JPS62266241A - Damping force regulating device for hydraulic shock absorber - Google Patents
Damping force regulating device for hydraulic shock absorberInfo
- Publication number
- JPS62266241A JPS62266241A JP10833586A JP10833586A JPS62266241A JP S62266241 A JPS62266241 A JP S62266241A JP 10833586 A JP10833586 A JP 10833586A JP 10833586 A JP10833586 A JP 10833586A JP S62266241 A JPS62266241 A JP S62266241A
- Authority
- JP
- Japan
- Prior art keywords
- valve
- port
- pressure
- damping force
- drive gear
- 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.)
- Pending
Links
- 238000013016 damping Methods 0.000 title claims abstract description 38
- 239000006096 absorbing agent Substances 0.000 title claims abstract description 17
- 230000035939 shock Effects 0.000 title claims abstract description 17
- 230000001105 regulatory effect Effects 0.000 title 1
- 230000006835 compression Effects 0.000 claims description 7
- 238000007906 compression Methods 0.000 claims description 7
- 125000006850 spacer group Chemical group 0.000 description 3
- 241001609030 Brosme brosme Species 0.000 description 1
- 238000005336 cracking Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004519 manufacturing process Methods 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
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
- F16F9/466—Throttling control, i.e. regulation of flow passage geometry
- F16F9/467—Throttling control, i.e. regulation of flow passage geometry using rotary valves
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は路面からの衝撃エネルギーを吸収、緩和させる
二輪車、四輪車等の油圧緩衝器における減衰力調整装置
に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a damping force adjusting device for a hydraulic shock absorber for two-wheeled vehicles, four-wheeled vehicles, etc., which absorbs and alleviates impact energy from a road surface.
この種従来の油圧緩衝器として牙５図に示す構造のもの
が知られている。As a conventional hydraulic shock absorber of this kind, one having a structure shown in Fig. 5 is known.
これはシリンダ１内にピストン２を介してピストンロッ
ド３が移動自在に挿入され、ピストン２はシリンダ内に
上下二つの油室Ａ、Ｂを区画し、シリンダ１の外周には
リザーバ室Ｃが区画されている。A piston rod 3 is movably inserted into a cylinder 1 via a piston 2, and the piston 2 defines two upper and lower oil chambers A and B within the cylinder, and a reservoir chamber C is defined on the outer periphery of the cylinder 1. has been done.
ピストン２には二つの油室Ａ、Ｂを連通ずル伸ポート４
と圧ポート５が穿たれ、伸ポート４の吐出側口端にはス
プリングで付勢されている伸バルブ６が開閉自在に設け
られ、同じく圧ポート５の口端には圧バルブ７が設けら
れている。The piston 2 has an extension port 4 that communicates the two oil chambers A and B.
A pressure port 5 is bored, and a spring-biased expansion valve 6 is provided at the outlet end of the expansion port 4 so as to be openable and closable, and a pressure valve 7 is also provided at the mouth end of the pressure port 5. ing.
ピストンロッド３には油室Ａ、Ｂを連通する連通孔１３
と通路１４が形成され、ピストンロッド３内に回転自在
に挿入されたロータリバルブには可変オリフィス１０が
形成され、ロータリバルブは外部からコントロールロッ
ド１５を介して回転操作される。The piston rod 3 has a communication hole 13 that communicates the oil chambers A and B.
A variable orifice 10 is formed in a rotary valve rotatably inserted into the piston rod 3, and the rotary valve is rotatably operated from the outside via a control rod 15.
ピストンロッド３の下端にはピストン等を締め付は保持
するピストンナツト１６が設けられ、このピストンナツ
ト１６には、通路１４に対向する伸オリフィスとチェッ
クバルブが組み込まれている。A piston nut 16 is provided at the lower end of the piston rod 3 for tightening and holding a piston, etc., and this piston nut 16 has an extension orifice facing the passage 14 and a check valve incorporated therein.
シリンダ１の下部にはベースバルブが設けられている。A base valve is provided at the bottom of the cylinder 1.
上記の油圧緩衝器では可変オリフィス１０が閉じており
、その時の伸長時にはピストン２が左行し、油室Ａの油
が伸ポート４より伸バルブ６を撓わませて油室Ｂに流れ
、その時の抵抗により油室Ａ、Ｂ間に差圧が発生し、伸
バルブ６による伸側高減衰力が発生する。この際ピスト
ンロッド３の排出体積分の油量がリザーバ室Ｃよりベー
スバルブを介して油［Ｂに供給される。In the above hydraulic shock absorber, the variable orifice 10 is closed, and during expansion, the piston 2 moves to the left, and the oil in the oil chamber A deflects the expansion valve 6 from the expansion port 4 and flows into the oil chamber B. Due to this resistance, a differential pressure is generated between the oil chambers A and B, and a high expansion-side damping force is generated by the expansion valve 6. At this time, the amount of oil corresponding to the discharge volume of the piston rod 3 is supplied from the reservoir chamber C to the oil [B] via the base valve.
他方、圧縮時にはピストン２が右行し、油室Ｂの油が圧
ポート５より圧バルブ７を撓わませて油室Ａに流れ、そ
の時油室Ａ、Ｂ間に差圧が発生するから圧側時の高減衰
力が発生する。この際ピストンロッド３の侵入量体積分
の油はベースバルブより油室Ｂの油をリザーバＣに戻す
が、ベースバルブの抵抗で油室Ｂの圧力は上昇すると共
にベースバルブによる減衰力も発生する。On the other hand, during compression, the piston 2 moves to the right, and the oil in the oil chamber B bends the pressure valve 7 from the pressure port 5 and flows into the oil chamber A. At this time, a differential pressure is generated between the oil chambers A and B, so the pressure side High damping force occurs when At this time, the oil corresponding to the volume of the intrusion of the piston rod 3 returns the oil in the oil chamber B to the reservoir C from the base valve, but the pressure in the oil chamber B increases due to the resistance of the base valve, and a damping force is also generated by the base valve.
更にコントロールロッド１５を回転し、可変オリフィス
１０を連通孔１３に開口すると、伸長時には前記の伸バ
ルブ４を流れる流路に加え、可変オリフィス１０から通
路１４を通り、ピストンナツト１６内の伸オリフィスよ
り油室Ｂに油が流れる。従って、前記の場合に比べて抵
抗が小さくなり、油室Ａ、Ｂ間の差圧も小さくなり、低
減衰力が発生することになる。この場合、通常ピストン
ナツト内の伸オリフィスの方が可程の低減衰力はこの伸
オリフィスにより制御される。When the control rod 15 is further rotated and the variable orifice 10 is opened to the communication hole 13, in addition to the flow path through the expansion valve 4 during expansion, the flow from the variable orifice 10 passes through the passage 14 and from the expansion orifice in the piston nut 16. Oil flows into oil chamber B. Therefore, compared to the above case, the resistance is smaller, the differential pressure between the oil chambers A and B is also smaller, and a lower damping force is generated. In this case, the expansion orifice in the piston nut usually controls the lower damping force, which is much lower than the expansion orifice.
次に圧縮行程時には前記の圧バルブ７を通る流路に加え
、通路１４と可変オリフィス１３を通る流れが発生し、
その結果前記の高減衰力に比べて抵抗が小さくなり、油
室Ａ、Ｂ間の差圧も小さくなり、低減衰力が発生する。Next, during the compression stroke, in addition to the flow path passing through the pressure valve 7, a flow is generated through the passage 14 and the variable orifice 13,
As a result, the resistance becomes smaller than the above-mentioned high damping force, and the differential pressure between the oil chambers A and B also becomes smaller, so that a low damping force is generated.
この時の減衰力は可変オリフィス１３により主に制御さ
れる。The damping force at this time is mainly controlled by the variable orifice 13.
上記の油圧緩衝器における減衰力特性は牙６図に示され
、可変オリフィス１３を閉じた時の高減衰力特性はグラ
フαｌ、αコで示され、可変オリフィス１３を開いた時
の低減衰力特性はグラフ’／ ＊ ’Ｊで示される。即
ち、ピストンの低速領域では伸バルブ４、圧バルブ７を
バイパスするオリフィスの面積が変更されて２乗特性の
発生減衰力は比較的大巾に変えられるが、伸バルブ・１
、圧バルブ７のクラッキング設定圧は圧力−ｉＭ帯Ｆ？
＞？Ｉｘわち刊１−中の１−安シ、？？ｔハム イ由
バルブ４、圧バルブ７が開くまではピストン速度（又は
油の流量）に対し減衰力（又は油量Ａ。The damping force characteristics of the above hydraulic shock absorber are shown in Figure 6, the high damping force characteristics when the variable orifice 13 is closed are shown by graphs αl and α, and the low damping force when the variable orifice 13 is open. The characteristics are shown in the graph '/*'J. That is, in the low speed region of the piston, the area of the orifice that bypasses the expansion valve 4 and the pressure valve 7 is changed, and the generated damping force of the square characteristic can be changed relatively widely.
, the cracking set pressure of pressure valve 7 is pressure - iM band F?
＞? Ix Wachikan 1-Naka no 1-Anshi,? ? Until the valve 4 and pressure valve 7 open, the damping force (or oil amount A) is proportional to the piston speed (or oil flow rate).
８間の差圧）は２乗特性となってもバルブ４又は７が開
いた後のバルブ特性についてはグラフｈ、 、 ｈ−の
如くとなり、ピストン速度の中速、或は高速域では高減
衰力特性αｌ、αコに比べてそれ程大きな差は無い。従
って自動車の乗心地′面においても、荒れた路面や悪路
等の速いピストン速度が発生する状況では所望通りの低
減衰力が得られないという問題がある。更に低速域なる
為に、ソフトな減衰力設定時には”だれ。Even if the differential pressure between valves 8 and 8 is a square characteristic, the valve characteristics after valve 4 or 7 open are as shown in graphs h, , h-, and high damping occurs in the medium or high piston speed range. There is not that much difference compared to the force characteristics αl and αko. Therefore, in terms of the ride comfort of an automobile, there is a problem in that the desired low damping force cannot be obtained in situations where high piston speeds occur, such as on rough or rough roads. Furthermore, since it is in the low speed range, when setting the damping force to a soft level, there is a ``slop''.
によるふわふわ状態が著しくなり、腰があって然もソフ
トであるという背反設定ができないという問題もある。There is also the problem that it becomes extremely fluffy, and it is not possible to set the product to be soft even though it has a waist.
従って本発明の目的は低速域では２乗特性から２／３乗
特性に変えることができて減衰不足感を解消し、文中、
高速域での減衰力設定時を大きくとれるようにした油圧
緩衝器の減衰力調整装置を提供することである。Therefore, the purpose of the present invention is to eliminate the feeling of insufficient damping by changing from the square power characteristic to the 2/3 power characteristic in the low speed range.
To provide a damping force adjusting device for a hydraulic shock absorber which allows a large damping force setting time in a high speed range.
上記の目的を達成するため、本考案の構成は、各伸ポー
トと圧ポートとに対して、各ポートとクロスする方向に
ロータリバルブを回転自在に挿入させ、各ロータリバル
ブにはバルブ用ギヤが一体にそれぞれ接続され、各バル
ブ用ギヤは駆動ギヤと連動し、当該駆動ギヤはコントロ
ールロッドと連動し、外部よりコントロールロッドを回
転した時、駆動ギヤを介してバルブ用ギヤとロータリバ
ルブとが回転して各伸ポートと圧ポートの開口面積を調
整させることを特徴とするものである。In order to achieve the above object, the configuration of the present invention is that a rotary valve is rotatably inserted into each expansion port and pressure port in a direction that crosses each port, and each rotary valve has a valve gear. Each valve gear is connected integrally, and each valve gear is interlocked with a drive gear, and the drive gear is interlocked with a control rod. When the control rod is rotated from the outside, the valve gear and rotary valve are rotated via the drive gear. This feature is characterized in that the opening area of each expansion port and pressure port is adjusted.
外部操作で各ロータリバルブを回動すると各ロータリバ
ルブとクロスする各伸ポートと各圧ポートの全部又は一
部が開き、開口している各伸ポートの合計と、各圧ポー
トの合計がそれぞれ伸バルブと圧バルブに対する受圧面
積となり、受圧面積の大きさに応じたバルブ特性が得ら
れる。When each rotary valve is rotated by external operation, all or part of each expansion port and each pressure port that cross each rotary valve opens, and the total of each open expansion port and the total of each pressure port are expanded. This is the pressure receiving area for the valve and the pressure valve, and valve characteristics can be obtained according to the size of the pressure receiving area.
以下本発明の実施の一例な矛１図〜牙４図について述べ
る。The spears 1 to 4, which are examples of the implementation of the present invention, will be described below.
油圧緩衝器１５０基本的構成は、１−５図の油圧緩衝器
と同じであるが、単筒式でも使用できる。The basic configuration of the hydraulic shock absorber 150 is the same as that of the hydraulic shock absorber shown in FIGS. 1-5, but a single cylinder type can also be used.
シリンダ１６内にはピストン１７を介してピストンロッ
ド１８が移動自在に挿入され、シリンダ１６内には、ピ
ストン１７によって上下二つの油室１９，２０が区画さ
れている。A piston rod 18 is movably inserted into the cylinder 16 via a piston 17, and two oil chambers 19 and 20, upper and lower, are defined within the cylinder 16 by the piston 17.
ピストン１７には、９０度変位した位置に四つの伸ポー
トＤ／、Ｄコ、Ｄ３．Ｄｇが縦方向に穿たれ、同じく各
伸ポートに対して４５度変位し、且つそれぞれ９０度づ
つ離れた位置に四つの圧ポートＥｌ、Ｅλ、ＥＪ、Ｅμ
が穿たれ、各伸ポートと圧ポートは上下の油室１９，２
０を連通させるようになっている。The piston 17 has four expansion ports D/, Dco, D3. Dg is bored in the longitudinal direction, and four pressure ports El, Eλ, EJ, and Eμ are also located 45 degrees apart from each expansion port and 90 degrees apart from each other.
are bored, and each expansion port and pressure port are located in the upper and lower oil chambers 19, 2.
0 is communicated.
ピストン１７の下端面には各伸ポートＤｉ −Ｄｐの下
部口端をかこむシート面ｄ／ ＊ ｄＪ ＊ ｄＪ ｒ
ｄ≠が起立し、このシート面ｄ／〜ｄ、には各伸ポー
ト丁）、−Ｔ）、、Ｊ−Ｆ”ｌＩ”ＩＱ、、トーＹ１１
−−−１０．１−１−一／−１５、ｌ’Ｊ−？１ｔｈ、
、ｐルブ２１が当接している。The lower end surface of the piston 17 has a seat surface d/ * dJ * dJ r that surrounds the lower mouth end of each expansion port Di -Dp.
d≠ stands up, and on this sheet surface d/~d, each expansion port (T), -T),, J-F"lI"IQ,, To Y11
---10.1-1-1/-15, l'J-? 1th,
, p-lube 21 are in contact with each other.
同じく、ピストン１７の上端面には各圧ポートＥ／〜Ｅ
４＝の上部口端をかこむシート面’／＋’２＋ｅＪ ＋
”Ａが起立し、これらのシート面ｔ ７ ”−ｅ ｙ
には各圧ポートＤｌ〜計を開閉するリーフバルブからな
る圧バルブ２２が当接している。Similarly, each pressure port E/~E is provided on the upper end surface of the piston 17.
Seat surface surrounding the upper mouth end of 4='/+'2+eJ +
``A stands up and these sheet surfaces t 7 ''-e y
A pressure valve 22 consisting of a leaf valve that opens and closes each pressure port Dl to the gauge is in contact with the pressure valve 22 .
伸バルブ２１はピストンロッド１８の下部に間座２３を
介して挿入され、伸バルブ２１と間座２３はピストンナ
ツト１８に螺合されたピストンナツト２５で保持されて
いる。The extension valve 21 is inserted into the lower part of the piston rod 18 via a spacer 23, and the extension valve 21 and spacer 23 are held by a piston nut 25 screwed into the piston nut 18.
伸バルブ２１の下面にはバルブ２６が当接し、このバル
ブ２６とピストンナツト２４のフランジ状シート２５間
にはスプリング２７が介装されて常時伸バルブ２１とバ
ルブ２６を閉じ方向に附勢している。 。A valve 26 is in contact with the lower surface of the expansion valve 21, and a spring 27 is interposed between the valve 26 and the flange-shaped seat 25 of the piston nut 24 to constantly bias the expansion valve 21 and the valve 26 in the closing direction. There is. .
圧バルブ２２の基端はピストン１７と上部のバルブスト
ッパ２８を間座２９とで保持されている。伸ポートＤＩ
に対して、このポートＤ／と直交する方向に中空な第１
の伸バルブ用ロータリバルブＦｉが回転自在に挿入され
、このロータリバルブＦｌには矛１の伸ポートＤ／に開
閉される通孔３１が穿たれると共に内端に第１の伸バル
ブ用ギヤｆｉが一体に接続されている。The base end of the pressure valve 22 is held by a piston 17, an upper valve stopper 28, and a spacer 29. Shin port DI
, the hollow first hole in the direction orthogonal to this port D/
A rotary valve Fi for an expansion valve is rotatably inserted, and a through hole 31 is bored in this rotary valve Fl to be opened and closed to the expansion port D/ of the spear 1, and a first expansion valve gear fi is provided at the inner end. are connected together.
同様に第２、牙３、牙４の伸ポートＤλ、ＤＪ。Similarly, the second, fang 3, and fang 4 extension ports Dλ, DJ.
Ｄ＜＝に対してもこれらのポートとクロスする方向から
、ｔ−２、矛３、牙４の伸バルブ用ロータリバルブＦ、
２．ＦＪ、Ｆμが回転自在に挿入され、各ロータリバル
ブＦ２．Ｆ３．Ｆｕの内端にはそれぞれ】・２、牙３、
矛４の伸バルブ用ギヤｆ、２．ｆｉ、ｆ弘が回転自在に
挿入されて各ポートを開閉するようになっている。For D<=, from the direction crossing these ports, there are t-2, spear 3, and fang 4 rotary valves F for extension valves;
2. FJ, Fμ are rotatably inserted, and each rotary valve F2. F3. At the inner end of Fu are 】・2, tusk 3,
Spear 4 extension valve gear f, 2. fi, f-hiro are rotatably inserted to open and close each port.
同じく、第１の圧ポートＥｌに対して、このポートＥ／
とクロスする方向から中空な第１の圧バルブ用ロータリ
バルブＧ／が回転自在に挿入され、このロータリバルブ
Ｇ／には第１の圧ポートＥ／に開閉される通孔３２が穿
たれると共に内端に第１の圧バルブ用ギヤＩ／が一体に
接続されている。Similarly, for the first pressure port El, this port E/
A hollow rotary valve G/ for a first pressure valve is rotatably inserted from a direction crossing the first pressure port E/, and a through hole 32 is bored in this rotary valve G/ to be opened and closed to the first pressure port E/. A first pressure valve gear I/ is integrally connected to the inner end.
同じく、他の圧ポートＥコ、ＥＪ、Ｅ≠に対してもこれ
とクロスする方向から第２、矛３、矛４の圧バルブ用ロ
ータリバルブＧ、２ 、ＧＪ 、Ｃｒ＜ｔが回転自在に
挿入され、各ロータリバルブＧ２．Ｇｊ 、Ｇμには通
孔３２が穿たれると共に第２、牙３、牙４の圧バルブ用
ギヤｐ、、ｉＪ、ｉφが一体に接続されている。伸バル
ブ用ギヤｆ１．ｆ、２．ｆｉ 、 ｆ−は軸心に対して
直交すると共にそれぞれ９０度づつ変位した位置にある
。Similarly, the rotary valves G, 2, GJ, and Cr<t for the pressure valves 2, 3, and 4 are rotatable from the direction crossing the other pressure ports E, EJ, and E≠. inserted, each rotary valve G2. Through holes 32 are bored in Gj and Gμ, and pressure valve gears p, , iJ, and iφ of the second, fang 3, and fang 4 are integrally connected. Extension valve gear f1. f, 2. fi and f- are perpendicular to the axis and are displaced by 90 degrees from each other.
同じく、圧バルブ用ギヤｉ、、ｙコ＋ ｆｌ ｊ ＋
１４’は軸心に対して直交し、且つそれぞれ９０度づつ
変位した位置にある。Similarly, gears for pressure valves i,, y + fl j +
14' are perpendicular to the axis and are at positions displaced by 90 degrees.
ピストンロッド１８は中空にされ、このピストンロッド
１８内にはコントロールロッド３０とオ・１の駆動ギャ
エと第２の駆動ギヤＨとが回転自在に挿入されており、
矛１の駆動ギヤ１はコントロールロッド３０の端部に接
続されている。The piston rod 18 is hollow, and a control rod 30, a drive gear H, and a second drive gear H are rotatably inserted into the piston rod 18.
The drive gear 1 of the spear 1 is connected to the end of the control rod 30.
ｆｆ１ｌの駆動ギャエの下端には円周方向に沿って重両
Ｐが形成され、この重両Ｐは圧バルブ用ギヤｇ／、ｉコ
ｒ Ｅ Ｊ ｒ ９４ｔの端部に形成した歯Ｑと噛合し
、駆動ギャエが回転すると四つの圧バルブ用ギヤｉ／、
ｐλ＋ｇＪ＋！ｉ４’と圧バルブ用ロータリバルブＧ／
、ＧＪ 、ＧＪ 、Ｇダが回転する。A double double P is formed along the circumferential direction at the lower end of the driving gear of ff1l, and this double double P meshes with the teeth Q formed on the end of the pressure valve gear g/, icor E J r 94t. When the drive gear rotates, the four pressure valve gears i/,
pλ+gJ+! i4' and rotary valve G/ for pressure valve
, GJ, GJ, and Gda rotate.
第２の駆動ギヤＨは圧バルブ用ギヤｇ／〜Ｉ≠と伸バル
ブ用ギヤｆ、−ｆ、の中間に介在し１．駆動ギヤＨの両
端方向に形成した重両Ｒが各ギヤｙ、−九とｆｌ−ｆ４
１の歯Ｑに噛合し、圧バルブ用ギヤ、９／ −Ｊ％が回
転すると矛２の駆動ギヤＨな介して伸バルブ用ギヤｆ、
〜ルに伝達されて伸バルブ用ロータリバルブＦｔ−Ｆμ
を回転する。The second driving gear H is interposed between the pressure valve gear g/~I≠ and the expansion valve gears f, -f. The heavy double R formed toward both ends of the drive gear H connects each gear y, -9 and fl-f4.
When the pressure valve gear 9/-J% is rotated, the expansion valve gear f is engaged with the gear 1 and the drive gear H of the spear 2 is rotated.
Rotary valve for expansion valve Ft-Fμ
Rotate.
伸バルブ用ロータリバルブＦｔ−Ｆμの通孔３１は同−
同面位置又は回転方向に沿ってそれぞれ異なった位置に
設けておけば、各ロータリバルブＦｉ−Ｆｇが同時に回
転した時、ある通孔３１は開くが、ある通孔３１は閉じ
る。The through hole 31 of the rotary valve Ft-Fμ for the expansion valve is the same as the
If they are provided on the same plane or at different positions along the rotational direction, when the rotary valves Fi-Fg rotate simultaneously, some of the through holes 31 will open, while others will close.
この為通孔３１が伸ポートに開口している時は、開口し
ている伸ポートの合計の通路面積の油量が伸バルブ２１
に作用する。いいかえれば、開口している伸ポートの合
計が伸バルブ２１の受圧面積となる。従ってコントロー
ルロッド３０を介してロータリバルブＦｉ−Ｆ＜＝を所
定量旧都す乙１” ３− Ｖ ？す６座而接か任音ＩＦ
序す１受圧面積に対応する伸側バルブ特性が得られる。Therefore, when the through hole 31 opens to the expansion port, the amount of oil in the total passage area of the open expansion ports is the same as that of the expansion valve 21.
It acts on In other words, the total number of open expansion ports is the pressure receiving area of the expansion valve 21. Therefore, via the control rod 30, the rotary valve Fi-F<= is controlled by a predetermined amount.
The expansion-side valve characteristics corresponding to one pressure-receiving area can be obtained.
同様に圧バルブ用ロータリバルブＦ／〜Ｆμを所定量回
転することにより圧側の受圧面積を任意に調節できる。Similarly, the pressure receiving area on the pressure side can be arbitrarily adjusted by rotating the pressure valve rotary valves F/ to Fμ by a predetermined amount.
次に作動について述べる。Next, we will discuss the operation.
今、ロータリバルブＦ／〜ＦＩＩの通孔３１と、ロータ
リバルブＦ／〜ＦＬＡＯ通孔３２が全部開口していると
する。It is now assumed that the through holes 31 of the rotary valves F/~FII and the through holes 32 of the rotary valves F/~FLAO are all open.
この状態で伸長すると、各伸ポートＤＩ−Ｄ４１より上
部油室１９の油が伸バルブ２１を開かせながら下部油室
２０に流れ、この時伸ポートＤ／−Ｄψの合計の受圧面
積に応じた最もソフトな伸側バルブ特性αｌが得られる
。この際低速時は２／３乗特性のカーブとなる。When it is extended in this state, the oil in the upper oil chamber 19 flows from each extension port DI-D41 to the lower oil chamber 20 while opening the extension valve 21, and at this time, the oil in the upper oil chamber 19 flows into the lower oil chamber 20 from each extension port DI-D41, and at this time, the oil in the upper oil chamber 19 flows into the lower oil chamber 20 from each extension port DI-D41. The softest expansion side valve characteristic αl is obtained. At this time, at low speeds, the curve becomes a 2/3 power characteristic.
又、圧作動時には下部油室２０の油が各圧ポートＥｔ−
Ｅｅと各通孔３２より圧バルブ２２を押し開いて上部油
室１９に流れ、この時与圧ポートＥ／〜Ｅ≠の合計の受
圧面積に応じた最もソフトな圧側減衰力バルブ特性り、
が得られる。Also, during pressure operation, the oil in the lower oil chamber 20 flows through each pressure port Et-.
The pressure valve 22 is pushed open through Ee and each through hole 32 and flows into the upper oil chamber 19, and at this time, the softest pressure side damping force valve characteristic according to the total pressure receiving area of the pressurized ports E/~E≠.
is obtained.
（牙４図）
ロータリバルブＦｔ −Ｆｅ 、 Ｇ／〜Ｇμの組み合
せ方により、ポートが一つだけ開いている場合は最もハ
ードな特性ａ／ ＋ ’／が得られ、二つのポートを開
かせる場合は特性αコ、ｂλが得られ、三つのポートが
開いている場合は特性α３．ｂ３が得られる。この際最
もハードな特性ａ／＋’／に対して最もソフトな特性ａ
ｕ ｓ Ｇ間には大きな可変中がある。(Figure 4) Depending on the combination of rotary valves Ft -Fe, G/~Gμ, when only one port is open, the hardest characteristic a/ + '/ is obtained, and when two ports are open, the hardest characteristic is obtained. gives the characteristics α, bλ, and if three ports are open, the characteristics α3. b3 is obtained. In this case, the softest characteristic a is the hardest characteristic a/+'/
There is a large variation between us and G.
ポートの開口面積を変更する場合は、外部よりコントロ
ールロッド３０を所定量回転して第１の駆動ロツドエを
回転し、この駆動ロツドエに連動して各ロータリバルブ
Ｆｉ −Ｆｕ 、 Ｇ／ ”’−’ｃ＜’を回転すれば
、コントロールロッド３０の回転量に見合った位置の通
孔３１．３２が選択され、これにより各ポートＤｔ ｘ
Ｄｕ 、 Ｅ／−Ｅｐの開口面積が設定される。When changing the opening area of the port, the control rod 30 is externally rotated by a predetermined amount to rotate the first driving rod, and in conjunction with this driving rod, each rotary valve Fi -Fu, G/ "'-' By rotating c<', the through holes 31 and 32 at positions commensurate with the amount of rotation of the control rod 30 are selected, and thereby each port Dt x
The opening areas of Du, E/-Ep are set.
本発明によれば次の効果がある。 According to the present invention, there are the following effects.
■伸・圧バルブに対する受圧面積を調整して減衰力を得
るようにしたから、低速域では２／３〆肖される。■The damping force is obtained by adjusting the pressure receiving area for the expansion/compression valve, so the damping force is reduced by 2/3 in the low speed range.
■同じく、中・高速域ではハードな減衰力特性とソフト
な減衰力特性との間には大きな可変中が得られる。■Similarly, in the medium and high speed ranges, there is a large degree of variation between hard damping force characteristics and soft damping force characteristics.
■伸・圧の減衰力調整が独立して行なえるため、いろい
ろな減衰力特性の組み合せが可能である。例えば伸側を
ハードに、圧側をソフトにし、又は伸側なソフトに圧側
なハードになるように組み合せできる。あるいは、両方
をハードに、両方をソフトにもできる。■Since the damping force for extension and compression can be adjusted independently, various combinations of damping force characteristics are possible. For example, it is possible to make the extension side hard and the compression side soft, or to combine a soft extension side with a hard compression side. Or you can make both hard and both soft.
■ソフトな特性を得るときでも、低速域における減衰力
を単なるオリフィス特性の場合に比べて高くできる。■Even when obtaining soft characteristics, the damping force in the low speed range can be higher than when using simple orifice characteristics.
第１図は本発明の一実施例に係る油圧緩衝器の一部縦断
正面図、矛２図はピストン下端部の横断右側面図、矛３
図はピストン上端部の横断左側面図、牙４図は減衰力特
性を示すグラフ、第５４図は従来の油圧緩衝器の縦断面
図、オ６図は従来の特性を示すグラフである。
１６＠・・シリンダ、１７・１ピストン、１８・・・ピ
ストンロッド、１９．２０−”・油室、２１・・・伸バ
ルブ、２２１・圧バルブ、３ｏ・・・コントロールロッ
ド、Ｄ／、ＤＪ、ＤＪ、Ｄ４１・・・伸ポート、Ｅ／、
ＥＪ、ＥＪ、Ｅμ・・曝圧ポート、Ｆｚ。
Ｆｘ、Ｆ３．Ｆｇ、Ｇｚ、Ｇａ、Ｇ３．Ｇｕ ｍａｎｏ
−タリｌ＜ＪＬブ、Ｈ，Ｉ・・・駆動ギヤ、ｆ／、ｆ２
．ｈ、ｆμ、ｉｔ、、ｆｌコ。
ＩＪ、Ｅｕ・・・バルブ用ギヤ。
第１ 囮
第２図
第３、図
ゝＤ３FIG. 1 is a partially vertical front view of a hydraulic shock absorber according to an embodiment of the present invention, FIG. 2 is a cross-sectional right side view of the lower end of the piston, and FIG.
Fig. 4 is a cross-sectional left side view of the upper end of the piston, Fig. 4 is a graph showing damping force characteristics, Fig. 54 is a longitudinal sectional view of a conventional hydraulic shock absorber, and Fig. 6 is a graph showing conventional characteristics. [email protected], 17.1 Piston, 18...Piston rod, 19.20-"・Oil chamber, 21...Extension valve, 221・Pressure valve, 3o...Control rod, D/, DJ , DJ, D41...Shin port, E/,
EJ, EJ, Eμ...pressure port, Fz. Fx, F3. Fg, Gz, Ga, G3. Gu mano
-Tari l < JL, H, I... Drive gear, f/, f2
．． h,fμ,it,,flco. IJ, Eu... Valve gear. 1st Decoy 2nd Figure 3, Figure D3
Claims (4)
移動自在に挿入され、ピストンはシリンダ内に上下二つ
の油室を区画し、ピストンには二つの油室を連通する伸
ポートと圧ポートとを複数設け、伸ポートの下部口端に
伸バルブを、圧ポートの上部口端に圧バルブをそれぞれ
開閉自在に設けた油圧緩衝器に於て、各伸ポートと圧ポ
ートとに対して、各ポートとクロスする方向にロータリ
バルブを回転自在に挿入させ、各ロータリバルブにはバ
ルブ用ギヤが一体にそれぞれ接続され、各バルブ用ギヤ
は駆動ギヤと連動し、当該駆動ギヤはコントロールロッ
ドと連動し、外部よりコントロールロッドを回転した時
、駆動ギヤを介してバルブ用ギヤとロータリバルブとが
回転して各伸ポートと圧ポートの開口面積を調整させる
ことを特徴とする油圧緩衝器の減衰力調整装置。(1) A piston rod is movably inserted into the cylinder via a piston, and the piston defines two upper and lower oil chambers in the cylinder, and the piston has an extension port and a pressure port that communicate the two oil chambers. In a hydraulic shock absorber, in which a plurality of extension valves are provided at the lower mouth end of the extension port and a pressure valve is provided at the upper mouth end of the pressure port so that they can be opened and closed, each port is provided for each extension port and pressure port. A rotary valve is rotatably inserted in a direction crossing the rotary valve, a valve gear is integrally connected to each rotary valve, each valve gear is interlocked with a drive gear, and the drive gear is interlocked with a control rod, A damping force adjustment device for a hydraulic shock absorber, characterized in that when a control rod is rotated from the outside, a valve gear and a rotary valve are rotated via a drive gear to adjust the opening area of each extension port and pressure port. .
バルブ用ギヤが各ポートに対応して四つづつ設けられて
いる特許請求の範囲第１項記載の油圧緩衝器の減衰力調
整装置。(2) Four expansion ports and four pressure ports are provided,
The damping force adjusting device for a hydraulic shock absorber according to claim 1, wherein four valve gears are provided corresponding to each port.
の駆動ギヤと、八つのバルブ用ギヤと噛合する第２の中
間ギヤとからなり、コントロールロッドが第１の駆動ギ
ヤを駆動し、第１の駆動ギヤの回転力が各バルブ用ギヤ
と第２の駆動ギヤに伝達される特許請求の範囲第１項又
は第２項記載の油圧緩衝器の減衰力調整装置。(3) The drive gear is the first gear connected to the control rod.
and a second intermediate gear that meshes with eight valve gears, the control rod drives the first drive gear, and the rotational force of the first drive gear is transmitted to each valve gear and the second intermediate gear. A damping force adjusting device for a hydraulic shock absorber according to claim 1 or 2, wherein the damping force adjustment device is transmitted to a drive gear of a hydraulic shock absorber according to claim 1 or 2.
閉される一つ又は複数の通孔が設けられ、各ロータリバ
ルブの回転により任意の伸ポートと圧ポートが選択的に
開閉され、開口した伸ポートと圧ポートの合計の開口面
積に応じた伸・圧バルブの受圧面積が得られる特許請求
の範囲第１項記載の油圧緩衝器の減衰力調整装置。(4) Each rotary valve is provided with one or more through holes that are opened and closed to each expansion port and pressure port, and by rotation of each rotary valve, any expansion port and pressure port can be selectively opened and closed. 2. The damping force adjustment device for a hydraulic shock absorber according to claim 1, wherein the pressure receiving area of the expansion/compression valve is obtained in accordance with the total opening area of the expansion port and the pressure port.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10833586A JPS62266241A (en) | 1986-05-12 | 1986-05-12 | Damping force regulating device for hydraulic shock absorber |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10833586A JPS62266241A (en) | 1986-05-12 | 1986-05-12 | Damping force regulating device for hydraulic shock absorber |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS62266241A true JPS62266241A (en) | 1987-11-19 |
Family
ID=14482082
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10833586A Pending JPS62266241A (en) | 1986-05-12 | 1986-05-12 | Damping force regulating device for hydraulic shock absorber |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62266241A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5058715A (en) * | 1988-11-28 | 1991-10-22 | Ilan Silberstein | Shock absorber |
| JP2008240743A (en) * | 2007-03-23 | 2008-10-09 | Showa Corp | Damping force generating device |
-
1986
- 1986-05-12 JP JP10833586A patent/JPS62266241A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5058715A (en) * | 1988-11-28 | 1991-10-22 | Ilan Silberstein | Shock absorber |
| JP2008240743A (en) * | 2007-03-23 | 2008-10-09 | Showa Corp | Damping force generating device |
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