JP5106054B2 - Shock absorber - Google Patents

Shock absorber Download PDF

Info

Publication number
JP5106054B2
JP5106054B2 JP2007292775A JP2007292775A JP5106054B2 JP 5106054 B2 JP5106054 B2 JP 5106054B2 JP 2007292775 A JP2007292775 A JP 2007292775A JP 2007292775 A JP2007292775 A JP 2007292775A JP 5106054 B2 JP5106054 B2 JP 5106054B2
Authority
JP
Japan
Prior art keywords
cylinder
reservoir
shock absorber
side chamber
passage
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 - Fee Related
Application number
JP2007292775A
Other languages
Japanese (ja)
Other versions
JP2009121498A (en
Inventor
大輔 石井
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
KYB Corp
Original Assignee
KYB Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by KYB Corp filed Critical KYB Corp
Priority to JP2007292775A priority Critical patent/JP5106054B2/en
Publication of JP2009121498A publication Critical patent/JP2009121498A/en
Application granted granted Critical
Publication of JP5106054B2 publication Critical patent/JP5106054B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Landscapes

  • Fluid-Damping Devices (AREA)

Description

本発明は、緩衝器の改良に関する。   The present invention relates to an improved shock absorber.

この種、シリンダ内からリザーバへ液体を排出する排出通路を持つ緩衝器としては、たとえば、ユニフロー型に設定されるものがあり、このような緩衝器では伸長行程時にシリンダ内である伸側室からリザーバへ液体を排出するとともに、リザーバから圧側室へ液体が供給されるようになっており、リザーバへ排出される液体の流れに減衰弁で抵抗を与えて、減衰力を発生するようにしている。   As this type of shock absorber having a discharge passage for discharging liquid from the inside of the cylinder to the reservoir, for example, there is one that is set to a uniflow type. In such a shock absorber, the reservoir from the extension side chamber in the cylinder during the extension stroke is used. The liquid is discharged from the reservoir to the pressure side chamber, and a resistance is given to the flow of the liquid discharged to the reservoir by a damping valve so as to generate a damping force.

このようなシリンダ内からリザーバへ液体を排出する緩衝器では、特に、正立縦置きにして使用される場合、上述のように伸縮行程時に伸側室からリザーバへ液体が排出されるので、単純に伸側室をリザーバに接続するとリザーバに排出される液体がリザーバの上方に充填されている気体を巻き込んで、リザーバ内の液体中への気体の混入を促進してしまう。さらに、緩衝器が伸長行程にある場合、リザーバから圧側室へ液体の供給が上記排出と同時に行われるので、気体混じりの液体が圧側室へ供給されることになり、減衰力特性（ピストン速度に対する発生減衰力の性質）の立上がり不良や減衰力低下といった緩衝器に好ましくない事態を招くことになる。   In such a shock absorber that discharges liquid from the cylinder to the reservoir, especially when used in an upright position, the liquid is discharged from the expansion side chamber to the reservoir during the expansion / contraction stroke as described above. When the extension side chamber is connected to the reservoir, the liquid discharged into the reservoir entrains the gas filled above the reservoir and promotes the mixing of the gas into the liquid in the reservoir. Further, when the shock absorber is in the extension stroke, the liquid is supplied from the reservoir to the pressure side chamber at the same time as the discharge, so that a liquid mixed with gas is supplied to the pressure side chamber. This leads to an unfavorable situation in the shock absorber, such as a poor rise in the nature of the generated damping force and a reduction in damping force.

そこで、このような事態を招くことが無いように、シリンダに嵌合するとともに伸側室とリザーバとを接続する通路が形成されるヘッド部材にリザーバの下方まで延びるパイプを取付けた緩衝器が知られており、このような緩衝器の場合、液体排出時における気体の巻き込みを防止することができる（たとえば、特許文献１参照）。
特開２００２−３４９６２９号公報（図２） Therefore, in order not to cause such a situation, a shock absorber is known in which a pipe extending to the lower side of the reservoir is attached to the head member that is fitted to the cylinder and has a passage that connects the extension side chamber and the reservoir. In the case of such a shock absorber, it is possible to prevent entrainment of gas during liquid discharge (see, for example, Patent Document 1).
JP 2002-349629 A (FIG. 2)

この従来の緩衝器では、上述のように、気体の巻き込みを防止できる点で良いのであるが、鉄道車両の車軸と台車との間のように長期間にわたり頻繁に振動入力されるとともに縦置きで使用されるような箇所に用いる場合、以下のような危惧がある。   In this conventional shock absorber, it is sufficient that gas can be prevented from being entrained as described above. However, vibrations are frequently input over a long period of time as between the axle of a railway vehicle and a carriage, and can be installed vertically. When used in places where it is used, there are the following concerns.

すなわち、上述の従来の緩衝器にあっては、リザーバ内の気体巻き込みを防止するため、ヘッド部材にパイプをぶら下げる格好で取付けるようにしているので、振動入力が繰り返されるとヘッド部材から脱落して、気体の巻き込みを阻止できなくなってしまう可能性がある。   That is, in the above-described conventional shock absorber, in order to prevent gas entrainment in the reservoir, the pipe is attached to the head member so that the pipe is suspended. , There is a possibility that gas entrapment cannot be prevented.

これを回避するべく、パイプをヘッド部材に螺子結合するとともに、螺子結合部に嫌気性接着剤を塗布する方策もあるが、激しい振動が継続的に入力され続けるとやはり上記のように脱落してしまうことを完全に防止しきれないのではないかとの不安も残ることになる。   In order to avoid this, there is a measure to screw the pipe to the head member and apply anaerobic adhesive to the screw joint, but if severe vibration continues to be input, it will fall off as described above. There is still some anxiety that it may not be possible to completely prevent it.

そこで、本発明は上記不具合を改善するために創案されたものであって、その目的とするところは、シリンダからリザーバへの液体排出時にリザーバ内の気体巻き込みを確実に防止できる緩衝器を提供することである。   Therefore, the present invention was devised to improve the above-mentioned problems, and an object of the present invention is to provide a shock absorber that can reliably prevent gas entrainment in the reservoir when liquid is discharged from the cylinder to the reservoir. That is.

上記した目的を達成するため、本発明の課題解決手段における緩衝器は、シリンダと、上記シリンダ内に摺動自在に挿入されるとともに上記シリンダ内を伸側室と圧側室とに区画するピストンと、上記シリンダの外周側に配置され上記シリンダとの間にリザーバを形成する外筒と、上記シリンダ内の液体を上記リザーバへ排出する排出通路とを備えた緩衝器において、上記リザーバ内に収容され上記シリンダ或いは上記外筒の一方に半径方向に位置決められて上記シリンダ或いは上記外筒の一方との間に気室を形成するとともに上記シリンダ或いは上記外筒の他方との間で上記排出通路の一部を形成する筒部材を設け、上記筒部材は、上記シリンダ或いは上記外筒の一方に嵌合する嵌合部と、上記シリンダ或いは上記外筒の他方との間に上記排出通路の一部をなす環状通路を形成する筒部と、上記嵌合部と上記筒部の上端とを接続する水平板状の接続部とを備え、更に、上記筒部の下端を拡径又は縮径させて漏斗状に形成し、又、上記シリンダ外周或いは上記外筒内周に段部を設け、上記嵌合部を上記段部にて下方への移動を規制させてなることを特徴とするものである。 In order to achieve the above object, a shock absorber in the problem solving means of the present invention includes a cylinder, a piston that is slidably inserted into the cylinder and that partitions the cylinder into an extension side chamber and a pressure side chamber, A shock absorber provided with an outer cylinder that is disposed on the outer peripheral side of the cylinder and forms a reservoir with the cylinder, and a discharge passage that discharges the liquid in the cylinder to the reservoir. A part of the discharge passage is formed between one of the cylinder and the outer cylinder, and is positioned radially with respect to the cylinder or the outer cylinder to form an air chamber between the cylinder and the outer cylinder. A cylindrical member is formed, and the cylindrical member is interposed between a fitting portion that is fitted to one of the cylinder or the outer cylinder and the other of the cylinder or the outer cylinder. Diameter a cylindrical portion which forms an annular passage forming a part of the output path, and a horizontal plate-shaped connecting portion for connecting the upper end of the fitting portion and the tubular portion, further, the lower end of the tubular portion Alternatively, the diameter is reduced to form a funnel, and a step is provided on the outer periphery of the cylinder or the inner periphery of the outer cylinder, and the fitting portion is restricted from moving downward at the step. It is what.

本発明の緩衝器によれば、筒部材で気室から隔離される排出通路を介してリザーバの下方へ排出されるので、当該作動油排出時に気室内の気体を巻き込む虞が全く無い。   According to the shock absorber of the present invention, it is discharged below the reservoir through the discharge passage that is isolated from the air chamber by the cylindrical member, so there is no possibility of entraining the gas in the air chamber when the hydraulic oil is discharged.

また、緩衝器に振動が継続的かつ頻繁に入力されても、筒部材がシリンダ或いは外筒と協働して気室を形成しているため、万が一、筒部材がシリンダ或いは外筒に対して位置ずれを生じたとしても、気体巻き込みを阻止できる。   Even if vibration is continuously and frequently input to the shock absorber, the cylinder member forms an air chamber in cooperation with the cylinder or the outer cylinder. Even if displacement occurs, gas entrainment can be prevented.

また、従来緩衝器のようにパイプを螺子締結して嫌気性接着剤で接着する必要が無いので、製造工程が簡略化される。さらに、排出通路がヘッド部材にて複数に分岐して伸側室に連通されるような場合、従来の緩衝器では排出通路数に見合った数のパイプを設けなくてはならないが、本発明の緩衝器にあっては、リザーバ内に一つの筒部材を収容することによって分岐する排出通路を単一の環状通路で収束させることが出来、加工コスト、加工工数の点で有利となる。   In addition, unlike the conventional shock absorber, it is not necessary to screw the pipe and bond it with an anaerobic adhesive, which simplifies the manufacturing process. Further, in the case where the discharge passage is branched into a plurality by the head member and communicates with the extension side chamber, in the conventional shock absorber, the number of pipes corresponding to the number of discharge passages must be provided. In the container, the discharge passage branched by accommodating one cylindrical member in the reservoir can be converged by a single annular passage, which is advantageous in terms of processing cost and man-hour.

以下、図に示した実施の形態に基づき、本発明を説明する。
図１は、一実施の形態における緩衝器の縦断面図である。
図２は、一実施の形態の一変形例における緩衝器の一部拡大縦断面図である。
図３は、一実施の形態の他の変形例における緩衝器の一部拡大縦断面図である。図４は、参考例における緩衝器の一部拡大縦断面図である。
図５は、他の参考例における緩衝器の一部拡大縦断面図である。
図６は、更に別の参考例における緩衝器の一部拡大縦断面図である。
The present invention will be described below based on the embodiments shown in the drawings.
FIG. 1 is a longitudinal sectional view of a shock absorber according to an embodiment.
FIG. 2 is a partially enlarged longitudinal sectional view of a shock absorber according to a modification of the embodiment.
FIG. 3 is a partially enlarged longitudinal sectional view of a shock absorber according to another modification of the embodiment. FIG. 4 is a partially enlarged longitudinal sectional view of the shock absorber in the reference example .
FIG. 5 is a partially enlarged longitudinal sectional view of a shock absorber according to another reference example .
FIG. 6 is a partially enlarged longitudinal sectional view of a shock absorber in still another reference example .

一実施の形態における緩衝器Ｄは、図１に示すように、シリンダ１と、シリンダ１内に摺動自在に挿入されるとともにシリンダ１内を伸側室Ｒ１と圧側室Ｒ２とに区画するピストン２と、シリンダ１内に移動自在に挿入されるともに一端がピストン２に連結されるロッド３と、シリンダ１の外周側に配置されシリンダ１との間にリザーバＲを形成する外筒４と、リザーバＲ内に収容され外筒４に半径方向に位置決められて外筒４との間に気室Ｇを形成するとともにシリンダ１との間で排出通路５を形成する筒部材６とを備えて構成され、この実施の形態の緩衝器Ｄの場合、ユニフロー型に設定されている。   As shown in FIG. 1, a shock absorber D in one embodiment includes a cylinder 1 and a piston 2 that is slidably inserted into the cylinder 1 and that partitions the cylinder 1 into an extension side chamber R1 and a pressure side chamber R2. A rod 3 that is movably inserted into the cylinder 1 and has one end connected to the piston 2, an outer cylinder 4 that is disposed on the outer peripheral side of the cylinder 1 and forms a reservoir R between the cylinder 1, And a cylindrical member 6 that is accommodated in R and is positioned in the outer cylinder 4 in the radial direction so as to form an air chamber G with the outer cylinder 4 and to form a discharge passage 5 with the cylinder 1. In the case of the shock absorber D of this embodiment, the uniflow type is set.

そして、伸側室Ｒ１、圧側室Ｒ２およびリザーバＲには液体たる作動油が充填され、リザーバＲには、筒部材６によって形成される気室Ｇ内に気体も充填されている。   The extension side chamber R1, the pressure side chamber R2 and the reservoir R are filled with hydraulic fluid, and the reservoir R is also filled with gas in an air chamber G formed by the cylindrical member 6.

また、この緩衝器Ｄは、ユニフロー型に設定されているので、収縮行程時にはシリンダ１内にロッド３が侵入するため過剰となるロッド侵入体積分の作動油がシリンダ１内から排出通路５を介してリザーバＲへ排出されるとともに、伸長行程時にはシリンダ１内からロッド３が退出するため伸側室Ｒ１内の作動油が排出通路５を介してリザーバＲへ排出され、ピストン２の上方変位によってシリンダ１内で不足する作動油がリザーバＲから圧側室Ｒ２へ供給されるようになっており、伸縮のどちらの行程においても、油の流れが常に圧側室Ｒ２から伸側室Ｒ１への一方通行となるように、圧側室Ｒ２から伸側室Ｒ１へ向かう液体の流れのみを許容する伸圧通路７と、リザーバＲから圧側室Ｒ２へ向かう液体の流れのみを許容する供給通路８とを備えている。   Further, since the shock absorber D is set to be a uniflow type, the rod 3 enters the cylinder 1 during the contraction stroke, so that excess hydraulic oil enters the cylinder 1 through the discharge passage 5 from the cylinder 1. In addition, the rod 3 is withdrawn from the cylinder 1 during the extension stroke, so that the hydraulic oil in the extension side chamber R1 is discharged to the reservoir R through the discharge passage 5, and the cylinder 2 is displaced by the upward displacement of the piston 2. Insufficient hydraulic oil is supplied from the reservoir R to the pressure side chamber R2, so that the flow of oil is always one-way from the pressure side chamber R2 to the extension side chamber R1 in both strokes. Furthermore, a pressure increasing passage 7 that allows only the flow of liquid from the pressure side chamber R2 to the expansion side chamber R1, and a supply passage 8 that allows only the flow of liquid from the reservoir R to the pressure side chamber R2. It is provided.

以下、各部について詳細に説明すると、シリンダ１は筒状に形成され、その上端は、排出通路５の一部を形成するヘッド部材９によって閉塞されるとともに、下端は、供給通路８が設けられるバルブディスク１０によって閉塞されて、内部には液体たる作動油が充填される。なお、本実施の形態においては、液体は作動油とされているが、これに限られるものではなく、これ以外の液体であってもよい。   Hereinafter, each part will be described in detail. The cylinder 1 is formed in a cylindrical shape, and its upper end is closed by a head member 9 that forms a part of the discharge passage 5, and the lower end is a valve provided with a supply passage 8. It is closed by the disk 10 and filled with hydraulic fluid as a liquid. In the present embodiment, the liquid is hydraulic oil, but is not limited to this, and other liquids may be used.

そして、シリンダ１内は、摺動自在に挿入されるピストン２によって伸側室Ｒ１と圧側室Ｒ２とに区画されており、ピストン２はロッド３の下端に連結され、当該ロッド３は、ヘッド部材９に摺動自在に軸支されている。   The cylinder 1 is partitioned into an expansion side chamber R1 and a compression side chamber R2 by a piston 2 that is slidably inserted. The piston 2 is connected to the lower end of a rod 3, and the rod 3 is connected to the head member 9 by a cylinder. Is slidably supported by the shaft.

また、シリンダ１の外方にはシリンダ１を覆いシリンダ１との間にリザーバＲを形成する外筒４が設けられており、外筒４の上端内周に上記ヘッド部材９が嵌合されるとともに下端はロアキャップ１１が接合され、外筒４内は密封状態とされている。   An outer cylinder 4 that covers the cylinder 1 and forms a reservoir R between the cylinder 1 and the cylinder 1 is provided outside the cylinder 1, and the head member 9 is fitted to the inner periphery of the upper end of the outer cylinder 4. In addition, the lower cap 11 is joined to the lower end, and the inside of the outer cylinder 4 is sealed.

ピストン２は、伸側室Ｒ１と圧側室Ｒ２とを連通するポート７ａを備えており、当該ポート７ａは、ピストン２の上端に配置されるチェックバルブ７ｂによって開閉されるようになっている。このチェックバルブ７ｂは、符示しないバネによって附勢されており、圧側室Ｒ２から伸側室Ｒ１へ作動油が移動する場合には、作動油によって押されて上記バネが縮んでピストン２から後退してポート７ａを開放するが、逆に、伸側室Ｒ１から圧側室Ｒ２へ作動油が移動しようとする流れに対してはポート７ａを閉じたままとして当該流れを阻止する。すなわち、この実施の形態の場合、伸圧通路７は、上記ポート７ａおよびチェックバルブ７ｂとで構成されている。なお、伸圧通路７はピストン２に設けられているが、ピストン２を迂回して圧側室Ｒ２から伸側室Ｒ１へ向かう流れを許容するようにしてもよい。   The piston 2 includes a port 7a that allows the extension side chamber R1 and the pressure side chamber R2 to communicate with each other. The port 7a is opened and closed by a check valve 7b disposed at the upper end of the piston 2. The check valve 7b is urged by a spring (not shown), and when the hydraulic oil moves from the compression side chamber R2 to the extension side chamber R1, the spring is compressed by the hydraulic oil and retracts from the piston 2. In contrast, the port 7a is opened, but conversely, with respect to the flow in which the hydraulic oil is about to move from the expansion side chamber R1 to the compression side chamber R2, the port 7a is kept closed to prevent the flow. That is, in this embodiment, the pressure increasing passage 7 is constituted by the port 7a and the check valve 7b. In addition, although the pressure expansion passage 7 is provided in the piston 2, the flow toward the expansion side chamber R1 from the pressure side chamber R2 by bypassing the piston 2 may be allowed.

ヘッド部材９は、筒状であって、外周側に形成されるフランジ９ａと、図１中上端内周の小さい内径を持つ小径部９ｂと、図１中下端内周の大きい内径を持つ大径部９ｃと、小径部９ｂと大径部９ｃとの間で小径部９ｂと大径部９ｃの間の内径を持つ中間部９ｄと、中間部９ｄから開口してフランジ９ａの下端に通じ排出通路５の一部をなす弁孔９ｅと、小径部９ｂの上端に設けた溝９ｆと、下端から開口して大径部９ｃに連なる嵌合部９ｇとを備えて構成されている。   The head member 9 has a cylindrical shape, a flange 9a formed on the outer peripheral side, a small diameter portion 9b having a small inner diameter at the inner periphery at the upper end in FIG. 1, and a large diameter having a large inner diameter at the inner periphery at the lower end in FIG. A portion 9c, an intermediate portion 9d having an inner diameter between the small-diameter portion 9b and the large-diameter portion 9c between the small-diameter portion 9b and the large-diameter portion 9c, and a discharge passage that opens from the intermediate portion 9d to the lower end of the flange 9a 5, a valve hole 9 e forming a part of 5, a groove 9 f provided at the upper end of the small-diameter portion 9 b, and a fitting portion 9 g that opens from the lower end and continues to the large-diameter portion 9 c.

また、ヘッド部材９の中間部９ｄの内周には、ロッド３の外周に摺接してロッド３のヘッド部材９に対する図１中上下方向の移動をガイドする筒状のベアリング１２が嵌め込まれて固定されるとともに、ロッド３の外周に摺接してロッド３の外周をシールするシール部材１３が溝９ｆ内に収容されて符示しないスナップリングで固定されている。   In addition, a cylindrical bearing 12 that is slidably contacted with the outer periphery of the rod 3 and guides the movement of the rod 3 in the vertical direction in FIG. In addition, a seal member 13 that slides in contact with the outer periphery of the rod 3 and seals the outer periphery of the rod 3 is accommodated in the groove 9f and fixed by a snap ring (not shown).

なお、大径部９ｃの内径は、ロッド３との間に充分に隙間が形成される径に設定され、作動油がこの隙間を介して伸側室Ｒ１から弁孔９ｅへ流入可能なようになっている。また、ベアリング１２の軸方向長さはロッド３の移動を充分にガイドできるよう配慮されるとともに、弁孔９ｅの大径部９ｃ側の開口位置は、弁孔９ｅをベアリング１２で塞ぐことが無いように配慮されるのは当然である。
The inner diameter of the large diameter portion 9c is set to a diameter that allows a sufficient gap to be formed between the large diameter portion 9c and the hydraulic oil can flow into the valve hole 9e from the expansion side chamber R1 through this gap. ing. Further, the axial length of the bearing 12 is considered so that the movement of the rod 3 can be sufficiently guided, and the opening position of the valve hole 9e on the large diameter portion 9c side does not block the valve hole 9e with the bearing 12. It is natural that this is taken into account.

さらに、ヘッド部材９は、フランジ９ａの外周が外筒４の内周に嵌合するようになっており、下端に設けた大径部９ｃより大径の嵌合部９ｇ内に嵌合されるシリンダ１を外筒４に対して半径方向に位置決めている。   Further, the head member 9 is configured such that the outer periphery of the flange 9a is fitted into the inner circumference of the outer cylinder 4, and is fitted into the fitting portion 9g having a larger diameter than the large diameter portion 9c provided at the lower end. The cylinder 1 is positioned in the radial direction with respect to the outer cylinder 4.

そして、上記弁孔９ｅ内には、減衰バルブ１４が設けられており、この減衰バルブ１４は、緩衝器Ｄの伸縮行程時に、弁孔９ｅを通過する作動油の流れに抵抗を与えて緩衝器Ｄに減衰力を発揮させるものである。   A damping valve 14 is provided in the valve hole 9e. The damping valve 14 provides resistance to the flow of hydraulic oil passing through the valve hole 9e during the expansion / contraction stroke of the shock absorber D, and the shock absorber. D causes the damping force to be exerted.

つづいて、バルブディスク１０は、シリンダ１より大径の本体１０ａと、シリンダ１の図１中下端に嵌合する筒状凸部１０ｂと、本体１０ａの外周から開口して上端へ通じるポート１０ｃとを備えて構成されている。そして、バルブディスク１０は、外筒４の下端に固定されるロアキャップ１１の凹部１１ａに本体１０ａを嵌合し、外筒４の図１中上端内周に螺合されるナット２５でヘッド部材９を図１中下方へ締め付けることで、シリンダ１およびヘッド部材９とともに外筒４に固定されるようになっている。
Subsequently, the valve disc 10 includes a main body 10a having a diameter larger than that of the cylinder 1, a cylindrical convex portion 10b fitted to the lower end in FIG. 1 of the cylinder 1, and a port 10c that opens from the outer periphery of the main body 10a and communicates with the upper end. It is configured with. Then, the valve disk 10 is fitted with a body 10a in a recess 11a of a lower cap 11 fixed to the lower end of the outer cylinder 4, and a head member with a nut 25 screwed into the inner periphery of the upper end in FIG. 1 is fixed to the outer cylinder 4 together with the cylinder 1 and the head member 9 by tightening 9 downward in FIG.

そして、バルブディスク１０の図１中上面には、チェックバルブ１５が配置され、このチェックバルブ１５によってポート１０ｃが開閉されるようになっている。このチェックバルブ１５は、符示しないバネによって附勢されており、リザーバＲから圧側室Ｒ２へ作動油が移動する場合には、作動油によって押されて上記バネが縮んでバルブディスク１０から後退してポート１０ｃを開放するが、逆に、圧側室Ｒ２からリザーバＲへ作動油が移動しようとする流れに対してはポート１０ｃを閉じたままとして当該流れを阻止する。すなわち、この実施の形態の場合、供給通路８は、上記ポート１０ｃおよびチェックバルブ１５とで構成されている。   A check valve 15 is disposed on the upper surface of the valve disk 10 in FIG. 1, and the port 10 c is opened and closed by the check valve 15. The check valve 15 is urged by a spring (not shown). When the hydraulic oil moves from the reservoir R to the pressure side chamber R2, the check valve 15 is pushed by the hydraulic oil and the spring is contracted to retract from the valve disk 10. In contrast, the port 10c is opened, but conversely, the flow of hydraulic fluid from the pressure side chamber R2 to the reservoir R is prevented from flowing while the port 10c is kept closed. That is, in this embodiment, the supply passage 8 is constituted by the port 10 c and the check valve 15.

つづいて、この緩衝器Ｄにあっては、リザーバＲ内に筒部材６を収容している。この筒部材６は、外筒４の内周に嵌合する嵌合部６ａと、シリンダ１の外周とのの間に排出通路５を形成する筒部６ｂと、嵌合部６ａと筒部６ｂとを接続する接続部６ｃとを備えて構成され、嵌合部６ａは、外筒４の内周に設けた段部４ａによって図１中下方となる圧側室Ｒ２側への移動が規制されている。   Subsequently, in the shock absorber D, the cylindrical member 6 is accommodated in the reservoir R. The cylindrical member 6 includes a fitting portion 6a that fits on the inner periphery of the outer tube 4, a cylindrical portion 6b that forms a discharge passage 5 between the outer periphery of the cylinder 1, and a fitting portion 6a and a cylindrical portion 6b. The fitting portion 6a is restricted from moving toward the pressure side chamber R2 which is the lower side in FIG. 1 by the step portion 4a provided on the inner periphery of the outer cylinder 4. Yes.

この筒部材６の場合、嵌合部６ａは筒状とされて外筒４の内周に嵌合できるようになっており、筒部６ｂはその内径がシリンダ外径より大径に設定されシリンダ１の外周に沿ってシリンダ１との間に一定の環状の隙間を形成するとともに下端が漏斗状に拡径されている。そして、筒部６ｂとシリンダ１との間の隙間によって排出通路５の一部をなす環状通路１６が形成され、当該環状通路１６で弁孔９ｅとリザーバＲの図２中下方とを連通し、当該環状通路１６と弁孔９ｅとで排出通路５が形成される。   In the case of this cylindrical member 6, the fitting portion 6a is formed in a cylindrical shape so that it can be fitted to the inner periphery of the outer cylinder 4, and the inner diameter of the cylindrical portion 6b is set to be larger than the outer diameter of the cylinder. A constant annular gap is formed along the outer periphery of the cylinder 1 with the cylinder 1, and the lower end is expanded in a funnel shape. An annular passage 16 that forms part of the discharge passage 5 is formed by the gap between the cylinder portion 6b and the cylinder 1, and the valve passage 9e communicates with the lower part of the reservoir R in FIG. The annular passage 16 and the valve hole 9e form the discharge passage 5.

また、接続部６ｃは、嵌合部６ａの上端と筒部６ｂの上端とに連なり、この場合、筒部材６は、パイプ材をプレス加工して製造可能とされている。   Moreover, the connection part 6c continues to the upper end of the fitting part 6a and the upper end of the cylinder part 6b. In this case, the cylinder member 6 can be manufactured by pressing a pipe material.

そして、リザーバＲ内に筒部材６を収容して筒部材６を外筒４の内周に嵌合すると、筒部材６でリザーバＲ内に部屋が仕切られて、当該部屋で気体が充填される気室Ｇが形成されるとともに、筒部材６とヘッド部材９のフランジ９ａとの間の空間Ａ内に気体が入り込むことが無いようになっている。   When the cylindrical member 6 is accommodated in the reservoir R and the cylindrical member 6 is fitted to the inner periphery of the outer cylinder 4, the chamber is partitioned into the reservoir R by the cylindrical member 6, and gas is filled in the chamber. An air chamber G is formed, and gas does not enter the space A between the tubular member 6 and the flange 9a of the head member 9.

また、筒部材６は外筒４に嵌合されるので、半径方向に位置決められ、筒部６ｂがシリンダ１と干渉してしまうことが防止され、排出通路５を安定的に形成することができるようになっている。   Moreover, since the cylindrical member 6 is fitted to the outer cylinder 4, it is positioned in the radial direction, the cylindrical portion 6b is prevented from interfering with the cylinder 1, and the discharge passage 5 can be stably formed. It is like that.

さらに、筒部６ｂの下端が拡径されているので、伸側室Ｒ１から排出されて筒部６ｂとシリンダ１との間を速い速度で通過してきた作動油の速度を、徐々に減速させて、供給通路８の吸込口があるリザーバＲの下方において乱流の発生を抑制するとともに、急減圧による作動油中の気泡の発生（エアレーション）を抑制している。   Furthermore, since the lower end of the cylinder part 6b is expanded, the speed of the hydraulic oil discharged from the extension side chamber R1 and passing between the cylinder part 6b and the cylinder 1 at a high speed is gradually reduced. While suppressing the generation of turbulent flow below the reservoir R where the suction port of the supply passage 8 is located, the generation of bubbles (aeration) in the hydraulic oil due to sudden pressure reduction is suppressed.

したがって、シリンダ１内からリザーバＲへの作動油の排出と、リザーバＲからシリンダ１への作動油の供給が同時に行われる緩衝器Ｄの伸長行程時において、圧側室Ｒ２内に気泡含みの作動油が供給されてしまうことが防止されている。   Therefore, hydraulic oil containing bubbles in the compression side chamber R2 is provided during the expansion stroke of the shock absorber D in which the hydraulic oil is discharged from the cylinder 1 to the reservoir R and the hydraulic oil is supplied from the reservoir R to the cylinder 1 at the same time. Is prevented from being supplied.

つづいて、このように構成された緩衝器Ｄにあっては、伸長する場合、ピストン２がシリンダ１に対して図１中上方へ移動するので、伸側室Ｒ１の容積が減少するので減少容積見合いの作動油が押し出され、当該作動油は、弁孔９ｅ内の減衰バルブ１４を押し開いて当該弁孔９ｅおよび筒部材６の筒部６ｂとシリンダ１との間の環状通路１６でなる排出通路５を介してリザーバＲへ排出される。   Subsequently, in the shock absorber D configured as described above, when the piston 2 is extended, the piston 2 moves upward in FIG. 1 with respect to the cylinder 1, so that the volume of the extension side chamber R1 is reduced, so that the reduced volume is commensurate. The hydraulic oil is pushed out, the hydraulic oil pushes open the damping valve 14 in the valve hole 9e, and the discharge passage is formed by the annular passage 16 between the valve hole 9e and the cylindrical portion 6b of the cylindrical member 6 and the cylinder 1. 5 to the reservoir R.

他方、ピストン２がシリンダ１に対して図１中上方へ移動によって容積が拡大される圧側室Ｒ２へは、供給通路８を介してリザーバＲから拡大容積見合いの作動油が供給される。   On the other hand, hydraulic oil commensurate with the expanded volume is supplied from the reservoir R via the supply passage 8 to the pressure side chamber R2 whose volume is expanded by moving the piston 2 upward in FIG.

この伸長行程時には、伸側室Ｒ１からリザーバＲへ排出される作動油は、上述の通り、筒部材６で気室Ｇから隔離される排出通路５を介してリザーバＲの下方へ排出されるので、当該作動油排出時に気室Ｇ内の気体を巻き込む虞が全く無い。   During this extension stroke, the hydraulic oil discharged from the expansion side chamber R1 to the reservoir R is discharged below the reservoir R through the discharge passage 5 isolated from the air chamber G by the cylindrical member 6 as described above. There is no possibility of entraining the gas in the air chamber G when the hydraulic oil is discharged.

また、緩衝器Ｄに振動が継続的かつ頻繁に入力されても、筒部材６が外筒４と協働して気室Ｇを形成しているため、万が一、筒部材６が外筒４に対して図１中上下方向へ位置ずれを生じたとしても、気体巻き込みを阻止できる。   Even if vibrations are continuously and frequently input to the shock absorber D, the cylinder member 6 cooperates with the outer cylinder 4 to form the air chamber G. On the other hand, even if a positional shift occurs in the vertical direction in FIG.

さらに、緩衝器Ｄに振動が継続的かつ頻繁に入力されても、半径方向に位置決めされているので、筒部材６が外筒４から脱落して何ら支持されずにリザーバＲ内で遊んでしまいシリンダ１に干渉して異音を発生してしまうような事態をも阻止できる。   Furthermore, even if vibration is continuously input to the shock absorber D, the cylinder member 6 falls off from the outer cylinder 4 and plays in the reservoir R without being supported at all because it is positioned in the radial direction. It is possible to prevent a situation in which abnormal noise is generated due to interference with the cylinder 1.

また、さらには、筒部材６の嵌合部６ａが外筒４の段部４ａによって圧側室Ｒ２側への移動を規制しているので、筒部材６の下方への移動を確実に防止できるので、筒部材６がロアキャップ１１と干渉して異音を発生してしまうことを確実に防止できる。なお、筒部材６が嵌合部６ａと接続部６ｃと筒部６ｂとで構成されているので、リザーバＲの上方に伸側室Ｒ１から排出されてきた作動油が噴出する空間Ａを形成することができ、筒部材６の嵌合部６ａが外筒４の段部４ａによって圧側室Ｒ２側への移動を規制される一方、空間Ａに発生する圧力で筒部材６が下方に押圧されるので筒部材６の図１中上下方向の移動を抑制することができる。   Furthermore, since the fitting portion 6a of the tubular member 6 restricts the movement of the tubular member 6 toward the pressure side chamber R2 by the step portion 4a of the outer tube 4, the downward movement of the tubular member 6 can be reliably prevented. It is possible to reliably prevent the cylindrical member 6 from interfering with the lower cap 11 and generating abnormal noise. In addition, since the cylinder member 6 is comprised by the fitting part 6a, the connection part 6c, and the cylinder part 6b, the space A where the hydraulic fluid discharged | emitted from the expansion side chamber R1 ejects above the reservoir | reserver R is formed. Since the fitting part 6a of the cylindrical member 6 is restricted from moving toward the pressure side chamber R2 by the step part 4a of the outer cylinder 4, the cylindrical member 6 is pressed downward by the pressure generated in the space A. The movement of the cylindrical member 6 in the vertical direction in FIG. 1 can be suppressed.

なお、段部４ａを設けずに外筒４の内周に嵌合部６ａを単に圧入する等して筒部材６を外筒４に固定する場合、筒部６ｂの図１中下端側の気室Ｇに対面しない部位に、筒部６ｂの内外を連通する切欠や孔を設けておけば、万が一、筒部材６が最下端にまで移動した場合にも、切欠や孔を介して作動油の流通が確保されるので、緩衝器Ｄに要求される減衰機能が損なわれることはない。   When the cylindrical member 6 is fixed to the outer cylinder 4 by simply press-fitting the fitting part 6a into the inner periphery of the outer cylinder 4 without providing the stepped part 4a, the air at the lower end side in FIG. If a notch or hole that communicates the inside and the outside of the cylinder portion 6b is provided in a portion that does not face the chamber G, the hydraulic oil can be removed through the notch or hole even if the cylinder member 6 moves to the lowest end. Since distribution is ensured, the damping function required for the shock absorber D is not impaired.

また、従来緩衝器のようにパイプを螺子締結して嫌気性接着剤で接着する必要が無いので、製造工程が簡略化される。さらに、弁孔９ｅが複数設けられるなど排出通路５がヘッド部材９にて複数に分岐して伸側室Ｒ１に連通されるような場合、従来の緩衝器では排出通路数に見合った数のパイプを設けなくてはならないが、本発明の緩衝器Ｄにあっては、リザーバＲ内に一つの筒部材６を収容することによって分岐する排出通路５を単一の環状通路１６で収束させることが出来、加工コスト、加工工数の点で有利となる。
In addition, unlike the conventional shock absorber, it is not necessary to screw the pipe and bond it with an anaerobic adhesive, which simplifies the manufacturing process. Further, when the discharge passage 5 is branched into a plurality at the head member 9 and communicates with the extension side chamber R1 such as by providing a plurality of valve holes 9e , the conventional shock absorber has a number of pipes corresponding to the number of discharge passages. Although it is necessary to provide the shock absorber D of the present invention, the discharge passage 5 branched by accommodating one cylindrical member 6 in the reservoir R can be converged by a single annular passage 16. This is advantageous in terms of processing cost and processing man-hours.

なお、筒部材６で仕切られる気室Ｇからの気体漏れをより確実に防止したい場合には、接続部６ｃの外周から垂下される嵌合部６ａの図１中下端を気室Ｇの下端より下方に配置されるように設定したり、嵌合部６ａと外筒４との間にシールリングを介装したりすればよく、さらには、図２に示すように、弁孔９ｅの出口端を閉塞しないようにヘッド部材９と接続部６ｃとの間に圧縮される状態でシールリング１７を介装することで気室Ｇからの気体漏れを防止しても良い。このように、ヘッド部材９と接続部６ｃとの間にシールリング１７を介装する場合には、筒部材６を図２中下方へ押圧することになるので嵌合部６ａが段部４ａに押し付けられる格好となり筒部材６の上下方向への移動を同時に規制することもでき、筒部材６がリザーバＲ内で遊んでしまうことを確実に防止することもできる。   In addition, when it is desired to more reliably prevent gas leakage from the air chamber G partitioned by the cylindrical member 6, the lower end in FIG. 1 of the fitting portion 6a suspended from the outer periphery of the connection portion 6c is connected to the lower end of the air chamber G. What is necessary is just to set so that it may be arrange | positioned below, or to interpose a seal ring between the fitting part 6a and the outer cylinder 4, and also as shown in FIG. 2, the exit end of the valve hole 9e Gas leakage from the air chamber G may be prevented by interposing the seal ring 17 in a compressed state between the head member 9 and the connection portion 6c so as not to block the air. As described above, when the seal ring 17 is interposed between the head member 9 and the connecting portion 6c, the tubular member 6 is pressed downward in FIG. 2, so that the fitting portion 6a becomes the step portion 4a. It is possible to prevent the cylinder member 6 from playing in the reservoir R, and it is possible to prevent the cylinder member 6 from playing in the reservoir R at the same time.

また、この実施の形態の場合、筒部材６は外筒４に嵌合されて固定されるようになっているが、反対に、図３に示すように、シリンダ１の外周に筒部材１８を嵌合するようにしても良い。この筒部材１８は、上述の筒部材６における嵌合部６ａと筒部６ｂの配置を、接続部６ｃを挟んで入れ替えた構造となっており、接続部１８ｃの内周側に嵌合部１８ａが設けられ、接続部１８ｃの外周側に筒部１８ｂが設けられている。   In the case of this embodiment, the cylindrical member 6 is fitted and fixed to the outer cylinder 4, but on the contrary, as shown in FIG. You may make it fit. The tubular member 18 has a structure in which the arrangement of the fitting portion 6a and the tubular portion 6b in the tubular member 6 described above is replaced with the connecting portion 6c interposed therebetween, and the fitting portion 18a is arranged on the inner peripheral side of the connecting portion 18c. And a cylindrical portion 18b is provided on the outer peripheral side of the connecting portion 18c.

そして、この筒部材１８は、嵌合部１８ａをシリンダ１の外周に嵌合してシリンダ１に半径方向に位置決められて固定されており、シリンダ１の外周に設けた段部１ａによって図３中下方側となる圧側室Ｒ２側への移動が規制されている。   The cylindrical member 18 is fixed to the cylinder 1 by being fitted with the fitting portion 18a on the outer periphery of the cylinder 1 in the radial direction. The step portion 1a provided on the outer periphery of the cylinder 1 in FIG. Movement to the pressure side chamber R2 side, which is the lower side, is restricted.

また、筒部１８ｂは、外筒４の内周との間に排出通路５の一部を成す環状通路１９を形成しており、筒部１８ｂの下端は外筒４から遠ざかるように縮径されて、環状通路１９の流路面積が徐々に拡大されるようになっている。   Further, the cylindrical portion 18 b forms an annular passage 19 that forms a part of the discharge passage 5 with the inner periphery of the outer cylinder 4, and the lower end of the cylindrical portion 18 b is reduced in diameter so as to move away from the outer cylinder 4. Thus, the flow passage area of the annular passage 19 is gradually enlarged.

このように、筒部材１８は上述の筒部材６とは異なりシリンダ１側に固定されることになり、シリンダ１と協働して気室Ｇを形成しており、筒部１８ｂの外周側に気室Ｇから隔絶された環状通路１９を形成するようになっているが、このようにしても筒部材６と同様の作用効果を奏することができる。   In this way, the cylindrical member 18 is fixed to the cylinder 1 side unlike the above-described cylindrical member 6, and forms an air chamber G in cooperation with the cylinder 1, and on the outer peripheral side of the cylindrical portion 18b. Although the annular passage 19 isolated from the air chamber G is formed, the same function and effect as the cylindrical member 6 can be obtained even in this way.

さらに、図４の参考例に示すように、筒部２０ｂと接続部２０ｃの構成は上記筒部材６と同様にする一方、筒部材２０における嵌合部２０ａを接続部２０ｃの外周から立ち上がるようにするようにしてもよく、この場合、嵌合部２０ａの上端をヘッド部材９のフランジ９ａの下端に当接させるとともに、嵌合部２０ａの接続部２０ｃから立ち上がる部分を外筒４の段部４ａに当接するようにしておけば、筒部材２０は、ヘッド部材９と外筒４の段部４ａとで挟持されて上下方向の移動が規制されるので、筒部材２０がリザーバＲ内で遊んでしまうことを確実に防止することもできる。
Furthermore, as shown in the reference example of FIG. 4, the configuration of the cylindrical portion 20b and the connecting portion 20c is the same as that of the cylindrical member 6, while the fitting portion 20a of the cylindrical member 20 is raised from the outer periphery of the connecting portion 20c. In this case, the upper end of the fitting portion 20a is brought into contact with the lower end of the flange 9a of the head member 9, and the portion rising from the connecting portion 20c of the fitting portion 20a is the step portion 4a of the outer cylinder 4. Since the cylinder member 20 is sandwiched between the head member 9 and the step portion 4a of the outer cylinder 4 and is prevented from moving in the vertical direction, the cylinder member 20 is idle in the reservoir R. It is also possible to reliably prevent this.

そして、さらに、図５の他の参考例に示すように、嵌合部２１ａと接続部２１ｃの構成は上記筒部材２０と同様にする一方、筒部材２１の軸方向長さとなる図５中上下方向長さをヘッド部材９とロアキャップ１１とで挟持可能な長さに設定しておき、筒部２１ｂの気室Ｇの下端より下方側の任意の位置に切欠２１ｄを設けるようにしてもよい。
Further, as shown in another reference example of FIG. 5, the configuration of the fitting portion 21 a and the connecting portion 21 c is the same as that of the cylindrical member 20, while the vertical length in FIG. 5 is the axial length of the cylindrical member 21. The length in the direction may be set to a length that can be sandwiched between the head member 9 and the lower cap 11, and the notch 21d may be provided at an arbitrary position below the lower end of the air chamber G of the cylindrical portion 21b. .

この場合、嵌合部２１ａの上端はヘッド部材９のフランジ９ａの下端に接し、筒部２１ｂの下端はロアキャップ１１に接して、筒部材２１の持つ弾性による張力により、上下方向の移動が規制されるとともに、嵌合部２１ａが外筒４の内周に嵌合してリザーバＲ内で半径方向に位置決められている。なお、図６の他の参考例に示すように、筒部材２１の上下方向の移動の規制に当たっては、筒部材２１における下端とロアキャップ１１との間、すなわち、筒部２１ｂの下端とロアキャップ１１との間に、スプリングワッシャ、バネ、ゴム等の弾性体２３を介装して、筒部材２１をヘッド部材９へ附勢するようにしても良い。
In this case, the upper end of the fitting portion 21 a is in contact with the lower end of the flange 9 a of the head member 9, and the lower end of the cylinder portion 21 b is in contact with the lower cap 11, and the vertical movement is restricted by the elastic tension of the cylinder member 21. In addition, the fitting portion 21a is fitted into the inner periphery of the outer cylinder 4 and is positioned in the radial direction in the reservoir R. As shown in another reference example of FIG. 6, when restricting the vertical movement of the cylindrical member 21, it is between the lower end of the cylindrical member 21 and the lower cap 11, that is, the lower end of the cylindrical portion 21 b and the lower cap. 11, an elastic body 23 such as a spring washer, a spring, or rubber may be interposed between the cylinder member 21 and the head member 9.

また、この筒部材２１にあっては、切欠２１ｄを介して気室Ｇ側と筒部２１ｂとシリンダ１との間に形成した環状通路２２との連通が確保されるので、リザーバＲの機能は損なわれることが無い。無論、環状通路２２と気室Ｇ側との連通に際しては、図６に示すように、切欠２１ｄに代えて設けた孔２１ｅを介して行うようにしても良い。   In addition, in this cylindrical member 21, the communication between the air chamber G side and the annular passage 22 formed between the cylindrical portion 21b and the cylinder 1 is ensured through the notch 21d. There is no damage. Of course, the communication between the annular passage 22 and the air chamber G side may be performed via a hole 21e provided in place of the notch 21d as shown in FIG.

この筒部材２１にあっても、外筒４と協働して気室Ｇを形成しており、筒部２１ｂの内周側に気室Ｇから隔絶された環状通路２２を形成するようになっているので、このようにしても筒部材６と同様の作用効果を奏することができるとともに、上下方向の移動が規制されるので、筒部材２１がリザーバＲ内で遊んでしまうことを確実に防止することもできる。なお、筒部材２１の嵌合部２１ａと筒部２１ｂの配置を、接続部２１ｃを挟んで内外を入れ替えて、筒部材２１をシリンダ１に固定するようにしても良い。   Even in this cylindrical member 21, the air chamber G is formed in cooperation with the outer cylinder 4, and an annular passage 22 isolated from the air chamber G is formed on the inner peripheral side of the cylindrical portion 21b. Therefore, even if it does in this way, while having the same effect as the cylinder member 6, since a vertical movement is controlled, it is surely prevented that the cylinder member 21 is idle in the reservoir R. You can also Note that the tubular member 21 may be fixed to the cylinder 1 by changing the arrangement of the fitting portion 21a and the tubular portion 21b of the tubular member 21 with the connection portion 21c interposed therebetween.

以上で、本発明の実施の形態と参考例についての説明を終えるが、本発明の範囲は図示されまたは説明された詳細そのものには限定されないことは勿論である。
This is the end of the description of the embodiment and the reference example of the present invention, but it is needless to say that the scope of the present invention is not limited to the details shown or described.

一実施の形態における緩衝器の縦断面図である。It is a longitudinal cross-sectional view of the shock absorber in one embodiment. 一実施の形態の一変形例における緩衝器の縦断面図である。It is a longitudinal cross-sectional view of the shock absorber in one modification of one embodiment. 一実施の形態の他の変形例における緩衝器の縦断面図である。It is a longitudinal cross-sectional view of the buffer in the other modification of one Embodiment. 参考例における緩衝器の縦断面図である。 It is a longitudinal cross-sectional view of the shock absorber in the reference example . 他の参考例における緩衝器の一部拡大縦断面図である。 It is a partially expanded longitudinal cross-sectional view of the shock absorber in another reference example . 別の参考例における緩衝器の一部拡大縦断面図である。 It is a partially expanded longitudinal cross-sectional view of the shock absorber in another reference example .

符号の説明Explanation of symbols

１ シリンダ
１ａ シリンダにおける段部
２ ピストン
３ ロッド
４ 外筒
４ａ 外筒における段部
５ 排出通路
６、１８、２０、２１ 筒部材
６ａ、１８ａ、２０ａ、２１ａ 嵌合部
６ｂ、１８ｂ、２０ｂ、２１ｂ 筒部
６ｃ、１８ｃ、２０ｃ、２１ｃ 接続部
７ 伸圧通路
７ａ ポート
７ｂ、１５ チェックバルブ
８ 供給通路
９ ヘッド部材
９ａ フランジ
９ｂ 小径部
９ｃ 大径部
９ｄ 中間部
９ｅ 弁孔
９ｆ 溝
９ｇ 嵌合部
１０ バルブディスク
１０ａ バルブディスクにおける本体
１０ｂ バルブディスクにおける筒状凸部
１０ｃ バルブディスクにおけるポート
１１ ロアキャップ
１１ａ ロアキャップにおける凹部
１２ ベアリング
１３ シール部材
１４ 減衰バルブ
２５ ナット
１６、１９、２２ 環状通路
１７ シールリング
２１ｄ 切欠
２１ｅ 孔
２３ 弾性体
Ａ 空間
Ｄ 緩衝器
Ｇ 気室
Ｒ リザーバ
Ｒ１ 伸側室
Ｒ２ 圧側室
DESCRIPTION OF SYMBOLS 1 Cylinder 1a Step part 2 in a cylinder Piston 3 Rod 4 Outer cylinder 4a Step part 5 in an outer cylinder Discharge passage 6, 18, 20, 21 Cylinder member 6a, 18a, 20a, 21a Fitting part 6b, 18b, 20b, 21b Cylinder Portions 6c, 18c, 20c, 21c Connecting portion 7 Pressure increasing passage 7a Port 7b, 15 Check valve 8 Supply passage 9 Head member 9a Flange 9b Small diameter portion 9c Large diameter portion 9d Intermediate portion 9e Valve hole 9f Groove 9g Fitting portion 10 Valve Disc 10a Body 10b in valve disc Cylindrical convex portion 10c in valve disc Port 11 in valve disc Lower cap 11a Concave portion in lower cap 12 Bearing 13 Seal member 14 Damping valve
25 Nut 16, 19, 22 Annular passage 17 Seal ring 21d Notch 21e Hole 23 Elastic body A Space D Buffer G Air chamber R Reservoir R1 Extension side chamber R2 Pressure side chamber

Claims (4)

シリンダと、上記シリンダ内に摺動自在に挿入されるとともに上記シリンダ内を伸側室と圧側室とに区画するピストンと、上記シリンダの外周側に配置され上記シリンダとの間にリザーバを形成する外筒と、上記シリンダ内の液体を上記リザーバへ排出する排出通路とを備えた緩衝器において、上記リザーバ内に収容され上記シリンダ或いは上記外筒の一方に半径方向に位置決められて上記シリンダ或いは上記外筒の一方との間に気室を形成するとともに上記シリンダ或いは上記外筒の他方との間で上記排出通路の一部を形成する筒部材を設け、上記筒部材は、上記シリンダ或いは上記外筒の一方に嵌合する嵌合部と、上記シリンダ或いは上記外筒の他方との間に上記排出通路の一部をなす環状通路を形成する筒部と、上記嵌合部と上記筒部の上端とを接続する水平板状の接続部とを備え、更に、上記筒部の下端を拡径又は縮径させて漏斗状に形成し、又、上記シリンダ外周或いは上記外筒内周に段部を設け、上記嵌合部を上記段部にて下方への移動を規制させてなることを特徴とする緩衝器。 A cylinder, a piston that is slidably inserted into the cylinder and that divides the cylinder into an extension side chamber and a pressure side chamber, and an outer surface that is disposed on the outer peripheral side of the cylinder and forms a reservoir with the cylinder In a shock absorber having a cylinder and a discharge passage for discharging the liquid in the cylinder to the reservoir, the cylinder or the outer cylinder is accommodated in the reservoir and is radially positioned on one of the cylinder or the outer cylinder. A cylinder member is provided which forms an air chamber with one of the cylinders and forms a part of the discharge passage with the other of the cylinder or the outer cylinder, and the cylinder member is the cylinder or the outer cylinder. A cylindrical portion that forms an annular passage that forms a part of the discharge passage between the fitting portion that is fitted to one of the cylinder and the other of the cylinder or the outer cylinder, and the fitting portion and the cylindrical portion. And a horizontal plate-shaped connecting portion for connecting the upper end, further, the lower end of the tubular portion by diameter or a reduced diameter formed in a funnel shape, also the cylinder periphery or the outer cylinder circumferential step portion The shock absorber is characterized in that the fitting portion is restricted from moving downward at the stepped portion. 上記嵌合部が下向きに形成され、上記嵌合部の上端と上記筒部の上端との間に上記接続部が一体に接続されている請求項１に記載の緩衝器。 The shock absorber according to claim 1, wherein the fitting portion is formed downward, and the connection portion is integrally connected between an upper end of the fitting portion and an upper end of the cylindrical portion . 上記接続部と上記シリンダの上端側に連結されるヘッド部材との間にシールリングを介装したことを特徴とする請求項１又は２に記載の緩衝器。 The shock absorber according to claim 1 or 2 , wherein a seal ring is interposed between the connecting portion and a head member coupled to the upper end side of the cylinder . 上記圧側室から上記伸側室へ向かう液体の流れのみを許容する伸圧通路と、上記リザーバから上記圧側室へ向かう液体の流れのみを許容する供給通路とを備え、上記排出通路は上記伸側室から上記リザーバへ向かう液体の流れのみを許容することを特徴とする請求項１、２又は３に記載の緩衝器。 A pressure-increasing passage that allows only the flow of liquid from the pressure-side chamber toward the expansion-side chamber, and a supply passage that allows only a flow of liquid from the reservoir toward the pressure-side chamber, and the discharge passage extends from the extension-side chamber. 4. The shock absorber according to claim 1, wherein only a liquid flow toward the reservoir is allowed .
JP2007292775A 2007-11-12 2007-11-12 Shock absorber Expired - Fee Related JP5106054B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2007292775A JP5106054B2 (en) 2007-11-12 2007-11-12 Shock absorber

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2007292775A JP5106054B2 (en) 2007-11-12 2007-11-12 Shock absorber

Related Child Applications (2)

Application Number Title Priority Date Filing Date
JP2011183676A Division JP5220907B2 (en) 2011-08-25 2011-08-25 Shock absorber
JP2011183675A Division JP5406894B2 (en) 2011-08-25 2011-08-25 Shock absorber

Publications (2)

Publication Number Publication Date
JP2009121498A JP2009121498A (en) 2009-06-04
JP5106054B2 true JP5106054B2 (en) 2012-12-26

Family

ID=40813860

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2007292775A Expired - Fee Related JP5106054B2 (en) 2007-11-12 2007-11-12 Shock absorber

Country Status (1)

Country Link
JP (1) JP5106054B2 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012007737A (en) * 2011-08-25 2012-01-12 Kyb Co Ltd Shock absorber
JP2012021647A (en) * 2011-08-25 2012-02-02 Kyb Co Ltd Buffer

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6353277B2 (en) * 2014-05-30 2018-07-04 Ｋｙｂ株式会社 Horizontal shock absorber
JP6491525B2 (en) * 2015-04-20 2019-03-27 Ｋｙｂ株式会社 Shock absorber

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5996441U (en) * 1982-12-20 1984-06-30 トヨタ自動車株式会社 hydraulic shock absorber
JPH0669780B2 (en) * 1984-03-19 1994-09-07 カヤバ工業株式会社 Attitude control device
JPH08294686A (en) * 1995-04-26 1996-11-12 Tdk Corp Water purifier, water purifying plate and production thereof
JPH09257079A (en) * 1996-03-19 1997-09-30 Tokico Ltd Hydraulic buffer
JP4456779B2 (en) * 2001-05-25 2010-04-28 カヤバ工業株式会社 Hydraulic shock absorber
JP4620415B2 (en) * 2004-09-13 2011-01-26 日本工機株式会社 Sound generator

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012007737A (en) * 2011-08-25 2012-01-12 Kyb Co Ltd Shock absorber
JP2012021647A (en) * 2011-08-25 2012-02-02 Kyb Co Ltd Buffer

Also Published As

Publication number Publication date
JP2009121498A (en) 2009-06-04

Similar Documents

Publication Publication Date Title
JP5150397B2 (en) Hydraulic shock absorber
CN106030149A (en) Shock absorber with frequency dependent passive valve
JP2009014019A (en) Shock absorber
KR101093474B1 (en) Vibration damper with amplitude-dependent damping force
US6622832B2 (en) Hydraulic shock absorber
JP5106054B2 (en) Shock absorber
JP2007057088A (en) Cylinder device
WO2015178287A1 (en) Shock absorber
JP2015163799A (en) hydraulic shock absorber
JP4898613B2 (en) Shock absorber
KR20110057073A (en) Valve comprising a valve closing body
JP5403755B2 (en) Shock absorber
JP5220907B2 (en) Shock absorber
US7677156B2 (en) Piston load of vehicle height adjusting shock absorber and method of machining the same
US20070170027A1 (en) Piston load of vehicle height adjusting shock absorber and method of machining the same
JP5406894B2 (en) Shock absorber
JP2013204792A (en) Shock absorber
JP2005201345A (en) Front fort for motorcycle or the like
CN102235455A (en) Oil pressure buffer
JP2009287719A (en) Hydraulic shock absorber
JP2009204118A (en) Hydraulic shock absorber
JP5132266B2 (en) Double cylinder type shock absorber
JP2023007996A (en) Buffer with vehicle height adjustment function
JP2014149003A (en) Fluid pressure shock absorber
KR20100119569A (en) Damper

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20100422

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20110622

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20110628

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20110825

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20120306

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20120425

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20120911

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20121002

R151 Written notification of patent or utility model registration

Ref document number: 5106054

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R151

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20151012

Year of fee payment: 3

S533 Written request for registration of change of name

Free format text: JAPANESE INTERMEDIATE CODE: R313533

R350 Written notification of registration of transfer

Free format text: JAPANESE INTERMEDIATE CODE: R350

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

LAPS Cancellation because of no payment of annual fees