JPH042826B2 - - Google Patents
Info
- Publication number
- JPH042826B2 JPH042826B2 JP58026075A JP2607583A JPH042826B2 JP H042826 B2 JPH042826 B2 JP H042826B2 JP 58026075 A JP58026075 A JP 58026075A JP 2607583 A JP2607583 A JP 2607583A JP H042826 B2 JPH042826 B2 JP H042826B2
- Authority
- JP
- Japan
- Prior art keywords
- chamber
- piston
- oil
- cylinder
- bellows
- 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 - Lifetime
Links
- 239000006096 absorbing agent Substances 0.000 claims description 13
- 230000035939 shock Effects 0.000 claims description 13
- 238000013016 damping Methods 0.000 claims description 12
- 239000003921 oil Substances 0.000 description 44
- 230000001419 dependent effect Effects 0.000 description 11
- 230000006835 compression Effects 0.000 description 8
- 238000007906 compression Methods 0.000 description 8
- 239000007788 liquid Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000010720 hydraulic oil Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000004513 sizing Methods 0.000 description 2
- 230000008602 contraction Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
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
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
Description
【発明の詳細な説明】
本発明は油圧緩和器の改良に係り、特に圧縮並
びに引張の両側に亘つてのストローク依存特性を
具備するようにした油圧緩衝器に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in a hydraulic damper, and more particularly to a hydraulic damper having stroke dependent characteristics on both compression and tension sides.
外筒と、該外筒内に起設したシリンダである内
筒と、該内筒内を摺動するピストンを保持するピ
ストンロツドとから成り、内・外筒間の油室と、
内筒内の油室とを圧縮行程においてのみ連通する
バルブ機構を内筒の下部に付設し、更に該バルブ
機構の下方に室を形成して該室内に、気体を封入
して成るベローズを収納して構成した油圧緩衝
器、所謂３次元ダンパは知られている。 It consists of an outer cylinder, an inner cylinder that is a cylinder installed inside the outer cylinder, and a piston rod that holds a piston that slides inside the inner cylinder, and an oil chamber between the inner and outer cylinders,
A valve mechanism that communicates with the oil chamber in the inner cylinder only during the compression stroke is attached to the lower part of the inner cylinder, and a chamber is further formed below the valve mechanism, and a bellows filled with gas is housed in the chamber. A hydraulic shock absorber, a so-called three-dimensional damper, is known.
斯かるダンパによれば、バルブ機構によるピス
トン速度依存特性と、ベローズによるピストンス
トローク依存特性とにより減衰力が決定され、３
次元特性が得られるが、微小な振動を吸収するス
トローク依存特性は圧縮行程においてのみ発揮さ
れるものであり、引張行程においては微小な振動
を吸収することができない。 According to such a damper, the damping force is determined by the piston speed dependent characteristic due to the valve mechanism and the piston stroke dependent characteristic due to the bellows.
Although dimensional characteristics can be obtained, stroke-dependent characteristics that absorb minute vibrations are exhibited only in the compression stroke, and minute vibrations cannot be absorbed in the tension stroke.
本発明は以上の点に鑑みて成されたもので、そ
の目的とする処は、引張側におけるストローク依
存特性をも具備し、引張行程での微小な振動を吸
収し得るようにし、従つて圧縮並びに引張の両側
に亘つてのストローク依存特性を発揮し得る油圧
緩衝器を提供するにある。 The present invention has been made in view of the above points, and its purpose is to provide a stroke-dependent characteristic on the tension side so as to be able to absorb minute vibrations in the tension stroke. Another object of the present invention is to provide a hydraulic shock absorber that can exhibit stroke-dependent characteristics on both sides of tension.
斯かる目的を達成すべく本発明は、シリンダ内
を摺動するピストンに減衰力を発生するバルブ機
構を付設して成る油圧緩衝器において、ピストン
ロツド内に室を形成し、該室と、ピストンにより
２室に画成されるシリンダ内の油室の上部および
下部のそれぞれの油室とを連通する油路をピスト
ンロツドに形成するとともに、該ピストンロツド
の上記室内に、気体を封入して成るベローズ等の
内容積可変部材を収納したことを要旨としてい
る。 In order to achieve such an object, the present invention provides a hydraulic shock absorber in which a piston sliding in a cylinder is provided with a valve mechanism that generates a damping force, in which a chamber is formed in the piston rod, and the chamber and the piston are connected to each other. An oil passage communicating with the upper and lower oil chambers of the oil chamber in the cylinder defined by two chambers is formed in the piston rod, and a bellows or the like formed by sealing gas is formed in the chamber of the piston rod. The gist is that a variable internal volume member is housed.
以下に本発明の実施例を添付図面に基づいて詳
述する。第１図は本発明に係る油圧緩衝器の半部
破断側面図、第２図は同要部の縦断側面図であ
る。 Embodiments of the present invention will be described in detail below with reference to the accompanying drawings. FIG. 1 is a half-cutaway side view of a hydraulic shock absorber according to the present invention, and FIG. 2 is a longitudinal sectional side view of the main part thereof.
油圧緩衝器１の本体は、外筒２と、該外筒内に
起設したシリンダである内筒３と、該内筒内を摺
動するピストン４を下端に固着保持したピストン
ロツド５とから構成され、ピストン４により２室
に画成された内筒３内の上部室S1と、下部室S2及
び内・外筒２，３間に形成されたリザーバ室S3の
各室内には作動油が封入されている。 The main body of the hydraulic shock absorber 1 is composed of an outer cylinder 2, an inner cylinder 3 that is a cylinder installed inside the outer cylinder, and a piston rod 5 that firmly holds a piston 4 sliding inside the inner cylinder at its lower end. The inner cylinder 3 is divided into two chambers by the piston 4, including an upper chamber S1 , a lower chamber S2, and a reservoir chamber S3 formed between the inner and outer cylinders 2 and 3. Oil is sealed.
そして内・外筒２，３の上端にはシールキヤツ
プ６が嵌着され、該シールキヤツプ６には上部室
S1とリザーバ室S3とを連通する油路７が形成さ
れ、一方内筒３の底部には、ピストン４の下動、
即ち圧縮行程においてのみ下部室S2とリザーバ室
S3とを連通して減衰力を発生させるバルブ機構８
及び両油室S2，S3を相連通するサイジング（不図
示）が付設されている。 A seal cap 6 is fitted to the upper ends of the inner and outer cylinders 2 and 3, and the seal cap 6 has an upper chamber.
An oil passage 7 communicating between S 1 and the reservoir chamber S 3 is formed, and at the bottom of the inner cylinder 3, a downward movement of the piston 4 is formed.
That is, only in the compression stroke the lower chamber S2 and the reservoir chamber
Valve mechanism 8 that communicates with S 3 to generate damping force
A sizing (not shown) is provided to communicate the oil chambers S 2 and S 3 with each other.
尚外筒２の上部外周にはばね受９が固設され、
該ばね受９と、ピストンロツド５の上部に固設さ
れる不図示のばね受との間にコイルスプリング１
０が張架されている。又外筒３の下部は車輪の軸
支部に、一方ピストンロツド５の上部は自動車等
の車両の車体構成部材に夫々連結される。 Furthermore, a spring receiver 9 is fixedly installed on the upper outer periphery of the outer cylinder 2.
A coil spring 1 is inserted between the spring receiver 9 and a spring receiver (not shown) fixedly installed on the upper part of the piston rod 5.
0 is displayed. The lower part of the outer cylinder 3 is connected to the shaft support of a wheel, while the upper part of the piston rod 5 is connected to a body component of a vehicle such as an automobile.
ところでピストン４の中央には取付孔４１が穿
設され、外周にはシールリング４２が嵌着されて
おり、取付孔４１の周辺には放射状に複数の小孔
４３…が穿設され、更にこれら小孔４３…の外周
辺にも同様に放射状に複数の小孔４４…が形成さ
れている。 By the way, a mounting hole 41 is drilled in the center of the piston 4, a seal ring 42 is fitted on the outer periphery, and a plurality of small holes 43 are drilled radially around the mounting hole 41. A plurality of small holes 44 are similarly formed radially around the outer periphery of the small holes 43.
斯かるピストン４の取付孔44に上方からピスト
ンロツド５の下端を構成するボルト６１を挿通
し、この時、ピストン４の上面とボルト６１の基
部外周にスリーブ２１を装着し、スリーブ２１の
外周にプレートリング状のバルブ２２を遊合さ
せ、該バルブ２２の上面とピストンロツド５の下
端面との間にコイルスプリング２４を縮装する。
このバルブ２２の外径はピストン４の取付孔４１
を取り巻く内外２重の小孔４３…及び４４…の外
側の小孔４４…まで閉塞するように充分大径であ
り、内側の小孔４３…と一致するバルブ２２面に
は夫々小孔２３…が穿設されている。 The bolt 61 constituting the lower end of the piston rod 5 is inserted from above into the mounting hole 44 of the piston 4. At this time, the sleeve 21 is attached to the upper surface of the piston 4 and the outer periphery of the base of the bolt 61, and a plate is attached to the outer periphery of the sleeve 21. A ring-shaped valve 22 is loosely engaged, and a coil spring 24 is compressed between the upper surface of the valve 22 and the lower end surface of the piston rod 5.
The outer diameter of this valve 22 is the diameter of the mounting hole 41 of the piston 4.
The diameter is sufficiently large to close up to the outer small hole 44 of the double inner and outer small holes 43 and 44 surrounding the inner and outer small holes 43... is drilled.
更にピストン４の下方に突出する前記ボルト６
１の中間部外周にスリーブ２５を装着し、スリー
ブ２５の外周に縦断面が鉤形を成すリング状のバ
ルブ２６を遊合し、スリーブ２５の下端にプレー
トワツシヤ２７を当て、この時、バルブ２６の下
面とプレートワツシヤ２７との間にコイルスプリ
ング２８を縮装し、ボルト６１の下部にナツト６
９を締結する。このバルブ２６の外径は内側の小
孔４３…のみを閉塞するように充分大径であり、
外側の小孔４４…の下端は開放されている。 Furthermore, the bolt 6 protrudes below the piston 4.
A sleeve 25 is attached to the outer periphery of the middle part of the sleeve 25, a ring-shaped valve 26 having a hook-shaped longitudinal section is loosely fitted to the outer periphery of the sleeve 25, and a plate washer 27 is applied to the lower end of the sleeve 25. A coil spring 28 is compressed between the lower surface of the bolt 61 and the plate washer 27, and a nut 6 is inserted under the bolt 61.
9 will be concluded. The outer diameter of this valve 26 is large enough to close only the inner small hole 43...
The lower ends of the outer small holes 44 are open.
斯かるバルブ機構２０により既知の如くピスト
ン４の上下動、即ち当該油圧緩衝器１の圧縮並び
に引張行程におけるピストン速度依存特性による
減衰力が得られる。これをピストン速度−減衰力
特性線図で表せば第５図の如くである。 As is known, such a valve mechanism 20 provides a damping force that is dependent on the piston speed in the vertical movement of the piston 4, that is, in the compression and tension strokes of the hydraulic shock absorber 1. This can be expressed as a piston speed-damping force characteristic diagram as shown in FIG.
尚第５図では、ストロークが大の時の特性を実
線で、小の時の特性を破線で夫々示している。 In FIG. 5, the characteristics when the stroke is large are shown by a solid line, and the characteristics when the stroke is small are shown by a broken line.
そして本発明では、前記ピストンロツド５内に
小ストロークにおける減衰力を小さくし得るピス
トンストローク依存特性発生装置を構成する。 In the present invention, a piston stroke dependent characteristic generating device is provided in the piston rod 5, which can reduce the damping force during small strokes.
即ちピストンロツド５を構成する本体５０と、
その下端に垂下突設する前記ボルト６１との間に
本体５０よりも大径なる胴部材５１を形成し、本
体５０の下端に該胴部材５１を緊密に螺合締結
し、更に胴部材５１の下端にボルト６１を同じく
緊密に螺合締結する。 That is, a main body 50 constituting the piston rod 5,
A body member 51 having a larger diameter than the main body 50 is formed between the bolt 61 hanging from the lower end thereof, and the body member 51 is tightly screwed and fastened to the lower end of the main body 50. A bolt 61 is also tightly screwed onto the lower end.
胴部材５１内には下方に開放する円筒状の室Ｃ
が形成され、該室Ｃの上方には同心的に油路５２
が連通形成され、油路５２の上部には当該胴部材
５１の外周に開放された相対向する２つの細径な
る油路５３，５３が連通形成されている。この細
径なる２本の油路５３，５３により上部室S1内の
作動油が胴部材５１内の室Ｃ内に流入する際のオ
リフイス効果が得られる。 Inside the body member 51 is a cylindrical chamber C that opens downward.
An oil passage 52 is formed concentrically above the chamber C.
The upper part of the oil passage 52 is formed with two opposing small diameter oil passages 53, 53 which are open to the outer periphery of the body member 51 and communicate with each other. The two small-diameter oil passages 53, 53 provide an orifice effect when the hydraulic oil in the upper chamber S1 flows into the chamber C in the body member 51.
一方ボルト６１の頭部６２内には同心的に油路
６３が形成され、該油路６３の下端には細径なる
油路６３が連通形成され、更にこの細径なる油路
６４の下端には若干大径なる油路６５が当該ボル
ト６１の下方に開放して連通形成されている。上
記細径なる油路６４により下部室S2内の作動油が
胴部材５１内の室Ｃ内に流入する際のオリフイス
効果が得られる。 On the other hand, an oil passage 63 is formed concentrically within the head 62 of the bolt 61, and a small diameter oil passage 63 is formed in communication with the lower end of the oil passage 63, and furthermore, a small diameter oil passage 63 is formed in communication with the lower end of this small diameter oil passage 64. An oil passage 65 having a slightly larger diameter is opened and communicated with the bolt 61 below. The small diameter oil passage 64 provides an orifice effect when the hydraulic oil in the lower chamber S2 flows into the chamber C in the body member 51.
尚ボルト６１の頭部６２上面にはリング溝６６
が形成されている。 There is a ring groove 66 on the top surface of the head 62 of the bolt 61.
is formed.
而して胴部材５１の下端にボルト６１を連結す
る際に、胴部材５１の室Ｃ内に内容積可変部材７
０である金属製のベローズを収納し、ボルト頭部
６２に形成したリング溝６６にコイルスプリング
７９を縮装してベローズ７０を下方から弾発付勢
する。 Therefore, when connecting the bolt 61 to the lower end of the body member 51, the internal volume variable member 7 is inserted into the chamber C of the body member 51.
A coil spring 79 is compressed into a ring groove 66 formed in a bolt head 62 to elastically bias the bellows 70 from below.
このベローズ７０内には気体とともに液体が封
入されており、これによりベローズ７０内の上部
は気体室Ｇを、下部は液体室Ｌを夫々構成してお
り、斯かるベローズ７０は自由状態において室Ｃ
内に伸長状態にある。 Gas and liquid are sealed inside the bellows 70, so that the upper part of the bellows 70 constitutes a gas chamber G and the lower part constitutes a liquid chamber L. In a free state, the bellows 70 forms a chamber C.
It is in a state of extension.
尚ベローズ７０内の気体室Ｇの容積は１乃至３
c.c.程度である。又ベローズ７０の上面及び下面に
は同心的に夫々ガイドロツド７１，７２が突設さ
れ、各ガイドロツド７１，７２は前記室Ｃの上下
に連通形成した油路５２，６３に間隙をもつて進
出状態にある。 The volume of the gas chamber G in the bellows 70 is 1 to 3.
It is about cc. Further, guide rods 71 and 72 are concentrically protruded from the upper and lower surfaces of the bellows 70, respectively, and the guide rods 71 and 72 extend into the oil passages 52 and 63 formed in communication with the upper and lower portions of the chamber C with gaps therebetween. be.
次に内容積可変部材７０の作用を述べる。 Next, the function of the variable internal volume member 70 will be described.
例えばザラザラ路等を車両が走行した場合、路
面から微小な振動を受け、当該油圧緩衝器１には
微小なる伸縮挙動が発生しようとする。 For example, when a vehicle travels on a rough road, it receives minute vibrations from the road surface, and the hydraulic shock absorber 1 tends to undergo minute expansion and contraction behavior.
そして先ず引張挙動が発生歳すると、シリンダ
３内をピストン４が微小量ながら上動し、これに
よりシリンダ３内の上部室S1の油は圧力を高めら
れ、胴部材５１に設けた油路５３，５３及び５２
を経て室Ｃ内に圧油が流入する。この圧油の流入
により室Ｃ内に収納したベローズ７０内の気体室
Ｇは圧縮され、ベローズ７０が圧縮されて上部室
S1内の油の斯かる圧力上昇分が当該ベローズ７０
の気体室Ｇに吸収される。 When the tensile behavior first occurs, the piston 4 moves upward in the cylinder 3 by a minute amount, and as a result, the pressure of the oil in the upper chamber S1 in the cylinder 3 is increased, and the oil passage 51 provided in the body member 51 , 53 and 52
Pressure oil flows into chamber C through . Due to the inflow of this pressure oil, the gas chamber G in the bellows 70 housed in the chamber C is compressed, and the bellows 70 is compressed and the upper chamber is compressed.
This pressure increase of the oil in S 1 is the corresponding bellows 70.
is absorbed into the gas chamber G.
又圧縮挙動が発生すると、シリンダ３内をピス
トン４が微小ながら下動し、この時、リザーバ室
S3内の油がシールキヤツプ６の油路７を経てシリ
ンダ３内の上部室S2に流入し、これにより既知の
如く該上部室S2内の油は圧力を高められるため、
前記と同様に胴部材５１に設けた油路５３，５３
及び５２を経て室Ｃ内に圧油が流入する。斯くし
て室Ｃ内に収納したベローズ７０が圧縮して上部
室S1内の油の斯かる圧力上昇分が当該ベローズ７
０の気体室Ｇに吸収される。 Also, when compression behavior occurs, the piston 4 moves slightly downward inside the cylinder 3, and at this time, the reservoir chamber
The oil in S 3 flows into the upper chamber S 2 in the cylinder 3 through the oil passage 7 of the seal cap 6, and as a result, the pressure of the oil in the upper chamber S 2 is increased as is known.
Oil passages 53, 53 provided in the body member 51 in the same manner as above
Pressure oil flows into the chamber C through . The bellows 70 stored in the chamber C is thus compressed, and the pressure increase of the oil in the upper chamber S1 causes the bellows 7 to compress.
It is absorbed into the gas chamber G at 0.
そして圧縮挙動時における室Ｃ内への上部室S1
からの圧油の流入とともに、該室Ｃ内へは下部室
S2からも圧油が流入する。 and upper chamber S 1 into chamber C during compression behavior
Along with the inflow of pressure oil from the lower chamber
Pressure oil also flows in from S2 .
即ちシリンダ３内の下部室S2の油は圧力を高め
られ、ボルト６１に設けた油路６５，６４及び６
３を経て室Ｃ内に圧油が流入する。この圧油の流
入により室Ｃ内に収納したベローズ７０は前記と
相俟つて同様に圧縮され、両油室S1，S2内の油の
斯かる圧力上昇分が当該ベローズ７０の気体室Ｇ
に吸収される。 That is, the pressure of the oil in the lower chamber S2 in the cylinder 3 is increased, and the oil passages 65, 64 and 6 provided in the bolt 61 are
Pressure oil flows into the chamber C through 3. Due to the inflow of this pressure oil, the bellows 70 housed in the chamber C is compressed in the same manner as described above, and the pressure increase of the oil in both oil chambers S 1 and S 2 is applied to the gas chamber G of the bellows 70.
absorbed into.
以上において、ピストン４に付設したバルブ機
構２０を構成する上下のバルブ２２，２６はとも
に閉状態にある。 In the above, the upper and lower valves 22 and 26 that constitute the valve mechanism 20 attached to the piston 4 are both in the closed state.
尚バルブ２２，２６はピストン４の約10mm程度
のストロークで開挙動するように初期設定されて
いる。又ベローズ７０内には液体室Ｌが構成され
ているため、ベローズ７０の圧縮挙動時におい
て、液体室Ｌがストツパーとなつて当該ベローズ
７０の収縮可能限界が設定される。 The valves 22 and 26 are initially set to open with a stroke of about 10 mm of the piston 4. Further, since the liquid chamber L is formed in the bellows 70, when the bellows 70 is compressed, the liquid chamber L acts as a stopper and sets the contractible limit of the bellows 70.
一方ピストン４のストロークが10mmを越える当
該油圧緩衝器１の伸縮挙動の場合は、ベローズ７
０が圧縮状態にあり、ピストン４に付設したバル
ブ機構２０及びシリンダ３底部に構成したバルブ
機構８並びにサイジングによりピストン速度依存
特性による減衰力が得られる。 On the other hand, if the stroke of the piston 4 exceeds 10 mm and the hydraulic shock absorber 1 expands and contracts, the bellows 7
0 is in a compressed state, and a damping force due to piston speed dependent characteristics is obtained by the valve mechanism 20 attached to the piston 4, the valve mechanism 8 configured at the bottom of the cylinder 3, and the sizing.
以上の構成により油圧緩衝器１のピストン速度
−減衰力特性を図で表せば第３図の通りである。 With the above configuration, the piston speed-damping force characteristics of the hydraulic shock absorber 1 are illustrated in FIG. 3.
尚第３図にあつては、ストロークが大の時の特
性を実線で、中の時の特性を鎖線で、小の時の特
性を破線で夫々示している。 In FIG. 3, the characteristics when the stroke is large are shown by a solid line, the characteristics when the stroke is medium are shown by a chain line, and the characteristics when the stroke is small are shown by a broken line.
以上の如くピストンロツド５内に、引張並びに
圧縮の両側に亘つての特にピストン４の小ストロ
ーク時における減衰力を小さくし得るピストンス
トローク依存特性発生装置を構成した。 As described above, a piston stroke dependent characteristic generating device is constructed in the piston rod 5, which can reduce the damping force on both sides of tension and compression, especially when the piston 4 makes a small stroke.
ところで実施例では、内容積可変部材７０をベ
ローズとしたが、その他、例えばゴム製の袋体等
の可撓材でこれを構成しても同様の効果が得られ
る。 By the way, in the embodiment, the internal volume variable member 70 is made of a bellows, but the same effect can be obtained even if it is made of a flexible material such as a rubber bag.
以上の説明から明らかな如く本発明によれば、
油圧緩衝器を構成するピストンロツド内に室を形
成し、該室とピストンにより２室に画成されるシ
リンダ内の油室の上部および下部のそれぞれの油
室とを連通する油路をピストンロツドに形成する
とともに、該ピストンロツドの上記室内に、気体
を封入して成る内容積可変部材を収納したため、
引張側におけるストローク依存特性をも具備する
ことができる。 As is clear from the above description, according to the present invention,
A chamber is formed in the piston rod constituting the hydraulic shock absorber, and an oil passage is formed in the piston rod that communicates the chamber with the upper and lower oil chambers of the oil chamber in the cylinder, which is defined into two chambers by the piston. At the same time, since a variable internal volume member formed by sealing gas is housed in the chamber of the piston rod,
Stroke-dependent properties on the tension side can also be provided.
図面は本発明の実施例を示すもので、第１図は
油圧緩衝器の半部破断側面図、第２図は同要部の
縦断側面図、第３図はピストン速度−減衰力特性
線図、第４図はバブル機構によるピストン速度−
減衰力特性線図である。
尚図面中１は油圧緩衝器、２は外筒、３はシリ
ンダ、４はピストン、２０はそのバルブ機構、５
はピストンロツド、５２，５３及び６３，６４，
６５はその油路、７０は内容積可変部材、Ｃはピ
ストンロツド内の室、Ｇは内容積可変部材の気体
室、Ｌは同液体室、S1，S2，S3は油室である。
The drawings show an embodiment of the present invention; Fig. 1 is a half-cutaway side view of a hydraulic shock absorber, Fig. 2 is a vertical sectional side view of the main part, and Fig. 3 is a piston speed-damping force characteristic diagram. , Figure 4 shows the piston speed due to the bubble mechanism.
FIG. 3 is a damping force characteristic diagram. In the drawing, 1 is a hydraulic shock absorber, 2 is an outer cylinder, 3 is a cylinder, 4 is a piston, 20 is its valve mechanism, 5
are piston rods, 52, 53 and 63, 64,
65 is the oil passage, 70 is the internal volume variable member, C is a chamber in the piston rod, G is the gas chamber of the internal volume variable member, L is the liquid chamber, and S 1 , S 2 , S 3 are oil chambers.
Claims (1)
生するバルブ機構を付設して成る油圧緩衝器にお
いて、上記ピストンを保持するピストンロツド内
に室を形成し、該室内に、気体を封入して成る内
容積可変部材を収納するとともに、上記ピストン
により２室に画成される上記シリンダ内の上部お
よび下部のそれぞれの油室と上記ピストンロツド
内の室とを連通する油路を当該ピストンロツドに
形成して成る油圧緩衝器。1. A hydraulic shock absorber in which a piston sliding in a cylinder is attached with a valve mechanism that generates a damping force, in which a chamber is formed in a piston rod that holds the piston, and gas is sealed in the chamber. The piston rod is formed with an oil passage that accommodates a variable volume member and communicates the upper and lower oil chambers in the cylinder, which are defined into two chambers by the piston, with the chamber in the piston rod. Hydraulic buffer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2607583A JPS59151648A (en) | 1983-02-18 | 1983-02-18 | Hydraulic shock absorber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2607583A JPS59151648A (en) | 1983-02-18 | 1983-02-18 | Hydraulic shock absorber |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59151648A JPS59151648A (en) | 1984-08-30 |
| JPH042826B2 true JPH042826B2 (en) | 1992-01-21 |
Family
ID=12183531
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2607583A Granted JPS59151648A (en) | 1983-02-18 | 1983-02-18 | Hydraulic shock absorber |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59151648A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2575439B2 (en) * | 1988-01-19 | 1997-01-22 | 日本発条株式会社 | accumulator |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5624313B2 (en) * | 1975-10-20 | 1981-06-05 | ||
| JPS56131410A (en) * | 1980-03-18 | 1981-10-15 | Honda Motor Co Ltd | Oil-hydraulic damper for automobile |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5624313U (en) * | 1979-08-02 | 1981-03-05 |
-
1983
- 1983-02-18 JP JP2607583A patent/JPS59151648A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5624313B2 (en) * | 1975-10-20 | 1981-06-05 | ||
| JPS56131410A (en) * | 1980-03-18 | 1981-10-15 | Honda Motor Co Ltd | Oil-hydraulic damper for automobile |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59151648A (en) | 1984-08-30 |
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