JPS6224850Y2 - - Google Patents
Info
- Publication number
- JPS6224850Y2 JPS6224850Y2 JP1981168789U JP16878981U JPS6224850Y2 JP S6224850 Y2 JPS6224850 Y2 JP S6224850Y2 JP 1981168789 U JP1981168789 U JP 1981168789U JP 16878981 U JP16878981 U JP 16878981U JP S6224850 Y2 JPS6224850 Y2 JP S6224850Y2
- Authority
- JP
- Japan
- Prior art keywords
- piston
- piston rod
- damping force
- communication hole
- solenoids
- 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
- 238000013016 damping Methods 0.000 claims description 53
- 239000006096 absorbing agent Substances 0.000 claims description 9
- 230000035939 shock Effects 0.000 claims description 9
- 230000006835 compression Effects 0.000 claims description 5
- 238000007906 compression Methods 0.000 claims description 5
- 230000008602 contraction Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 2
- 238000012856 packing Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 230000014759 maintenance of location Effects 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
- F16F9/461—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 characterised by actuation means
- F16F9/462—Rotary actuation means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
- Reciprocating, Oscillating Or Vibrating Motors (AREA)
Description
【考案の詳細な説明】 この考案は減衰力調整式油圧緩衝器に関する。[Detailed explanation of the idea] This invention relates to a damping force adjustable hydraulic shock absorber.
例えば車においては乗心地を良くするために各
種の油圧緩衝器が用いられている。このような油
圧緩衝器の一例として、シリンダ内に摺動自在に
嵌入されたピストンを、ピストンロツドに、中空
ナツトにより固定し、かつピストンの両側にそれ
ぞれ縮み側減衰弁、伸び側減衰弁を配設し、前記
中空ナツトの中空部を、ピストンロツドに形成さ
れた連通路を介してピストン上室に連通すると共
に、中空ナツトに連通孔を形成してピストン下室
に連通し、これにより油が封入されたピストン上
室とピストン下室とを連通し、ピストンロツドの
中心部に挿通された回転軸を回すことにより、こ
の回転軸の端部に設けられた連通孔開閉体で前記
連通孔を開閉して、緩衝器の伸び行程、縮み行程
における減衰力の調整を行なうようにしたものが
知られている。 For example, various hydraulic shock absorbers are used in cars to improve riding comfort. As an example of such a hydraulic shock absorber, a piston that is slidably fitted into a cylinder is fixed to a piston rod with a hollow nut, and a compression damping valve and a rebound damping valve are respectively arranged on both sides of the piston. The hollow part of the hollow nut is communicated with the piston upper chamber through a communication passage formed in the piston rod, and a communication hole is formed in the hollow nut to communicate with the piston lower chamber, whereby oil is sealed. The piston upper chamber and the piston lower chamber are connected to each other, and by rotating a rotating shaft inserted through the center of the piston rod, a communicating hole opening/closing body provided at the end of the rotating shaft opens and closes the communicating hole. It is known that the damping force is adjusted during the extension stroke and contraction stroke of the shock absorber.
しかしながら、従来のこのような緩衝器にあつ
ては、減衰弁の外には、中空ナツトに形成された
単一の連通孔を開閉して減衰力を調整するだけで
あるから、その調整量が十分でなく、例えば車が
凹凸の激しい悪い道路を走る場合においてその伸
縮行程が急激である場合、車が滑らかで良好な道
路を走る場合においてその伸縮行程が緩慢な場合
等の各伸縮行程に最適な減衰特性を得ることがで
きないという事情があつた。 However, in conventional shock absorbers, the only thing outside the damping valve is a single communication hole formed in a hollow nut to adjust the damping force. For example, if the expansion and contraction stroke is rapid when the car is running on a rough and rough road, or when the expansion and contraction stroke is slow when the car is running on a smooth and good road, etc. There was a situation in which it was not possible to obtain suitable damping characteristics.
この考案は前記事情に鑑みてなされたもので、
ピストンロツドに、減衰弁を有するピストンを固
定した中空ナツトの複数の連通孔及びピストンロ
ツドに形成された連通路を介してピストン上室と
ピストン下室とを連通し、ピストンロツドに挿通
され連通孔開閉体を有する回転軸を、これに取り
付けられた磁石の周囲に複数のソレノイドを配設
して該ソレノイドに選択的に通電して回し、連通
孔開閉体により中空ナツトの複数の連通孔を適宜
開閉することにより、減衰力の多段調整を行なう
ことができる減衰力調整式油圧緩衝器を提供する
ことを目的とする。 This idea was made in view of the above circumstances,
The upper piston chamber and the lower piston chamber are connected to the piston rod through a plurality of communication holes in a hollow nut to which a piston having a damping valve is fixed and a communication passage formed in the piston rod, and a communication hole opening/closing body inserted into the piston rod is connected to the piston rod. A plurality of solenoids are arranged around a magnet attached to the rotary shaft, and the solenoid is selectively energized to rotate the rotating shaft, and the plurality of communication holes of the hollow nut are opened and closed as appropriate by a communication hole opening/closing body. Accordingly, it is an object of the present invention to provide a damping force adjustable hydraulic shock absorber capable of performing multi-stage adjustment of damping force.
以下、この考案の一実施例を図面に基づいて説
明する。第１図中１はシリンダであり、このシリ
ンダ１は外シリンダ２、内シリンダ３及びこれら
の下端部、上端部にそれぞれ設けられた底蓋４、
上蓋５からなつている。外シリンダ２と、内シリ
ンダ３との間にはリザーバ６が設けられている。
このリザーバ６は、内シリンダ３の下部に設けら
れた連通孔７によつて内シリンダ３内と連通され
ている。底蓋４の外面には取付環８が取り付けら
れており、シリンダ１の頂部にはロツドガイド
９、スプリング１０、ワツシヤ１１、シール部材
１２が設けられている。 An embodiment of this invention will be described below based on the drawings. In FIG. 1, 1 is a cylinder, and this cylinder 1 includes an outer cylinder 2, an inner cylinder 3, and a bottom cover 4 provided at the lower and upper ends of these cylinders, respectively.
It extends from the top lid 5. A reservoir 6 is provided between the outer cylinder 2 and the inner cylinder 3.
This reservoir 6 is communicated with the inside of the inner cylinder 3 through a communication hole 7 provided at the lower part of the inner cylinder 3. A mounting ring 8 is attached to the outer surface of the bottom cover 4, and a rod guide 9, a spring 10, a washer 11, and a seal member 12 are provided at the top of the cylinder 1.
また、内シリンダ３内にはピストン１３が摺動
自在に嵌入され、このピストン１３の中心部には
ロツド孔１４が形成されている。ピストン１３
は、ピストンロツド１５の一端に形成された小径
部に、ロツド孔１４を嵌合されかつ小径部の先端
に中空ナツト１６を螺合されてピストンロツド１
５に取り付けられている。ピストンロツド１５の
他端はシリンダ１の頂部のロツドガイド９、ワツ
シヤ１１、シール部材１２を貫通してシリンダ１
外に突出している。従つて、内シリンダ３内はピ
ストン１３によりピストン上室１７と、ピストン
下室１８とに区画されている。ピストン上室１
７、ピストン下室１８及びリザーバ６内には油が
封入され、リザーバ６内の油の上部にはガスが封
入されている。ピストンロツド１５には中空ナツ
ト１６の中空部とピストン上室１７とを連通する
連通路１９が形成されている。この連通路１９は
ピストンロツド１５の中心を貫通する中心孔２０
と、この中心孔２０から分岐してピストン上室１
７に開口する分岐孔２１とからなつている。 A piston 13 is slidably fitted into the inner cylinder 3, and a rod hole 14 is formed in the center of the piston 13. Piston 13
The piston rod 1 is assembled by fitting the rod hole 14 into a small diameter part formed at one end of the piston rod 15 and screwing a hollow nut 16 into the tip of the small diameter part.
It is attached to 5. The other end of the piston rod 15 passes through the rod guide 9, the washer 11, and the seal member 12 at the top of the cylinder 1, and is connected to the cylinder 1.
It sticks out to the outside. Therefore, the inside of the inner cylinder 3 is divided by the piston 13 into a piston upper chamber 17 and a piston lower chamber 18. Piston upper chamber 1
7. Oil is sealed in the piston lower chamber 18 and the reservoir 6, and gas is sealed above the oil in the reservoir 6. A communication passage 19 is formed in the piston rod 15, which communicates the hollow part of the hollow nut 16 with the piston upper chamber 17. This communication passage 19 has a central hole 20 passing through the center of the piston rod 15.
The piston upper chamber 1 branches from this center hole 20.
It consists of a branch hole 21 opening at 7.
ピストン１３の両端面にはそれぞれ環状の溝２
４，２５が形成されている。また、ピストン１３
には溝２５に連通してピストン上室１７と、ピス
トン下室１８とを連通する連通孔２６と、溝２４
に連通してピストン下室１８とピストン上室１７
とを連通する連通孔２７とが形成されている。ピ
ストン１３の上部で、ピストンロツド１５の小径
部の外周部には縮み側減衰弁２８が配設されてい
る。この縮み側減衰弁２８は、ピストン１３の連
通孔２７を覆う２枚の板からなるデイスクバルブ
２９と、デイスクバルブ２９の撓みの支点となる
リテーナ３０と、デイスクバルブ２９の過大撓み
を防止するワツシヤ３１とからなつている。な
お、デイスクバルブ２９、リテーナ３０及びワツ
シヤ３１はピストンロツド１５に形成された段部
１５ａと、ピストン１３との間に挾持されてい
る。また、デイスクバルブ２９の２枚の板のうち
のピストン１３側の板の外周部にはこの板の径方
向に延びる凹部状の切欠部（図示せず）が形成さ
れている。また、ピストン１３の下部で、ピスト
ンロツド１５の小径部の外周部には伸び側減衰弁
３２が配設されている。この伸び側減衰弁３２
は、ピストン１３の連通孔２６を開閉するデイス
クバルブ３３と、このデイスクバルブ３３の撓み
の支点となるリテーナ３４と、デイスクバルブ３
３の過大撓みを防止するワツシヤ３５とからなつ
ている。なお、デイスクバルブ３３、リテーナ３
４及びワツシヤ３５は中空ナツト１６とピストン
１３との間に挾持されている。 An annular groove 2 is provided on both end surfaces of the piston 13.
4 and 25 are formed. In addition, the piston 13
A communication hole 26 that communicates with the groove 25 and communicates the piston upper chamber 17 and the piston lower chamber 18, and the groove 24.
The piston lower chamber 18 and the piston upper chamber 17 communicate with each other.
A communication hole 27 is formed to communicate with the. At the upper part of the piston 13 and on the outer periphery of the small diameter portion of the piston rod 15, a compression damping valve 28 is disposed. The compression damping valve 28 includes a disc valve 29 made of two plates that cover the communication hole 27 of the piston 13, a retainer 30 that serves as a fulcrum for the deflection of the disc valve 29, and a washer that prevents excessive deflection of the disc valve 29. It consists of 31. The disc valve 29, retainer 30, and washer 31 are held between the piston 13 and a stepped portion 15a formed on the piston rod 15. Further, of the two plates of the disc valve 29, the plate on the piston 13 side has a recess-shaped notch (not shown) extending in the radial direction of this plate. Further, at the lower part of the piston 13 and on the outer periphery of the small diameter portion of the piston rod 15, an extension damping valve 32 is disposed. This expansion side damping valve 32
The disc valve 33 opens and closes the communication hole 26 of the piston 13, the retainer 34 serves as a fulcrum for the deflection of the disc valve 33, and the disc valve 3
3 and a washer 35 to prevent excessive deflection. In addition, the disc valve 33 and the retainer 3
4 and washer 35 are held between hollow nut 16 and piston 13.
また、ピストンロツド１５に形成された連通路
１９の中心孔２０には、この中心孔２０との間に
隙間を設けて回転軸４１が挿通されている。この
回転軸４１の上端部はピストンロツド１５から外
部へ突出し、ピストンロツド１５の上端部と回転
軸４１との間には回転軸４１の回転を許容してシ
ール部材４２が設けられている。回転軸４１の下
端部はピストンロツド１５から突出しており、こ
の下端部には、中空ナツト１６の中空部において
連通孔開閉体４３が取り付けられている。この連
通孔開閉体４３は断面Ｌ字形に形成され、回転軸
４１の回転により回転軸４１と一体的に回転し、
かつ中空ナツト１６の内周部に摺動回転自在に嵌
合され、中空ナツト１６の壁にその円周方向に離
間して形成された２つの連通孔４５，４６を後述
するように開閉可能とされている。なお、中空ナ
ツト１６には第３図に示すように連通孔開閉体４
３の回転を阻止するストツパ４７が設けられてい
る。連通孔開閉体４３と、中空ナツト１６に形成
された段部１６ａとの間には複数のリング状のパ
ツキン４８が介在されている。中空ナツト１６の
下端部には閉塞板４９がねじ込まれ、この閉塞板
４９と連通孔開閉体４３との間には連通孔開閉体
４３を上方へ付勢するようにスプリング５０が介
在されている。なお、連通孔開閉体４３にはパツ
キン４８の内周面の内側の下方に位置して、中空
ナツト１６の中空部における連通孔開閉体４３の
上下部を連通する複数の連通孔５１が形成されて
いる。 Further, a rotating shaft 41 is inserted through a center hole 20 of a communication passage 19 formed in the piston rod 15 with a gap provided between the center hole 20 and the center hole 20. The upper end of this rotary shaft 41 projects outward from the piston rod 15, and a seal member 42 is provided between the upper end of the piston rod 15 and the rotary shaft 41 to allow rotation of the rotary shaft 41. The lower end of the rotating shaft 41 protrudes from the piston rod 15, and a communication hole opening/closing body 43 is attached to the lower end in the hollow portion of the hollow nut 16. This communicating hole opening/closing body 43 is formed to have an L-shaped cross section, and rotates integrally with the rotating shaft 41 as the rotating shaft 41 rotates.
It is slidably and rotatably fitted into the inner periphery of the hollow nut 16, and two communication holes 45 and 46 formed in the wall of the hollow nut 16 spaced apart in the circumferential direction can be opened and closed as described later. has been done. Note that the hollow nut 16 has a communicating hole opening/closing body 4 as shown in FIG.
A stopper 47 is provided to prevent rotation of 3. A plurality of ring-shaped packings 48 are interposed between the communication hole opening/closing body 43 and the step portion 16a formed in the hollow nut 16. A closing plate 49 is screwed into the lower end of the hollow nut 16, and a spring 50 is interposed between the closing plate 49 and the communicating hole opening/closing body 43 so as to bias the communicating hole opening/closing body 43 upward. . In addition, a plurality of communication holes 51 are formed in the communication hole opening/closing body 43 and are located below the inside of the inner circumferential surface of the packing 48 and communicate with the upper and lower parts of the communicating hole opening/closing body 43 in the hollow part of the hollow nut 16. ing.
前記ピストンロツド１５の上端部には外周にね
じ部を有する小径部が形成されており、このピス
トンロツド１５の上端部は車体５３に嵌挿されか
つ小径部に螺合されたナツト５２により車体５３
に取り付けられる。また、ピストンロツド１５の
上端部には取付部材５４が取り付けられる。この
取付部材５４にはテーブル５５が取り付けられて
いる。 The upper end of the piston rod 15 is formed with a small diameter portion having a threaded portion on the outer periphery.
can be attached to. Further, a mounting member 54 is attached to the upper end of the piston rod 15. A table 55 is attached to this attachment member 54.
テーブル５５には、回転軸４１にこの回転軸４
１と同心で一体的に回転するようにかつ着脱可能
に連結された回転軸５６が回転自在に嵌挿されて
いる。この回転軸５６には棒磁石（永久磁石）５
７の中央部が嵌合されて取り付けられている。こ
の棒磁石５７の周囲には、棒磁石５７の両端の外
側で、回転軸５６を中心とする円の円周方向に第
２図に示すように離間して配され、かつ前記円の
径方向に２個ずつ対向させられてなる３組のソレ
ノイド５８−１，５８−２；５９−１，５９−
２；６０−１，６０−２がテーブル５５に取り付
けられて設けられている。これらソレノイド５８
−１，５８−２，５９−１，５９−２，６０−
１，６０−２には選択的に通電がなされるように
電源６１が切換スイツチ６２を介して電気的に接
続されている。なお、取付環８は車輪に取り付け
られる。 The table 55 has a rotary shaft 41 connected to the rotary shaft 4.
A rotating shaft 56 is rotatably inserted into the rotating shaft 56, which is concentrically connected to the rotating shaft 56 and is removably connected to rotate integrally with the rotating shaft 1. A bar magnet (permanent magnet) 5 is attached to this rotating shaft 56.
7 are fitted and attached. Around this bar magnet 57, spaced apart from each other in the circumferential direction of a circle centered on the rotating shaft 56 on the outside of both ends of the bar magnet 57 as shown in FIG. 2, and in the radial direction of the circle. Three sets of solenoids 58-1, 58-2; 59-1, 59-
2; 60-1 and 60-2 are attached to the table 55. These solenoids 58
-1,58-2,59-1,59-2,60-
1 and 60-2 are electrically connected to a power source 61 via a changeover switch 62 so as to selectively energize them. Note that the attachment ring 8 is attached to the wheel.
次に、上記構成の減衰力調整式油圧緩衝器の作
用について説明する。第４図において、横軸はピ
ストン速度Ｖを示し、縦軸は横軸より上方は伸び
側減衰力W1横軸より下方は縮み側減衰力W2をそ
れぞれ示す。まず、ソレノイド５８−１，５８−
２に通電すると、これらソレノイド５８−１，５
８−２に棒磁石の両端が引かれて第２図に示す状
態に位置する。これにより、連通孔開閉体４３は
第３図に示すように連通孔４５，４６を閉塞す
る。この状態で伸び行程の場合、ピストン１３が
ピストンロツド１５等と共にシリンダ１に対して
相対的に第１図において矢印Ａ方向に移動する。
すると、ピストン上室１７内の油がデイスクバル
ブ２９のピストン１３側に形成された切欠部及び
溝２４並びにピストン１３の連通孔２７を介して
ピストン下室１８に流入する。また、この時同時
にリザーバ６内の油がその上部のガス圧に押され
て連通孔７を介しピストン下室１８内に流入す
る。これにより伸び行程時における減衰力が発生
する。これを図示すると第４図にＤ線により示す
如くなる。そして、同図に示すD1点付近の状態
になると、デイスクバルブ３３がリテーナ３４を
支点として撓められ、これによりピストン１３の
連通孔２６が開放され、ピストン上室１７内の油
が連通孔２６、溝２５を介してピストン下室１８
内に流入するので、ピストン上室１７からピスト
ン下室１８へ油が流通し易くなり、伸び行程時に
おけるピストン速度の増加に対する減衰力の増加
量が減少する。 Next, the operation of the damping force adjustable hydraulic shock absorber having the above structure will be explained. In FIG. 4, the horizontal axis shows the piston speed V, and the vertical axis shows the damping force W on the extension side above the horizontal axis, and the damping force W2 on the compression side below the horizontal axis. First, solenoid 58-1, 58-
2, these solenoids 58-1, 5
Both ends of the bar magnet are pulled at 8-2 and are positioned in the state shown in FIG. As a result, the communication hole opening/closing body 43 closes the communication holes 45 and 46 as shown in FIG. In this state, in the case of an extension stroke, the piston 13 moves in the direction of arrow A in FIG. 1 relative to the cylinder 1 together with the piston rod 15 and the like.
Then, the oil in the piston upper chamber 17 flows into the piston lower chamber 18 through the notch and groove 24 formed on the piston 13 side of the disc valve 29 and the communication hole 27 of the piston 13. At the same time, the oil in the reservoir 6 is pushed by the gas pressure above the reservoir 6 and flows into the lower piston chamber 18 through the communication hole 7. This generates a damping force during the extension stroke. This is illustrated by line D in FIG. 4. When the state is near point D1 shown in the figure, the disc valve 33 is bent about the retainer 34, thereby opening the communication hole 26 of the piston 13, and the oil in the piston upper chamber 17 is released from the communication hole. 26, the piston lower chamber 18 via the groove 25
Therefore, oil flows easily from the piston upper chamber 17 to the piston lower chamber 18, and the amount of increase in damping force with respect to increase in piston speed during the extension stroke is reduced.
他方、縮み行程の場合、ピストン１３がピスト
ンロツド１５等と共にシリンダ１に対して相対的
に第１図において矢印Ｂ方向に移動する。する
と、ピストン下室１８内の油がピストン１３の連
通孔２７、溝２４、デイスクバルブ２９のピスト
ン１３側に形成された切欠部を介してピストン上
室１７内に流入し、この時同時にピストン下室１
８内の油が連通孔７を介してリザーバ６に流入す
る。これにより縮み行程における減衰力が発生す
る。これを図示すると第４図にｄ線により示す如
くなる。そして、同図に示すd1点付近の状態にな
ると、デイスクバルブ２９のワツシヤ３１側がリ
テーナ３０を支点として上方へ撓められ、これに
よりピストン下室１８からピストン上室１７へ油
が流通し易くなり、縮み行程時におけるピストン
速度の増加に対する減衰力の増加量が減少する。 On the other hand, in the case of the retraction stroke, the piston 13 moves in the direction of arrow B in FIG. 1 relative to the cylinder 1 together with the piston rod 15 and the like. Then, the oil in the piston lower chamber 18 flows into the piston upper chamber 17 through the communication hole 27 of the piston 13, the groove 24, and the notch formed on the piston 13 side of the disc valve 29, and at the same time, the oil in the piston lower chamber Room 1
Oil in 8 flows into reservoir 6 via communication hole 7. This generates a damping force during the retraction stroke. This is illustrated by the d line in FIG. 4. When the state is near point d shown in the figure, the washer 31 side of the disc valve 29 is bent upward using the retainer 30 as a fulcrum, thereby facilitating the flow of oil from the piston lower chamber 18 to the piston upper chamber 17. Therefore, the amount of increase in damping force with respect to increase in piston speed during the retraction stroke decreases.
次に、スイツチ６２を切換えてソレノイド５９
−１，５９−２に通電すると、これらソレノイド
に棒磁石５７の両端が引かれて回転軸４１と共に
連通孔開閉体４３が回転して中空ナツト１６の連
通孔４５を開放する。（この時連通孔４６は閉塞
されている。）これにより、伸び行程時、縮み行
程時共、分岐孔２１、中心孔２０、連通孔５１、
中空ナツト１６の中空部、連通孔４５を介してピ
ストン上室１７内、ピストン下室１８内の油が流
通し、ピストン上室１７とピストン下室１８との
相互間の油の流通が前記の場合よりも流通し易く
なり、この結果、伸び側減衰力特性、縮み側減衰
力特性はそれぞれ第４図にＥ、ｅ線により示すよ
うになる。 Next, switch 62 is switched to solenoid 59.
-1 and 59-2, both ends of the bar magnet 57 are pulled by these solenoids, and the communicating hole opening/closing body 43 rotates together with the rotating shaft 41 to open the communicating hole 45 of the hollow nut 16. (At this time, the communication hole 46 is closed.) As a result, during both the extension stroke and the contraction stroke, the branch hole 21, the center hole 20, the communication hole 51,
The oil in the piston upper chamber 17 and the piston lower chamber 18 flows through the hollow part of the hollow nut 16 and the communication hole 45, and the oil flows between the piston upper chamber 17 and the piston lower chamber 18 as described above. As a result, the damping force characteristics on the extension side and the damping force characteristics on the contraction side become as shown by lines E and e in FIG. 4, respectively.
次に、スイツチ６２を切換えてソレノイド６０
−１，６０−２に通電すると、これらソレノイド
に棒磁石５７の両端が引かれて回転軸４１と共に
連通孔開閉体４３が回転し、中空ナツト１６の連
通孔４５，４６を共に開放する。これにより、伸
び行程時、縮み行程時共、分岐孔２１、中心孔２
０、連通孔５１、中空ナツト１６の中空部、連通
孔４５，４６を介してピストン上室１７、ピスト
ン下室１８内の油が流通し、ピストン上室１７と
ピストン下室１８との相互間の油の流通が前記の
場合よりもさらに流通し易くなり、この結果伸び
側減衰力特性、縮み側減衰力特性はそれぞれ第４
図にＦ，ｆ線により示すようになる。なお、回転
軸４１を回転させるときは所定のソレノイドに大
電流を流してこの回転軸４１を回し、回転軸４１
をその状態に保持しておくためにコイルの温度を
それ程高くしないような弱電流を前記所定のソレ
ノイドに流しておく。 Next, switch 62 is turned on solenoid 60
-1 and 60-2, both ends of the bar magnet 57 are pulled by these solenoids, and the communication hole opening/closing body 43 rotates together with the rotating shaft 41, opening both the communication holes 45 and 46 of the hollow nut 16. As a result, during both the extension stroke and the contraction stroke, the branch hole 21 and the center hole 2
0, the oil in the piston upper chamber 17 and the piston lower chamber 18 flows through the communication hole 51, the hollow part of the hollow nut 16, and the communication holes 45 and 46, and between the piston upper chamber 17 and the piston lower chamber 18. The oil flows more easily than in the case described above, and as a result, the damping force characteristics on the extension side and the damping force characteristics on the contraction side are respectively 4th.
This is shown by lines F and f in the figure. Note that when rotating the rotating shaft 41, a large current is applied to a predetermined solenoid to rotate the rotating shaft 41.
In order to maintain this state, a weak current that does not raise the temperature of the coil too much is passed through the predetermined solenoid.
従つて、例えば車が凹凸の激しい悪路を走行す
る場合にはソレノイド５８−１，５８−２に通電
すればこの場合に最適の減衰力を得ることがで
き、車が凹凸の極めて少ない良い道路を走行する
場合にはソレノイド６０−１，６０−２に通電す
ればこの場合に最適の減衰力を得ることができ、
またこの中間の道路状態の場合にはソレノイド５
９−１，５９−２に通電すればこの場合に最適の
減衰力を得ることができる。また、本実施例によ
れば、ソレノイドに選択的に通電するだけで回転
軸４１を回して減衰力を調整することができるの
で、その制御機構が簡単でコストが安く、故障が
少ない。 Therefore, for example, when the car is traveling on a rough road with extremely uneven surfaces, the optimum damping force can be obtained by energizing the solenoids 58-1 and 58-2. When traveling, the optimum damping force can be obtained by energizing the solenoids 60-1 and 60-2.
In addition, in the case of intermediate road conditions, solenoid 5
In this case, the optimum damping force can be obtained by energizing 9-1 and 59-2. Furthermore, according to this embodiment, the damping force can be adjusted by rotating the rotary shaft 41 simply by selectively energizing the solenoid, so the control mechanism is simple, the cost is low, and there are few failures.
また、回転軸４１に取り付けられた棒磁石５７
の両端の外側に円周方向に離間して複数のソレノ
イドが設けられているので、減衰力調整時には減
衰力調整切換えポジシヨンに棒磁石５７を直接位
置させることができるので、減衰力調整のための
切換え時間が極めて短く、さらに減衰力調整作動
時に連通孔開閉体４３の回転抵抗が大きく、仮り
に減衰力調整切換えポジシヨンに対し連通孔開閉
体４３、棒磁石５７の位置がずれていたとして
も、その後ソレノイドへの通電を切換えるスイツ
チ６２を作動させたときには連通孔開閉体４３、
棒磁石５７を所望の減衰力調整切換えポジシヨン
に確実に速やかに位置させることができる。 In addition, a bar magnet 57 attached to the rotating shaft 41
Since a plurality of solenoids are provided spaced apart in the circumferential direction on the outside of both ends of the bar magnet 57, the bar magnet 57 can be directly positioned at the damping force adjustment switching position when adjusting the damping force. The switching time is extremely short, and the rotational resistance of the communicating hole opening/closing body 43 is large during the damping force adjustment operation, and even if the communicating hole opening/closing body 43 and the bar magnet 57 are misaligned with respect to the damping force adjustment switching position. After that, when the switch 62 for switching the energization to the solenoid is operated, the communication hole opening/closing body 43,
The bar magnet 57 can be reliably and quickly positioned at a desired damping force adjustment switching position.
なお、前記実施例においては、棒磁石５７の周
囲に３組のソレノイドを設け、中空ナツト１６に
２つの連通孔４５，４６を形成して減衰力を３段
切換えとしたが、これに限られることなく、ソレ
ノイドの組数及び中空ナツトに形成する連通孔の
数を増加すれば減衰力を多段切換えとすることも
できる。 In the above embodiment, three sets of solenoids were provided around the bar magnet 57, and two communication holes 45 and 46 were formed in the hollow nut 16 to switch the damping force in three stages, but the present invention is not limited to this. Instead, the damping force can be switched in multiple stages by increasing the number of solenoids and the number of communicating holes formed in the hollow nut.
以上説明したようにこの考案によれば、ピスト
ンロツドに、減衰弁を有するピストンを固定した
中空ナツトの複数の連通孔及びピストンロツドに
形成された連通路を介してピストン上室と、ピス
トン下室とを連通し、ピストンロツドに挿通され
連通孔開閉体を有する回転軸を、これに取り付け
られた磁石の周囲に複数のソレノイドを配設して
該ソレノイドに選択的に通電して回し、連通孔開
閉体により中空ナツトの複数の連通孔を適宜開閉
する構成であるから、減衰力の多段切換え調整が
可能となり、これにより、例えば車が凹凸の激し
い悪路を走行する場合、凹凸の極めて少ない良い
道路を走行する場合、これらの中間状態の道路を
走行する場合等において、それぞれ最適の減衰力
を得ることができる。また、ソレノイドに選択的
に通電するだけで回転軸を回して減衰力を調整す
ることができるので、その制御機構が簡単でコス
トが安く、故障が少ない。 As explained above, according to this invention, the piston upper chamber and the piston lower chamber are connected to the piston rod through the plurality of communication holes of the hollow nut to which the piston having the damping valve is fixed and the communication passage formed in the piston rod. A plurality of solenoids are arranged around a magnet attached to a rotary shaft that is inserted into the piston rod and has a communication hole opening/closing body, and the solenoids are selectively energized and rotated. Since the structure is such that the multiple communication holes in the hollow nut are opened and closed as appropriate, it is possible to adjust the damping force in multiple stages.For example, when the car is driving on a rough road with many bumps, it is possible to drive on a good road with very few bumps and bumps. In this case, the optimum damping force can be obtained when driving on a road in an intermediate state. In addition, the damping force can be adjusted by rotating the rotary shaft simply by selectively energizing the solenoid, so the control mechanism is simple, the cost is low, and there are fewer failures.
しかも、回転軸に取り付けられた棒磁石の両端
の外側に円周方向に離間して複数のソレノイドが
設けられているので、減衰力調整時には減衰力調
整切換えポジシヨンに棒磁石を直接位置させるこ
とができるので、減衰力調整のための切換え時間
が極めて短く、
減衰力調整作動時に連通孔開閉体の回転抵抗が
大きく、仮りに減衰力調整切換えポジシヨンに対
し連通孔開閉体、棒磁石の位置がずれていたとし
ても、その後ソレノイドへの通電を切換えるスイ
ツチを作動させたときには連通孔開閉体、棒磁石
を所望の減衰力調整切換えポジシヨンに確実に速
やかに位置させることができ、さらにソレノイド
への通電を切換えるスイツチを車の運転席の近傍
に配設すれば、運転席から減衰力を切換え調整す
ることができるので非常に便利である。 Moreover, since multiple solenoids are provided circumferentially apart from each other on the outside of both ends of the bar magnet attached to the rotating shaft, the bar magnet can be directly positioned at the damping force adjustment switching position when adjusting the damping force. Therefore, the switching time for damping force adjustment is extremely short, and the rotational resistance of the communicating hole opening/closing body is large when the damping force adjustment is activated, and if the position of the communicating hole opening/closing body and bar magnet deviates from the damping force adjustment switching position. Even if the switch is operated to switch the energization to the solenoid, the communication hole opening/closing body and the bar magnet can be reliably and quickly positioned at the desired damping force adjustment switching position, and furthermore, when the switch to switch the energization to the solenoid is operated, the solenoid can be energized. If the switch is placed near the driver's seat of the car, it is very convenient because the damping force can be switched and adjusted from the driver's seat.
第１図はこの考案の一実施例を示す縦断面図、
第２図はその回転軸の回転機構を示す概略説明
図、第３図は第１図の−線に沿う一部の横断
面図、第４図はその減衰力特性図である。
７，２６，２７，４５，４６，５１……連通
孔、１３……ピストン、１５……ピストンロツ
ド、１６……中空ナツト、１７……ピストン上
室、１８……ピストン下室、１９……連通路、２
８……縮み側減衰弁、３２……伸び側減衰弁、４
１，５６……回転軸、４３……連通孔開閉体、５
５……テーブル、５７……棒磁石、５８−１，５
８−２，５９−１，５９−２，６０−１，６０−
２……ソレノイド、６１……電源。
FIG. 1 is a longitudinal sectional view showing an embodiment of this invention.
FIG. 2 is a schematic explanatory diagram showing the rotation mechanism of the rotating shaft, FIG. 3 is a cross-sectional view of a portion taken along the line - in FIG. 1, and FIG. 4 is a diagram showing the damping force characteristics. 7, 26, 27, 45, 46, 51... Communication hole, 13... Piston, 15... Piston rod, 16... Hollow nut, 17... Piston upper chamber, 18... Piston lower chamber, 19... Connection aisle, 2
8... Contraction side damping valve, 32... Retention side damping valve, 4
1, 56...Rotating shaft, 43...Communication hole opening/closing body, 5
5...Table, 57...Bar magnet, 58-1,5
8-2, 59-1, 59-2, 60-1, 60-
2... Solenoid, 61... Power supply.
Claims (1)
ンをピストンロツドに中空ナツトによつて固定
し、該中空ナツト、前記ピストンロツドにそれぞ
れ形成された連通孔、連通路を介してピストン下
室とピストン上室とを連通し、前記ピストンロツ
ドに挿通された回転軸の回転により該回転軸の一
端に設けられた連通孔開閉体で前記連通孔を開閉
する油圧緩衝機において、前記ピストンロツドの
他端にテーブルを嵌合して取り付け、該テーブル
の近傍に位置しかつ前記回転軸に棒磁石の中央部
を取り付け、該棒磁石の両端の外側で前記回転軸
を中心とする円の円周方向に離間して配された複
数のソレノイドを前記円の径方向に２個ずつ対向
させてなる複数組のソレノイドを、前記テーブル
に取り付け、該各複数組のソレノイドに選択的に
通電可能に電源を接続したことを特徴とする減衰
力調整式油圧緩衝器。 A piston having an extension side damping valve and a compression side damping valve is fixed to a piston rod by a hollow nut, and a lower piston chamber and an upper piston chamber are connected to each other through the hollow nut, a communication hole formed in the piston rod, and a communication passage. In a hydraulic shock absorber, a table is fitted to the other end of the piston rod, and the communication hole is opened and closed by a communication hole opening/closing body provided at one end of the rotation shaft by rotation of a rotation shaft inserted into the piston rod. The central part of a bar magnet is attached to the rotating shaft, and the center part of the bar magnet is located near the table and is spaced apart from each other in the circumferential direction of a circle centered on the rotating shaft on the outside of both ends of the bar magnet. A plurality of sets of solenoids each having a plurality of solenoids facing each other in the radial direction of the circle are attached to the table, and a power source is connected to each of the plurality of sets of solenoids so as to selectively energize them. Hydraulic shock absorber with adjustable damping force.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16878981U JPS5872546U (en) | 1981-11-12 | 1981-11-12 | Damping force adjustable hydraulic shock absorber |
| GB08232113A GB2112104A (en) | 1981-11-12 | 1982-11-10 | Adjusting hydraulic dampers |
| DE19823241984 DE3241984A1 (en) | 1981-11-12 | 1982-11-12 | HYDRAULIC SHOCK ABSORBER |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16878981U JPS5872546U (en) | 1981-11-12 | 1981-11-12 | Damping force adjustable hydraulic shock absorber |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5872546U JPS5872546U (en) | 1983-05-17 |
| JPS6224850Y2 true JPS6224850Y2 (en) | 1987-06-25 |
Family
ID=15874495
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16878981U Granted JPS5872546U (en) | 1981-11-12 | 1981-11-12 | Damping force adjustable hydraulic shock absorber |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS5872546U (en) |
| DE (1) | DE3241984A1 (en) |
| GB (1) | GB2112104A (en) |
Families Citing this family (34)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3324321C2 (en) * | 1983-04-11 | 1985-06-27 | F & O Electronic Systems GmbH & Co, 6901 Neckarsteinach | Adjustable valve for the piston rod of a vibration damper |
| DE3312899C2 (en) * | 1983-04-11 | 1985-06-13 | F & O Electronic Systems GmbH & Co, 6901 Neckarsteinach | Adjustable valve for the piston rod of a vibration damper |
| DE3334255A1 (en) * | 1983-09-22 | 1985-04-11 | Boge Gmbh, 5208 Eitorf | Hydraulic, controllable shock absorber with a damping piston fixed on a hollow piston rod |
| DE3323405A1 (en) * | 1983-06-29 | 1985-01-17 | Boge Gmbh, 5208 Eitorf | Hydraulic, adjustable shock absorber with a damping piston fixed to a hollow piston rod |
| ES533297A0 (en) * | 1983-06-29 | 1985-03-01 | Boge Gmbh | ADJUSTABLE HYDRAULIC DAMPER |
| JPS6052439U (en) * | 1983-09-20 | 1985-04-12 | トキコ株式会社 | Damping force adjustable hydraulic shock absorber |
| GB2147683B (en) * | 1983-09-24 | 1986-10-01 | Bilstein August Gmbh Co Kg | Shock absorber, with electromagnetically biased pressure responsive valve |
| DE3334704A1 (en) * | 1983-09-24 | 1985-04-11 | August Bilstein GmbH & Co KG, 5828 Ennepetal | Controllable shock absorber especially for motor vehicles |
| DE3348176C2 (en) * | 1983-09-24 | 1988-02-04 | August Bilstein Gmbh & Co Kg, 5828 Ennepetal, De | Adjustable shock absorber, in particular for motor vehicles |
| DE3344029C2 (en) * | 1983-12-06 | 1986-09-18 | Boge Gmbh, 5208 Eitorf | Hydraulic vibration damper |
| JPS60103734U (en) * | 1983-12-21 | 1985-07-15 | 自動車電機工業株式会社 | hydraulic shock absorber |
| US5326129A (en) * | 1984-04-04 | 1994-07-05 | Ohlins Racing Ab | Means for a shock absorber |
| SE443622B (en) * | 1984-04-04 | 1986-03-03 | Rolf Blixt | FOR SHOCK MUSHERS DESIGNED TO POSSIBLE VARIATION VARIATION VARIATION |
| GB8411319D0 (en) * | 1984-05-03 | 1984-06-06 | Armstrong Patents Co Ltd | Shock absorbers |
| DE3419879A1 (en) * | 1984-05-28 | 1985-11-28 | Boge Gmbh, 5208 Eitorf | HYDRAULIC, ADJUSTABLE TWO-TUBE SHOCK ABSORBER |
| DE3421601A1 (en) * | 1984-06-09 | 1985-12-19 | Boge Gmbh, 5208 Eitorf | Adjustable hydraulic shock absorber |
| DE8421106U1 (en) * | 1984-06-09 | 1987-07-02 | Boge Gmbh, 5208 Eitorf, De | |
| DE3432465A1 (en) * | 1984-09-04 | 1986-03-13 | Boge Gmbh, 5208 Eitorf | ADJUSTABLE DAMPING VALVE FOR A HYDRAULIC VIBRATION DAMPER |
| JPH0444905Y2 (en) * | 1984-10-19 | 1992-10-22 | ||
| SE445850B (en) * | 1984-12-07 | 1986-07-21 | Magnus Lizell | PRESSURE VALVE DEVICE FOR PRESSURE MEDIA Separately for Hydraulic Oil in Vehicle Shock Absorbers and Similar |
| NL8503031A (en) * | 1985-11-05 | 1987-06-01 | Koni Bv | ELECTRICALLY ADJUSTABLE SHOCK ABSORBER. |
| FR2605231B2 (en) * | 1985-12-04 | 1989-04-14 | Miccoli Cosimo | HYDRAULIC SYSTEM APPLIED TO WEIGHING EQUIPMENT |
| CA1263414A (en) | 1986-06-05 | 1989-11-28 | Magnus Lizell | Restriction valve device for hydraulic pressure fluids in vehicle shock absorbing mechanisms |
| US5217095A (en) | 1986-06-05 | 1993-06-08 | Monroe Auto Equipment Company | Method and apparatus for absorbing mechanical shock |
| JPH0834683B2 (en) * | 1986-07-04 | 1996-03-29 | アイシン精機株式会社 | Rotary drive |
| JPH0732579B2 (en) * | 1986-10-31 | 1995-04-10 | 株式会社ユニシアジェックス | Variable damping force actuator for hydraulic shock absorber |
| FR2606109B1 (en) * | 1986-10-31 | 1992-12-04 | Atsugi Motor Parts Co Ltd | ROTARY HANDLING DEVICE AND VARIABLE ACTION SHOCK ABSORBER |
| JPH0732577B2 (en) * | 1987-10-22 | 1995-04-10 | アイシン精機株式会社 | Rotary actuator for multi-position control |
| JP2781176B2 (en) * | 1988-02-17 | 1998-07-30 | 株式会社ユニシアジェックス | Actuator |
| DE3805934A1 (en) * | 1988-02-25 | 1989-09-07 | Bosch Gmbh Robert | HYDRAULIC SHOCK ABSORBER |
| US5123671A (en) * | 1989-03-13 | 1992-06-23 | Monroe Auto Equipment Company | Method and apparatus for controlling shock absorbers |
| US4943083A (en) * | 1989-03-13 | 1990-07-24 | Monroe Auto Equipment Company | Signal conditioning circuit assembly |
| US5152379A (en) * | 1990-04-16 | 1992-10-06 | Monroe Auto Equipment Company | Adjustable shock absorber assembly |
| US5529152A (en) * | 1994-07-08 | 1996-06-25 | Aimrite Systems International, Inc. | Variable constant force hydraulic components and systems |
-
1981
- 1981-11-12 JP JP16878981U patent/JPS5872546U/en active Granted
-
1982
- 1982-11-10 GB GB08232113A patent/GB2112104A/en not_active Withdrawn
- 1982-11-12 DE DE19823241984 patent/DE3241984A1/en not_active Ceased
Also Published As
| Publication number | Publication date |
|---|---|
| GB2112104A (en) | 1983-07-13 |
| DE3241984A1 (en) | 1983-06-09 |
| JPS5872546U (en) | 1983-05-17 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPS6224850Y2 (en) | ||
| US4463839A (en) | Hydraulic damper | |
| KR860001691B1 (en) | Hydraulic damper | |
| US4645042A (en) | Hydraulic damper | |
| US3420341A (en) | Variable shock absorber | |
| US4535877A (en) | Hydraulic damper of adjustable damping force type | |
| JP2725856B2 (en) | Hydraulic pneumatic suspension jack for vehicles | |
| JPH05149364A (en) | Damping force regulating system hydraulic shock absorber | |
| US4800994A (en) | Hydraulic damper of adjustable damping force type | |
| JPH05500553A (en) | adjustable shock absorber assembly | |
| US5251927A (en) | Steer-sensitive hydraulic shock absorber and method | |
| JPS61129309A (en) | Suspension system for vehicle | |
| US6213262B1 (en) | Shock absorber | |
| JPH036379B2 (en) | ||
| US5207301A (en) | Active suspension actuator with real time damping | |
| GB2262971A (en) | Shock absorber | |
| JPH023060B2 (en) | ||
| JPS6136826Y2 (en) | ||
| US4705263A (en) | Fluid-filled bushing | |
| KR100623276B1 (en) | Valve structure for shock absorber | |
| JPS6364654B2 (en) | ||
| JPS6221164Y2 (en) | ||
| JPS6243159Y2 (en) | ||
| JPS5861344A (en) | Spring load adjuster of hydraulic damper | |
| JPH031636Y2 (en) |