JPH024811B2 - - Google Patents
Info
- Publication number
- JPH024811B2 JPH024811B2 JP6201182A JP6201182A JPH024811B2 JP H024811 B2 JPH024811 B2 JP H024811B2 JP 6201182 A JP6201182 A JP 6201182A JP 6201182 A JP6201182 A JP 6201182A JP H024811 B2 JPH024811 B2 JP H024811B2
- Authority
- JP
- Japan
- Prior art keywords
- piston
- oil
- cylinder
- retainer
- orifice
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 230000001105 regulatory effect Effects 0.000 claims description 3
- 239000006096 absorbing agent Substances 0.000 description 10
- 230000035939 shock Effects 0.000 description 10
- 230000008602 contraction Effects 0.000 description 9
- 238000013016 damping Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 125000006850 spacer group Chemical group 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
- F16F9/516—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 resulting in the damping effects during contraction being different from the damping effects during extension, i.e. responsive to the direction of movement
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Description
【発明の詳細な説明】
本発明はシリンダ内にピストンとピストンロツ
ドとからなるピストン−ピストンロツドアセンブ
リを摺動可能に設け、該ピストン−ピストンロツ
ドアセンブリの伸長行程および縮小行程において
多段に減衰力を発生させる油圧緩衝器、ガススプ
リング等のシリンダ装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention provides a piston-piston rod assembly consisting of a piston and a piston rod in a slidable manner within a cylinder, and applies damping force in multiple stages during the extension stroke and contraction stroke of the piston-piston rod assembly. This relates to cylinder devices such as hydraulic shock absorbers and gas springs that generate .
第１図に従来技術によるシリンダ装置としての
油圧緩衝器を示す。 FIG. 1 shows a hydraulic shock absorber as a cylinder device according to the prior art.
同図において、１はシリンダで、該シリンダ１
の一端はキヤツプ２により施蓋されており、他端
にはロツドガイド３およびシール部材４が嵌着さ
れている。５はシリンダ１内に摺動可能に設けた
ピストン、６はロツドガイド３、シール部材４を
貫通してシリンダ１内に突出して設てたピストン
ロツドを示し、前記ピストンはピストンロツド６
の先端に嵌入固着されている。 In the figure, 1 is a cylinder, and the cylinder 1
One end is covered by a cap 2, and a rod guide 3 and a seal member 4 are fitted to the other end. Reference numeral 5 indicates a piston that is slidably provided within the cylinder 1; 6 indicates a piston rod that extends through the rod guide 3 and the seal member 4 and protrudes into the cylinder 1;
It is inset and fixed at the tip of the.
次に、７はシリンダ１のキヤツプ２側において
摺動可能に挿嵌されたフリーピストンで、該フリ
ーピストン７とキヤツプ２との間にはピストンロ
ツド６のシリンダ１内への進入体積分を補償する
ための気体室Ａが形成され、該気体室Ａには所定
圧力の気体が封入されている。また、フリーピス
トン７とピストン５との間およびピストン５とシ
ール部材４との間には油室Ｂ，Ｃが形成されて、
油液で満たされている。８はピストン５に穿設し
たオリフイスで、該オリフイス８により油室Ｂ，
Ｃは小さな流路面積をもつて常時連通している。 Next, reference numeral 7 denotes a free piston that is slidably fitted on the cap 2 side of the cylinder 1, and there is a space between the free piston 7 and the cap 2 to compensate for the volume of the piston rod 6 entering the cylinder 1. A gas chamber A is formed for this purpose, and gas at a predetermined pressure is sealed in the gas chamber A. Further, oil chambers B and C are formed between the free piston 7 and the piston 5 and between the piston 5 and the seal member 4,
filled with oil. 8 is an orifice bored in the piston 5, and the orifice 8 allows the oil chamber B,
C has a small flow path area and is always in communication.
なお、９，１０はそれぞれピストン５およびフ
リーピストン７に設けられたシール部材、１１，
１２はそれぞれピストン５の基端部およびキヤツ
プ２に取付けたブラケツトを示す。 In addition, 9 and 10 are seal members provided on the piston 5 and the free piston 7, respectively, and 11,
Reference numerals 12 indicate brackets attached to the base end of the piston 5 and the cap 2, respectively.
従来技術による油圧緩衝器は前述の構成を有す
るもので、ピストンロツド６に図中矢示ａ方向に
外力が加わると、ピストンロツド６はピストン５
と共に伸長する方向に変位する。このため油室Ｃ
内が高圧となつて、該油室Ｃ内の油液がオリフイ
ス８を介して油室Ｂ内に流入する。この油液がオ
リフイス８を通過する際の油圧抵抗力によつて、
ピストン５は減速せしめられる。 The hydraulic shock absorber according to the prior art has the above-mentioned configuration, and when an external force is applied to the piston rod 6 in the direction of arrow a in the figure, the piston rod 6 moves toward the piston 5.
It is also displaced in the direction of elongation. For this reason, oil chamber C
The pressure inside becomes high, and the oil in the oil chamber C flows into the oil chamber B through the orifice 8. Due to the hydraulic resistance force when this oil passes through the orifice 8,
Piston 5 is decelerated.
一方、ピストンロツド６に図中矢示ｂ方向に外
力が加わると、ピストンロツド６はピストン５と
共に縮小する方向に変位し、このとき油室Ｂ内の
油液がオリフイス８を通過して油室Ｃ内に流入す
る際の油圧抵抗力によつて、ピストン５の緩衝作
用が行なわれる。 On the other hand, when an external force is applied to the piston rod 6 in the direction of arrow b in the figure, the piston rod 6 is displaced together with the piston 5 in the direction of contraction, and at this time, the oil in the oil chamber B passes through the orifice 8 and flows into the oil chamber C. The damping effect of the piston 5 is achieved by the hydraulic resistance force upon inflow.
第２図にピストン５の速度に対する油圧抵抗力
の関係を示す。同図から明らかなように、ピスト
ン５に設けたオリフイス８の流路面積は一定であ
るから、ピストン５の速度に対する油圧抵抗力の
特性は一定で、その伸長行程、縮小行程共に同じ
である。従つて、例えばピストン５の速度が低速
域にあるときには僅かの油圧抵抗力しか生じず、
高速域になると極めて大きな油圧抵抗力を発生さ
せる必要がある等、油圧抵抗力特性をピストン５
の速度域に応じて変化させるような制御を行なう
ことは、前述の従来技術による油圧緩衝器では不
可能であつた。従つて、油圧抵抗力の特性設定に
おける自由度は限られ、油圧緩衝器の用途に応じ
て最適の特性設定を行なうことができない欠点が
あつた。また、オリフイス８は両方向に油液を流
通させるものであるから、ピストン５の速度に対
する油圧抵抗力の特性は伸長行程と縮小行程とで
は対称となつている。従つて、前述の油圧緩衝器
にあつては、例えば伸長行程において、縮小行程
より大きな油圧抵抗力を発生させるような油圧抵
抗力特性の設定を行なうのは不可能であつた。 FIG. 2 shows the relationship between the hydraulic resistance force and the speed of the piston 5. As is clear from the figure, since the flow path area of the orifice 8 provided in the piston 5 is constant, the characteristics of the hydraulic resistance force with respect to the speed of the piston 5 are constant, and are the same in both the extension stroke and the contraction stroke. Therefore, for example, when the speed of the piston 5 is in a low speed range, only a small hydraulic resistance force is generated;
At high speeds, it is necessary to generate an extremely large hydraulic resistance force, so the hydraulic resistance characteristics of the piston 5
It has been impossible to perform control such as changing the speed according to the speed range of the hydraulic shock absorber according to the prior art described above. Therefore, the degree of freedom in setting the characteristics of the hydraulic resistance force is limited, and there is a disadvantage that it is not possible to set the characteristics optimally depending on the application of the hydraulic shock absorber. Further, since the orifice 8 allows oil to flow in both directions, the characteristics of the hydraulic resistance force with respect to the speed of the piston 5 are symmetrical between the extension stroke and the contraction stroke. Therefore, in the above-mentioned hydraulic shock absorber, it has been impossible to set the hydraulic resistance characteristics such that, for example, in the extension stroke, a greater hydraulic resistance force is generated than in the contraction stroke.
本発明は前述した従来技術の欠点を解消するこ
とをその目的とするものであつて、その特徴とす
るところは、ピストンをピストンロツドの軸方向
に移動可能に挿嵌し、前記ピストンロツドには前
記ピストンの移動範囲を規制する一対のリテーナ
を設け、前記ピストンには２個の油室間を連通す
る絞り通路を設け、前記ピストンには前記リテー
ナ側への移動に対して抵抗力を与える付勢手段を
設け、前記ピストンが前記リテーナに当接したと
き前記絞り通路を開閉しうる弾性部材を設け、前
記絞り通路が前記弾性部材によつて閉じられてい
るとき前記各油室間に油液を流すオリフイスを設
けたことにより、ピストンがリテーナに当接する
前後および弾性部材が絞り通路を開閉する前後に
おいて、それぞれ油圧抵抗力の特性を３段に変化
させることができるようにしたシリンダ装置を提
供することにある。 The present invention aims to solve the above-mentioned drawbacks of the prior art, and is characterized in that a piston is fitted into a piston rod so as to be movable in the axial direction, and the piston a pair of retainers are provided for regulating the movement range of the piston, the piston is provided with a throttle passage that communicates between the two oil chambers, and the piston is provided with an urging means that provides a resistance force against movement toward the retainer. and an elastic member capable of opening and closing the throttle passage when the piston abuts the retainer, and when the throttle passage is closed by the elastic member, oil fluid flows between the oil chambers. To provide a cylinder device in which the characteristic of hydraulic resistance force can be changed in three stages before and after a piston contacts a retainer and before and after an elastic member opens and closes a throttle passage by providing an orifice. It is in.
以下、第３図ないし第８図に基づき本発明の実
施例について説明する。 Embodiments of the present invention will be described below with reference to FIGS. 3 to 8.
まず、第３図において、第１図と同一構成要素
については同一符号を付してその説明を省略する
ものとするに、ピストンロツド２１のシリンダ１
内側の先端部には小径部２１Ａが形成されてお
り、該小径部２１Ａにはカラー２２が嵌合される
と共に、該カラー２２の両端部とピストンロツド
２１の段部２１Ｂおよびカシメ手段で形成された
先端突出部２１Ｃとの間にはカラー２２を挾んで
リテーナ２３，２４、１枚のデイスクで形成した
弾性部材２５と２枚のデイスクからなる弾性部材
２６、スペーサ２７，２８、ストツパ２９，３０
がそれぞれ介装されており、これらの各部材はい
ずれもシリンダ１内径より小径に形成されてい
る。 First, in FIG. 3, the same components as those in FIG.
A small diameter portion 21A is formed at the inner tip, and a collar 22 is fitted into the small diameter portion 21A, and is formed by both ends of the collar 22, a stepped portion 21B of the piston rod 21, and a caulking means. Retainers 23 and 24 sandwich the collar 22 between the tip protrusion 21C, an elastic member 25 formed of one disk and an elastic member 26 formed of two disks, spacers 27 and 28, and stoppers 29 and 30.
are interposed, and each of these members is formed to have a smaller diameter than the inner diameter of the cylinder 1.
３１はカラー２２に嵌合されたピストンで、該
ピストン３１はシリンダ１の内壁に沿つて摺動す
ると共に、カラー２２上を各リテーナ２３，２４
に当接する位置までピストンロツド２１の軸方向
に移動することができるようになつている。そし
て、ピストン３１の内周側は短尺部３１Ａとなつ
ていると共に、外周側は長尺部３１Ｂとなつてお
り、該短尺部３１Ａと長尺部３１Ｂとの境界部に
は段部３１Ｃ，３１Ｄが形成されている。しか
も、ピストン３１の外周面側には両側面との角隅
部を切欠くことにより凹部３１Ｅ，３１Ｆが形成
されている。また、ピストン３１の短尺部３１Ａ
には段部３１Ｃ，３１Ｄとカラー２２外周面との
間に形成される環状溝３１Ｇ，３１Ｈにそれぞれ
開口する絞り通路３２が穿設されており、該絞り
通路３２はピストン３１がリテーナ２３，２４か
ら離間しているときには油室Ｂ，Ｃ間を油圧抵抗
力を発生させながら連通し、ピストン３１がリテ
ーナ２３または２４と当接したときには、絞り通
路３２と油室ＢまたはＣとの連通が遮断されるよ
うに構成されている。３３，３４はオリフイス
で、該各オリフイス３３，３４の一端はピストン
３１の凹部３１Ｅ，３１Ｆに開口し、その他端は
絞り通路３２内の中間部位に開口し、該絞り通路
３２を介してそれぞれ油室Ｂ，Ｃと常時連通して
いる。そして、オリフイス３３は絞り通路３２よ
り小径となつており、またオリフイス３４はオリ
フイス３３よりさらに小径に形成されている。 A piston 31 is fitted into the collar 22, and the piston 31 slides along the inner wall of the cylinder 1 and slides on the collar 22 between the retainers 23 and 24.
The piston rod 21 can be moved in the axial direction to a position where it comes into contact with the piston rod 21. The inner circumferential side of the piston 31 is a short part 31A, and the outer circumferential side is a long part 31B, and the boundary between the short part 31A and the long part 31B has step parts 31C and 31D. is formed. Furthermore, recesses 31E and 31F are formed on the outer circumferential surface of the piston 31 by cutting out corner portions with both side surfaces. In addition, the short portion 31A of the piston 31
Throttle passages 32 are formed in the annular grooves 31G and 31H formed between the step portions 31C and 31D and the outer peripheral surface of the collar 22, respectively, and the piston 31 is connected to the retainers 23 and 24. When the piston 31 is separated from the retainer 23 or 24, the communication between the oil chambers B and C occurs while generating a hydraulic resistance force, and when the piston 31 comes into contact with the retainer 23 or 24, the communication between the throttle passage 32 and the oil chamber B or C is cut off. is configured to be Reference numerals 33 and 34 denote orifices, one end of each orifice 33 and 34 opens into the concave portions 31E and 31F of the piston 31, and the other end opens into an intermediate portion within the throttle passage 32, and oil is supplied through the throttle passage 32, respectively. It is in constant communication with rooms B and C. The orifice 33 has a smaller diameter than the throttle passage 32, and the orifice 34 has an even smaller diameter than the orifice 33.
３５，３６はそれぞれピストン３１の各段部３
１Ｃ，３１Ｄとリテーナ２３，２４との間に張設
された付勢手段としてのコイルばねで、該各コイ
ルばね３５，３６により、ピストン３１はその中
立位置においてはリテーナ２３，２４からそれぞ
れ所定の距離だけ離間した状態に保持されてい
る。そして、各コイルばね３５，３６はピストン
３１が油室Ｂ，Ｃ間の差圧によつてリテーナ２３
または２４側に移動するときに、その移動に対し
て抵抗力を与える機能を有するものである。 35 and 36 are respective step portions 3 of the piston 31
Coil springs as biasing means are stretched between 1C and 31D and retainers 23 and 24, and the coil springs 35 and 36 cause the piston 31 to release a predetermined amount from the retainers 23 and 24 in its neutral position. They are kept a distance apart. Then, each coil spring 35, 36 is connected to the retainer 23 by the piston 31 due to the differential pressure between the oil chambers B, C.
Alternatively, it has a function of providing resistance to the movement when it moves to the 24 side.
さらに、各リテーナ２３，２４はそれぞれスト
ツパ２９，３０に対面する背面側には環状凹部２
３Ａ，２４Ａが形成され、また、該各リテーナ２
３，２４には環状溝３１Ｇ，３１Ｈに一側が開口
し、他側が環状凹部２３Ａ，２４Ａに開口する油
穴３７，３８が穿設されている。各環状凹部２３
Ａ，２４Ａは常時には弾性部材２５，２６によつ
て閉塞されており、油室Ｂ，Ｃ間の差圧が所定値
以上となつたときには、環状凹部２３Ａ，２４Ａ
に作用する液圧で弾性部材２５，２６がそれぞれ
ストツパ２９，３０側に弾性変形してリテーナ２
３，２４から離間せしめられ、弾性部材２５，２
６とリテーナ２３，２４との間には環状通路３
９，４０が形成される（第７図、第５図参照）。 Furthermore, each of the retainers 23 and 24 has an annular recess 2 on the back side facing the stoppers 29 and 30, respectively.
3A and 24A are formed, and each retainer 2
3 and 24 are provided with oil holes 37 and 38, which open on one side to the annular grooves 31G and 31H and open on the other side to the annular recesses 23A and 24A. Each annular recess 23
A, 24A are normally closed by elastic members 25, 26, and when the differential pressure between oil chambers B, C exceeds a predetermined value, annular recesses 23A, 24A are closed.
The elastic members 25 and 26 are elastically deformed toward the stoppers 29 and 30, respectively, by the hydraulic pressure acting on the retainer 2.
3, 24, and the elastic members 25, 2
An annular passage 3 is provided between the retainer 6 and the retainers 23 and 24.
9 and 40 are formed (see FIGS. 7 and 5).
本発明に係るシリンダ装置は前述の構成を有す
るもので、次にその作動について説明する。 The cylinder device according to the present invention has the above-mentioned configuration, and its operation will be explained next.
まず、ピストンロツド２１に外力が作用し、図
中矢示ａ方向に変位せしめられると、伸長行程が
開始する。このため、ピストン３１はシリンダ１
内をピストンロツド２１と共に矢示ａ方向に摺動
変位する。従つて、油室Ｃは高圧となつて、該油
室Ｃ内の油液は絞り通路３２を流通する際に発生
する油圧抵抗力によりピストン３１の減速作用が
行なわれる。ところで、油室Ｃ内が高圧になる
と、ピストン３１はその油圧力によつてリテーナ
２４側に押動せしめられるが、ピストン３１とリ
テーナ２４との間にはコイルばね３６が張設され
ているから、該コイルばね３６の付勢力がピスト
ン３１の移動に対する抵抗力となる。 First, when an external force is applied to the piston rod 21 and the piston rod 21 is displaced in the direction of arrow a in the figure, an extension stroke begins. Therefore, the piston 31 is in the cylinder 1
The piston rod 21 is slid inside the piston rod 21 in the direction of arrow a. Therefore, the pressure in the oil chamber C is high, and the hydraulic resistance force generated when the oil in the oil chamber C flows through the throttle passage 32 causes the piston 31 to be decelerated. By the way, when the pressure inside the oil chamber C becomes high, the piston 31 is pushed toward the retainer 24 by the oil pressure, but since a coil spring 36 is stretched between the piston 31 and the retainer 24. The biasing force of the coil spring 36 acts as a resistance force against the movement of the piston 31.
然るに、ピストン３１の速度が増大すると、油
室Ｃ内の圧力も増大し、油室Ｃと油室Ｂとの間の
差圧が拡大することになる。このため、ピストン
３１はコイルばね３６を撓めながら徐々にリテー
ナ２４に近接する方向へ移動し、油室Ｂ，Ｃ間の
差圧がコイルばね３６のばね力faより大きくなつ
たときに、ピストン３１がリテーナ２４と当接し
た第４図の状態となる。このために、絞り通路３
２と油室Ｂとの連通が遮断され、油室Ｃ内の油液
は絞り通路３２を介してオリフイス３４から油室
Ｂ内に流入することになる。該オリフイス３４の
流路面積は絞り通路３２より小さいものであるか
ら、大きな油圧抵抗力を発生させることができ
る。 However, when the speed of the piston 31 increases, the pressure within the oil chamber C also increases, and the differential pressure between the oil chamber C and the oil chamber B increases. Therefore, the piston 31 gradually moves toward the retainer 24 while bending the coil spring 36, and when the differential pressure between the oil chambers B and C becomes larger than the spring force fa of the coil spring 36, the piston 31 moves toward the retainer 24. 31 is in contact with the retainer 24 as shown in FIG. 4. For this purpose, the throttle passage 3
2 and the oil chamber B is cut off, and the oil in the oil chamber C flows into the oil chamber B from the orifice 34 via the throttle passage 32. Since the flow path area of the orifice 34 is smaller than that of the throttle passage 32, a large hydraulic resistance force can be generated.
そして、ピストン３１の速度がさらに高速にな
ると、油室Ｃ内の油液がさらに高圧となつて、こ
の高圧油は絞り通路３２、環状溝３１Ｈ、油穴３
８を介して環状凹部２４Ａに供給され、弾性部材
２６を押動させることになる。そして、この環状
凹部２４Ａに作用する油圧力が弾性部材２６のば
ね力FAより大きくなつたときに、弾性部材２６
が弾性変形してリテーナ２４から離間し、環状通
路４０が形成されるから、油室Ｃから油室Ｂへの
油液の流量はオリフイス３４と環状通路４０との
和となる。従つて、流量が増加するから、油圧抵
抗力の増加率が減少し、その特性が再び変化す
る。 When the speed of the piston 31 becomes higher, the pressure of the oil in the oil chamber C becomes higher, and this high-pressure oil flows through the throttle passage 32, the annular groove 31H, and the oil hole 3.
8 to the annular recess 24A, thereby pushing the elastic member 26. When the hydraulic pressure acting on this annular recess 24A becomes larger than the spring force F A of the elastic member 26, the elastic member 26
is elastically deformed and separated from the retainer 24 to form an annular passage 40, so the flow rate of the oil from the oil chamber C to the oil chamber B is the sum of the orifice 34 and the annular passage 40. Therefore, since the flow rate increases, the rate of increase of the hydraulic resistance force decreases and its characteristics change again.
一方、ピストンロツド２１に外力が作用して図
中矢示ｂ方向に変位すると、縮小行程となる。そ
して、ピストン３１はピストンロツド２１と共に
矢示ｂ方向に摺動変位せしめられる。このとき
に、油室Ｂ内の油液が絞り通路３２を介して油室
Ｃ内に流入する際に生じる油圧抵抗力により、ピ
ストン３１の緩衝作用が行なわれる。そして、油
室Ｂ，Ｃ間の差圧がコイルばね３５のばね力fbよ
り大きくなると、ピストン３１がリテーナ２３と
当接せしめられ、絞り通路３２と油室Ｃとの連通
が遮断されて、第６図に示したように、油室Ｂ内
の油液は絞り通路３２を介してオリフイス３３を
介して油室Ｃ内に流入することになる。該オリフ
イス３３は絞り通路３２より小さな流路面積を有
するものであるから油圧抵抗力が大きくなる。 On the other hand, when an external force acts on the piston rod 21 and the piston rod 21 is displaced in the direction of arrow b in the figure, the piston rod 21 enters a contraction stroke. Then, the piston 31 is slidably displaced together with the piston rod 21 in the direction of arrow b. At this time, the hydraulic resistance force generated when the oil in the oil chamber B flows into the oil chamber C through the throttle passage 32 causes a buffering effect on the piston 31. Then, when the differential pressure between the oil chambers B and C becomes larger than the spring force f b of the coil spring 35, the piston 31 comes into contact with the retainer 23, and communication between the throttle passage 32 and the oil chamber C is cut off. As shown in FIG. 6, the oil in the oil chamber B flows into the oil chamber C through the throttle passage 32 and the orifice 33. Since the orifice 33 has a flow path area smaller than that of the throttle passage 32, the hydraulic resistance force becomes large.
さらに、ピストン３１の摺動変位が高速になる
と、第７図に示したように、油室Ｂ内の油液が絞
り通路３２、油穴３７、環状凹部２３Ａを介して
弾性部材２５に作用し、この油圧力が弾性部材２
５のばね力FBより大きくなつたときに弾性部材
２５が弾性変形して環状通路４０が形成される。
従つて、油室Ｂから油室Ｃに流れる油液の流量は
オリフイス３３と環状通路３９との和となり、流
量が増加して油圧抵抗力の増加率が減少し、その
特性が再び変化する。 Furthermore, when the sliding displacement of the piston 31 becomes high speed, the oil in the oil chamber B acts on the elastic member 25 through the throttle passage 32, the oil hole 37, and the annular recess 23A, as shown in FIG. , this hydraulic pressure causes the elastic member 2
When the spring force becomes larger than the spring force F B of 5, the elastic member 25 is elastically deformed and the annular passage 40 is formed.
Therefore, the flow rate of the oil flowing from the oil chamber B to the oil chamber C becomes the sum of the flow rate of the orifice 33 and the annular passage 39, the flow rate increases, the rate of increase in hydraulic resistance decreases, and its characteristics change again.
次に、ピストン３１の速度と油圧抵抗力との関
係を第８図に示す。同図から明らかなように、ピ
ストン３１の低速域では流路面積は伸長行程、縮
小行程ともに主として絞り通路３２であるから、
油圧抵抗力は点Ｍ，Ｎまでピストン３１の速度に
応じて漸増し、その特性はほぼ対称となつてい
る。そして、ピストン３１の高速域では絞り通路
３２は閉塞されて、流路面積はオリフイス３３，
３４となり、急激に油圧抵抗力が増大し、その特
性は点Ｍ，Ｎ以後変化する。この場合、オリフイ
ス３４はオリフイス３３より小径となつているか
ら、伸長行程における油圧抵抗力の増加の割合の
方が縮小行程におけるそれより大きい。しかも、
ピストン３１の速度がさらに高速となると、弾性
部材２５，２６が弾性変形し、環状通路３９，４
０が形成されるから、点Ｐ，Ｑ以後に油圧抵抗力
特性がさらに変化し、その増加の割合は間お
よび間よりも少なくなる。従つて、絞り通路
３２、オリフイス３３，３４の流路面積およびコ
イルばね３５，３６および弾性部材２５，２６ば
ね力を適宜設定すれば、所望の油圧抵抗力の特性
を得ることができる。 Next, FIG. 8 shows the relationship between the speed of the piston 31 and the hydraulic resistance force. As is clear from the figure, in the low speed range of the piston 31, the flow path area is mainly the throttle passage 32 in both the extension stroke and the contraction stroke.
The hydraulic resistance force gradually increases up to points M and N according to the speed of the piston 31, and its characteristics are almost symmetrical. In the high speed range of the piston 31, the throttle passage 32 is closed, and the flow passage area is reduced to the orifice 33,
34, the hydraulic resistance suddenly increases, and its characteristics change after points M and N. In this case, since the orifice 34 has a smaller diameter than the orifice 33, the rate of increase in the hydraulic resistance force during the extension stroke is greater than that during the contraction stroke. Moreover,
When the speed of the piston 31 becomes higher, the elastic members 25 and 26 are elastically deformed, and the annular passages 39 and 4
0 is formed, the hydraulic resistance force characteristics further change after points P and Q, and the rate of increase is smaller than between and between. Therefore, by appropriately setting the flow area of the throttle passage 32, the orifices 33, 34, and the spring forces of the coil springs 35, 36 and the elastic members 25, 26, desired hydraulic resistance characteristics can be obtained.
なお、前述の実施例では、本発明に係るシリン
ダ装置を油圧緩衝器として使用する場合につき述
べたが、ガススプリングとしても用いることがで
きるのは勿論である。また、カラー２２はピスト
ン３１の移動を円滑にするためのもので、ピスト
ン３１をピストンロツド２１上に直接嵌合する構
成としてもよい。一方、ピストンロツド２１に小
径部２１Ａおよび段部２１Ｂを形成しない場合に
は、ストツパ２９，３０をＣ輪等の手段で保持さ
せてもよく、またＣ輪を用いる場合には先端突出
部２１Ｃを形成する必要はない。さらに、絞り通
路３２は短尺部３１Ａに形成する必要はなく、長
尺部３１Ｂに形成してもよい。この場合、油穴３
７，３８を絞り通路３２と対面させ、当該対面部
位のピストン３１またはリテーナ２３，２４に環
状の溝を形成させておくのが好ましい。そして、
絞り通路３２、オリフイス３３，３４はいずれも
１個に限るものではなく、さらにオリフイス３
３，３４は同径であつても、オリフイス３３の方
が小径であつてもよく、また弾性部材２５，２６
の枚数やばね力も同じであつても異なつていても
よい。 In the above-mentioned embodiments, the case where the cylinder device according to the present invention is used as a hydraulic shock absorber has been described, but it goes without saying that it can also be used as a gas spring. Further, the collar 22 is for smooth movement of the piston 31, and the piston 31 may be directly fitted onto the piston rod 21. On the other hand, if the piston rod 21 is not formed with the small diameter portion 21A and the stepped portion 21B, the stoppers 29, 30 may be held by C-rings or other means, and if a C-ring is used, a tip protruding portion 21C is formed. do not have to. Furthermore, the throttle passage 32 does not need to be formed in the short part 31A, and may be formed in the long part 31B. In this case, oil hole 3
It is preferable that the pistons 7 and 38 face the throttle passage 32, and an annular groove is formed in the piston 31 or the retainers 23 and 24 at the facing portions. and,
The number of the throttle passage 32 and the orifices 33 and 34 is not limited to one, and the orifice 3
3 and 34 may have the same diameter, or the orifice 33 may have a smaller diameter, and the elastic members 25 and 26 may have the same diameter.
The number of sheets and the spring force may be the same or different.
さらにまた、ブラケツト１２を上方に取付ける
構成とすれば、フリーピストン７は必ずしも設け
る必要はない。 Furthermore, if the bracket 12 is mounted upwardly, the free piston 7 is not necessarily required.
以上詳細に述べた如く、本発明に係るシリンダ
装置によれば、ピストンをピストンロツドの軸方
向に移動可能に挿嵌し、前記ピストンロツドには
前記ピストンの移動範囲を規制する一対のリテー
ナを設け、前記ピストンには２個の油室間を連通
する絞り通路を設け、前記ピストンには前記リテ
ーナ側への移動に対して抵抗力を与える付勢手段
を設け、前記ピストンが前記リテーナに当接した
とき前記絞り通路を開閉しうる弾性部材を設け、
前記絞り通路が前記弾性部材によつて閉じられて
いるとき前記各油室間に油液を流すオリフイスを
設けた構成としたから、ピストンの速度に応じて
両油室間の流路を絞り通路による場合と、オリフ
イスによる場合と、オリフイスと油穴による場合
との３段で油圧抵抗力の特性を変化させることが
でき、シリンダ装置の用途により所望の油圧抵抗
力特性が得ることができる。また、オリフイスの
流路面積および弾性部材のばね力を相異なるよう
に形成しておけば、リテーナによる絞り通路閉塞
後の油圧抵抗力特性を伸長行程と縮小行程とでは
異なるように形成することもできる。 As described in detail above, according to the cylinder device according to the present invention, the piston is fitted into the piston rod so as to be movable in the axial direction, the piston rod is provided with a pair of retainers for regulating the movement range of the piston, and the piston is fitted into the piston rod so as to be movable in the axial direction. The piston is provided with a throttle passage that communicates between the two oil chambers, and the piston is provided with an urging means that provides a resistance force against movement toward the retainer, and when the piston comes into contact with the retainer. providing an elastic member capable of opening and closing the throttle passage;
Since an orifice is provided for flowing oil between the oil chambers when the throttle passage is closed by the elastic member, the flow passage between the oil chambers is throttled depending on the speed of the piston. The characteristics of the hydraulic resistance force can be changed in three stages: when using an orifice, when using an orifice and an oil hole, and desired hydraulic resistance characteristics can be obtained depending on the use of the cylinder device. Furthermore, if the flow path area of the orifice and the spring force of the elastic member are made different, it is possible to make the hydraulic resistance characteristics different in the extension stroke and the contraction stroke after the restriction passage is closed by the retainer. can.
第１図は従来技術によるシリンダ装置としての
油圧緩衝器を示す縦断面図、第２図は第１図の油
圧緩衝器のピストン速度に対する油圧抵抗力特性
を示す線図、第３図ないし第８図は本発明の実施
例を示すもので、第３図はシリンダ装置としての
油圧緩衝器の縦断面図、第４図ないし第７図はそ
れぞれ異なる作動状態を示す第３図の部分拡大
図、第８図はピストン速度に対する油圧抵抗力特
性を示す線図である。
１…シリンダ、２１…ピストンロツド、２３，
２４…リテーナ、２５，２６…弾性部材、３１…
ピストン、３２…絞り通路、３３，３４…オリフ
イス、３５，３６…コイルばね、３７，３８…油
穴、Ｂ，Ｃ…油室。
FIG. 1 is a vertical sectional view showing a hydraulic shock absorber as a cylinder device according to the prior art, FIG. 2 is a diagram showing hydraulic resistance characteristics with respect to piston speed of the hydraulic shock absorber shown in FIG. 1, and FIGS. The figures show an embodiment of the present invention; FIG. 3 is a longitudinal sectional view of a hydraulic shock absorber as a cylinder device; FIGS. 4 to 7 are partially enlarged views of FIG. 3 showing different operating states; FIG. 8 is a diagram showing hydraulic resistance force characteristics with respect to piston speed. 1...Cylinder, 21...Piston rod, 23,
24...Retainer, 25, 26...Elastic member, 31...
Piston, 32... Throttle passage, 33, 34... Orifice, 35, 36... Coil spring, 37, 38... Oil hole, B, C... Oil chamber.
Claims (1)
設け、該ピストンロツドのシリンダ内端には前記
シリンダ内を摺動し該シリンダ内を２個の油室に
画成するピストンを前記ピストンロツドの軸方向
に移動可能に挿嵌し、前記ピストンロツドには前
記ピストンの移動範囲を規制する一対のリテーナ
を設け、前記ピストンには前記各油室間を連通す
る絞り通路を設け、前記ピストンには前記リテー
ナ側への移動に対して抵抗力を与える付勢手段を
設け、前記ピストンが前記リテーナに当接したと
き前記絞り通路を開閉しうる弾性部材を設け、前
記絞り通路が前記弾性部材によつて閉じられてい
るとき前記各油室間に油液を流すオリフイスを設
けたシリンダ装置。 ２ 前記付勢手段はリテーナとピストンとの間に
配設されたコイルばねであり、前記弾性部材はデ
イスクである特許請求の範囲１項記載のシリンダ
装置。[Scope of Claims] 1. A piston rod is provided in the cylinder to protrude, and at the inner end of the cylinder there is a piston that slides in the cylinder and defines the inside of the cylinder into two oil chambers. The piston rod is provided with a pair of retainers for regulating the range of movement of the piston, the piston is provided with a restriction passage that communicates between the oil chambers, and the piston is provided with a pair of retainers that restrict the movement range of the piston. A biasing means that provides a resistance force against movement toward the retainer is provided, an elastic member is provided that can open and close the throttle passage when the piston comes into contact with the retainer, and the throttle passage is opened and closed by the elastic member. The cylinder device is provided with an orifice that allows oil to flow between the oil chambers when the cylinder is closed. 2. The cylinder device according to claim 1, wherein the biasing means is a coil spring disposed between the retainer and the piston, and the elastic member is a disk.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6201182A JPS58180847A (en) | 1982-04-14 | 1982-04-14 | Cylinder apparatus |
| GB08309523A GB2122305B (en) | 1982-04-10 | 1983-04-08 | Fluid spring or damper with slidable piston |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6201182A JPS58180847A (en) | 1982-04-14 | 1982-04-14 | Cylinder apparatus |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58180847A JPS58180847A (en) | 1983-10-22 |
| JPH024811B2 true JPH024811B2 (en) | 1990-01-30 |
Family
ID=13187780
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6201182A Granted JPS58180847A (en) | 1982-04-10 | 1982-04-14 | Cylinder apparatus |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58180847A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4932531B2 (en) * | 2007-02-23 | 2012-05-16 | カヤバ工業株式会社 | Buffer valve structure |
-
1982
- 1982-04-14 JP JP6201182A patent/JPS58180847A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58180847A (en) | 1983-10-22 |
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