部及びこれと同軸の小径部と
からなる貫通孔を具えたガイド部材と、この方イド部材
及びシールリテーナの貫通孔を貫通して前記シリンダの
内部に延びる、摺動可能なピストンロンドと、このピス
トンロンドの外周面に弾接されて、封入気体等の外筒外
への漏出を阻止するメインリップを内周部に有すると共
に、外周部が前記シールリテーナの大径部内に圧入され
たロットシール部材と、前記ピストンロンドの外周面に
弾接される油溜りツブを内周部に有すると共に、前記メ
インリップよシも低くない高さに突出する補強環が埋設
された外周部が前記ガイド部材の大径部内に圧入された
油溜７一ル部材と、一端が前記ロットシール部材と前記
油溜シール部材との間に形成されたシール室に開口し、
他端が前記リザーバ室に開口するように前記ガイド部材
に穿設された還流通路と、前記シール室から前記リザー
バ室への作動液の流入は許容するも、前記リザーバ室か
ら前記シール室への加圧気体の流入は阻止する一方向弁
と、前記シリンダ内部を上部液室と下部液室との二基に
隔成すべく前記ピストンロッドに固着された。減衰力発
生手段？有するピストンとを備え、前記ピストンロッド
の少くとも伸び行程時に、前記上部液室内の作動油の一
部を、前記ピストンロッドと前記ガイド部材との間の隙
間から、前記油溜りソッと前記ピストンロッドの外周面
とで形成されたシール下室内に流入させるようにした液
圧緩衝器において、前記油溜シール部材内に埋設した補
強環と前記還流通路のシール室側開口端との間に、前記
ピストンロッドと略同軸に、前記補強環の上端縁の高さ
よりも低くない高さに突出する上端縁を有する環状部を
設けるとともに、前記補強環と環状部との間に、前記シ
ール室と前記シール下室と全連通するバイパス通路を形
成したことを特徴とする液圧緩衝器。(1) A cylinder whose inside is filled with working fluid, and a reservoir chamber surrounding this cylinder and filled with a desired amount of working fluid under pressure of 11 by the enclosed gas. A seal retainer having a bottomed cylindrical outer cylinder, a seal retainer fixed inside one end of the outer cylinder and having a through hole consisting of a large diameter part facing downward and a small diameter part coaxial with this, and this seal. It was sandwiched between the retainer and the cylinder. a guide member having a through hole consisting of a large diameter portion facing upward and a small diameter portion coaxial with the guide member; and a slidable guide member extending into the interior of the cylinder through the through hole of the guide member and the seal retainer. A piston rond, and a main lip on the inner periphery that is in elastic contact with the outer periphery of the piston rond to prevent sealed gas, etc. from leaking out of the outer cylinder, and the outer periphery is inside the large diameter portion of the seal retainer. An outer periphery having a press-fitted rod seal member and an oil reservoir knob on the inner periphery that comes into elastic contact with the outer periphery of the piston rod, and a reinforcing ring embedded therein that protrudes to a height that is not lower than the main lip. an oil sump member having a portion press-fitted into the large diameter portion of the guide member, and one end opening into a seal chamber formed between the lot seal member and the oil sump seal member;
A reflux passage is bored in the guide member such that the other end opens into the reservoir chamber, and although the flow of the working fluid from the seal chamber to the reservoir chamber is allowed, the flow of the working fluid from the reservoir chamber to the seal chamber is allowed. A one-way valve that prevents the inflow of pressurized gas was attached to the piston rod to separate the inside of the cylinder into an upper liquid chamber and a lower liquid chamber. Damping force generation means? and a piston having a piston having a piston, at least during an extension stroke of the piston rod, a part of the hydraulic oil in the upper liquid chamber is transferred from the gap between the piston rod and the guide member to the oil reservoir and the piston rod. In the hydraulic shock absorber, the oil flows into the lower seal chamber formed by the outer circumferential surface of the oil sump seal member, and the oil sump seal is disposed between the reinforcing ring embedded in the oil sump seal member and the opening end of the reflux passage on the seal chamber side. An annular portion having an upper edge protruding to a height not lower than the height of the upper edge of the reinforcing ring is provided approximately coaxially with the piston rod, and between the reinforcing ring and the annular portion, the seal chamber and the A hydraulic shock absorber characterized by forming a bypass passage that fully communicates with a lower chamber of the seal.
れた環状部材からなる前記特許請求の範囲第１項記載の
液圧緩衝器。(2) The hydraulic shock absorber according to claim 1, wherein the annular portion comprises an annular member formed separately from the guide member.
てなる前記特許請求の範囲第１項記載の液圧緩衝器。(3) The hydraulic shock absorber according to claim 1, wherein the annular portion is formed integrally with the guide member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3695584A JPS60179539A (en) | 1984-02-28 | 1984-02-28 | Hydraulic damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP3695584A JPS60179539A (en) | 1984-02-28 | 1984-02-28 | Hydraulic damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60179539A true JPS60179539A (en) | 1985-09-13 |
| JPH0437298B2 JPH0437298B2 (en) | 1992-06-18 |
Family
ID=12484163
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3695584A Granted JPS60179539A (en) | 1984-02-28 | 1984-02-28 | Hydraulic damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60179539A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62181986A (en) * | 1986-02-06 | 1987-08-10 | ヤマハ発動機株式会社 | Steering shock absorber for motorcycle |
| JPS6399048U (en) * | 1986-12-19 | 1988-06-27 | ||
| US5579876A (en) * | 1994-10-15 | 1996-12-03 | August Bilstein Gmbh & Co. Kg | Stopper for a hydraulic dashpot |
| JP2007205435A (en) * | 2006-01-31 | 2007-08-16 | Hitachi Ltd | Hydraulic shock absorber |
| JP2009036262A (en) * | 2007-07-31 | 2009-02-19 | Kayaba Ind Co Ltd | Buffer |
| JP2011236935A (en) * | 2010-05-07 | 2011-11-24 | Kyb Co Ltd | Pneumatic shock absorber |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5276893U (en) * | 1975-12-06 | 1977-06-08 | ||
| JPS5869157U (en) * | 1981-11-04 | 1983-05-11 | 厚木自動車部品株式会社 | sealing device |
| JPS59180134A (en) * | 1983-03-29 | 1984-10-13 | Atsugi Motor Parts Co Ltd | Seal device in hydraulic shock absorber |
| JPS59155341U (en) * | 1983-04-06 | 1984-10-18 | 株式会社 昭和製作所 | Hydraulic shock absorber sealing device |
-
1984
- 1984-02-28 JP JP3695584A patent/JPS60179539A/en active Granted
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5276893U (en) * | 1975-12-06 | 1977-06-08 | ||
| JPS5869157U (en) * | 1981-11-04 | 1983-05-11 | 厚木自動車部品株式会社 | sealing device |
| JPS59180134A (en) * | 1983-03-29 | 1984-10-13 | Atsugi Motor Parts Co Ltd | Seal device in hydraulic shock absorber |
| JPS59155341U (en) * | 1983-04-06 | 1984-10-18 | 株式会社 昭和製作所 | Hydraulic shock absorber sealing device |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62181986A (en) * | 1986-02-06 | 1987-08-10 | ヤマハ発動機株式会社 | Steering shock absorber for motorcycle |
| JPS6399048U (en) * | 1986-12-19 | 1988-06-27 | ||
| JPH0434261Y2 (en) * | 1986-12-19 | 1992-08-14 | ||
| US5579876A (en) * | 1994-10-15 | 1996-12-03 | August Bilstein Gmbh & Co. Kg | Stopper for a hydraulic dashpot |
| JP2007205435A (en) * | 2006-01-31 | 2007-08-16 | Hitachi Ltd | Hydraulic shock absorber |
| JP2009036262A (en) * | 2007-07-31 | 2009-02-19 | Kayaba Ind Co Ltd | Buffer |
| JP2011236935A (en) * | 2010-05-07 | 2011-11-24 | Kyb Co Ltd | Pneumatic shock absorber |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0437298B2 (en) | 1992-06-18 |
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