JPS645174B2 - - Google Patents
Info
- Publication number
- JPS645174B2 JPS645174B2 JP5802481A JP5802481A JPS645174B2 JP S645174 B2 JPS645174 B2 JP S645174B2 JP 5802481 A JP5802481 A JP 5802481A JP 5802481 A JP5802481 A JP 5802481A JP S645174 B2 JPS645174 B2 JP S645174B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- piston
- damping
- electromagnetic solenoid
- fixed shaft
- 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 39
- 239000003921 oil Substances 0.000 claims description 18
- 230000035939 shock Effects 0.000 claims description 11
- 239000006096 absorbing agent Substances 0.000 claims description 9
- 239000010720 hydraulic oil Substances 0.000 claims description 9
- 239000000696 magnetic material Substances 0.000 claims description 4
- 230000003247 decreasing effect Effects 0.000 claims description 3
- 238000001514 detection method Methods 0.000 description 6
- 230000005284 excitation Effects 0.000 description 5
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- WABPQHHGFIMREM-UHFFFAOYSA-N lead(0) Chemical compound [Pb] WABPQHHGFIMREM-UHFFFAOYSA-N 0.000 description 4
- 239000007789 gas Substances 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 238000001179 sorption measurement Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000011261 inert gas Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000003566 sealing material Substances 0.000 description 1
- 125000006850 spacer group Chemical group 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/06—Characteristics of dampers, e.g. mechanical dampers
- B60G17/08—Characteristics of fluid dampers
Description
【発明の詳細な説明】
本発明は自動二輪あるいは四輪車の油圧緩衝器
に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic shock absorber for a motorcycle or a four-wheeled vehicle.
油圧緩衝器に要求される減衰特性は、運転条件
に応じて種々多様に変化するのであるが、一般的
に予め設定された固定的な特性しか附与できず、
厳密には要求に対応できないのが現状であつた。 The damping characteristics required for a hydraulic shock absorber change in various ways depending on the operating conditions, but generally only preset fixed characteristics can be imparted.
Strictly speaking, the current situation was that it was not possible to meet the demands.
これに対して、本出願人により特公昭46−
14368号公報において、運転条件に応じて電磁切
換弁を作動させ減衰力を切換変化させるようにし
たものが提案されている。 In contrast, the applicant has
Japanese Patent No. 14368 proposes a system in which an electromagnetic switching valve is operated to switch and change the damping force according to operating conditions.
これによれば、旋回、舵行走行、急停車、急発
進時などに減衰力を高めて車体のローリングやピ
ツチングを防ぎつつ、通常走行時には柔らかい減
衰特性を発揮して乗心地の改善がはかれるのであ
るが、緩衝器のピストンに内蔵した電磁切換弁
は、電磁ソレノイドの励磁により２位置間でオン
オフ的に切換移動するスプール弁で構成されてい
るため、減衰特性の制御が２段階に切換えられる
のみで、正確には要求減衰特性を満たしえないの
と、ピストン振動に伴いスプール弁が挙動して、
電磁ソレノイドの励磁と無関係に減衰力が切換わ
るという作動不安により、いま一歩の信頼性に欠
けるという問題点があつた。 According to this, the damping force is increased during turns, steering, sudden stops, sudden starts, etc. to prevent rolling and pitching of the vehicle body, while providing soft damping characteristics during normal driving to improve ride comfort. However, the electromagnetic switching valve built into the shock absorber piston consists of a spool valve that switches between two positions on and off when the electromagnetic solenoid is excited, so the control of the damping characteristics can only be switched to two stages. To be more precise, the required damping characteristics cannot be met, and the spool valve behaves due to piston vibration.
There was a problem in that reliability was lacking due to operational instability in that the damping force was switched regardless of the excitation of the electromagnetic solenoid.
本発明はかかる問題を解決するために提案され
たもので、機械的な可動部分をもたずに制御電流
（電圧）値に応じて減衰力を連続的に可変とする
ことのできる油圧緩衝器を提供することを目的と
する。 The present invention was proposed to solve this problem, and is a hydraulic shock absorber that can continuously vary the damping force according to the control current (voltage) value without having any mechanically moving parts. The purpose is to provide
このために本発明では、シリンダにピストンを
摺動自由に収装してピストンの両面に油室を形成
する一方、ピストンに連結したピストンロツドの
進入体積の変動分を吸収するガス室を備えた油圧
緩衝器において、ピストンの移動に伴つて作動油
の流れる流路にバルブボデイを固定し、このバル
ブボデイの内部に該バルブボデイに設けたバルブ
孔のシート部を開閉する磁性材からなる板状の減
衰バルブを配設すると共に、この減衰バルブを上
記シート部から離間する方向にバルブスプリング
力に抗して吸引する電磁ソレノイドを収設し、か
つこの電磁ソレノイドは、ソレノイドコイルを巻
き付けたボビンを該ボビン及びバルブボデイを貫
通する固定軸を介してピストンロツドの一端に締
め付けた構成とすると共に、前記固定軸の端部に
ソレノイドコイルを包囲するカバー体を設けて固
定軸を磁芯として該カバー体から減衰バルブにわ
たる閉磁路を形成し、当該減衰バルブの開弁圧を
電磁ソレノイドの吸引力に応じて連続的に増減さ
せるようにした。 To this end, in the present invention, the piston is housed in the cylinder so as to be able to slide freely and oil chambers are formed on both sides of the piston, while the oil pressure chamber is equipped with a gas chamber that absorbs the fluctuation in the volume of the piston rod connected to the piston. In a shock absorber, a valve body is fixed in a flow path through which hydraulic oil flows as the piston moves, and a plate-shaped damping valve made of a magnetic material is installed inside the valve body to open and close the seat of a valve hole provided in the valve body. At the same time, an electromagnetic solenoid is arranged to attract the damping valve in a direction away from the seat part against the valve spring force, and the electromagnetic solenoid moves a bobbin around which a solenoid coil is wound between the bobbin and the valve body. The solenoid coil is fastened to one end of the piston rod through a fixed shaft passing through the piston rod, and a cover body surrounding the solenoid coil is provided at the end of the fixed shaft, and a closed magnet extends from the cover body to the damping valve with the fixed shaft as the magnetic core. The opening pressure of the damping valve is continuously increased or decreased in accordance with the suction force of the electromagnetic solenoid.
以下、本発明の実施例を図面にもとづいて説明
する。 Embodiments of the present invention will be described below based on the drawings.
第１図は本発明をタンク別置タイプの油圧緩衝
器に適用したもので、まず、シリンダ１にはピス
トン２が摺動自由に収装され油室C1、C2を画成
する一方、シリンダ下端のブラケツト３と、ピス
トン２に連結するピストンロツド４の先端のブラ
ケツト５とを介して、それぞれ車軸と車体とに連
結される。 FIG. 1 shows the application of the present invention to a separate tank type hydraulic shock absorber. First, a piston 2 is housed in a cylinder 1 so as to be freely slidable, defining oil chambers C 1 and C 2 . It is connected to the axle and the vehicle body through a bracket 3 at the lower end of the cylinder and a bracket 5 at the tip of a piston rod 4 connected to the piston 2, respectively.
シリンダ１の外周下部には、スプリングホルダ
６が螺着され、ピストンロツド４の先端部に係止
したスプリングホルダ７との間に懸架ばね８が介
装され、これにより荷重を支持するとともに衝撃
を吸収する。 A spring holder 6 is screwed onto the lower outer circumference of the cylinder 1, and a suspension spring 8 is interposed between the spring holder 7 and the spring holder 7, which supports the load and absorbs shock. do.
ピストンロツド４はシリンダ１の上部に嵌めた
軸受部１０で摺動自由に支持され、軸受部１０に
はピストン２の伸び切り荷重を受けるストツプラ
バー１１がリテーナ１２を介して取付けられる。 The piston rod 4 is slidably supported by a bearing part 10 fitted into the upper part of the cylinder 1, and a stop rubber 11 which receives the full extension load of the piston 2 is attached to the bearing part 10 via a retainer 12.
このストツプラバー１１に対向してピストンロ
ツド４の先端段付部１３にはストツパ１４が係止
されると共に、このストツパ１４に隣設してピス
トン２が係止固定される。 A stopper 14 is engaged with the stepped portion 13 of the piston rod 4 facing the stop rubber 11, and the piston 2 is engaged and fixed adjacent to the stopper 14.
そして、このピストン２は第２図で示したよう
に、円筒状に内部がくり抜かれてバルブボデイを
形成しこの空胴部２Ｂにボビン１６に巻かれたソ
レノイドコイル１７が、上記ピストンロツド４の
先端部に螺着する固定軸１５及びボビン１６を包
囲するカバー体１９を介して挿入固定されて電磁
ソレノイド１８を形成している。 As shown in FIG. 2, the inside of this piston 2 is hollowed out in a cylindrical shape to form a valve body, and a solenoid coil 17 wound around a bobbin 16 is installed in this cavity 2B at the tip of the piston rod 4. An electromagnetic solenoid 18 is formed by being inserted and fixed through a cover body 19 that surrounds a fixed shaft 15 and a bobbin 16 that are screwed into the bobbin 16 .
この電磁ソレノイド１８の端部には中空円盤状
の磁性材からなる伸側減衰バルブ２０が上記固定
軸１５の外周を軸方向移動可能に配設され、カバ
ー体１９の外周にその基端部が担持された板バネ
からなるバルブスプリング２３及びスペーサ２４
により常に閉じ方向に付勢されて、ピストン２を
貫通して上下の油室C1，C2を連通するバルブ孔
２１を開閉するようになつている。図中２２がバ
ルブ孔２１のシート部である。 At the end of the electromagnetic solenoid 18, a hollow disc-shaped expansion damping valve 20 made of a magnetic material is disposed so as to be movable in the axial direction around the outer periphery of the fixed shaft 15, and its base end is arranged on the outer periphery of the cover body 19. Valve spring 23 and spacer 24 consisting of supported leaf springs
The piston 2 is always biased in the closing direction to open and close the valve hole 21 that passes through the piston 2 and communicates with the upper and lower oil chambers C 1 and C 2 . In the figure, 22 is the seat portion of the valve hole 21.
従つて、上記シート部２２を閉じる伸側減衰バ
ルブ２０は、電磁ソレノイド１８が励磁されると
磁性材からなるカバー体１９の端部（吸着部）１
９ａ側に吸引され、バルブシート部２２に対する
バルブスプリング２３の押圧力を低減するように
なつている。 Therefore, when the electromagnetic solenoid 18 is excited, the extension damping valve 20 that closes the seat portion 22 closes the end portion (adsorption portion) 1 of the cover body 19 made of a magnetic material.
9a side, thereby reducing the pressing force of the valve spring 23 against the valve seat portion 22.
伸側バルブ孔２１の外側には、圧側バルブ孔２
５がピストン２を貫通して形成され、ピストン２
の上端でこのバルブ孔２５を閉じる圧側チエツク
バルブ２６がストツパ１４との間に介装されてい
る。 A compression side valve hole 2 is provided on the outside of the expansion side valve hole 21.
5 is formed passing through the piston 2, and the piston 2
A pressure side check valve 26 that closes the valve hole 25 at the upper end of the valve is interposed between the valve hole 25 and the stopper 14.
ところで、上記ソレノイドコイル１７は、その
リード線２９が固定軸１５及びピストンロツド４
の中心に設けた配線通路２７Ａ，２７Ｂを通し
て、ピストンロツド４の上部ブラケツト５をくり
抜いた導孔３０から外部へと取り出され、このリ
ード線２９に制御信号（電流）を入力させること
により、電磁ソレノイド１８の励磁力、換言する
と伸側減衰バルブ２０の設定荷重（開弁圧）を連
続的に調整しうるようになつている。 By the way, the lead wire 29 of the solenoid coil 17 is connected to the fixed shaft 15 and the piston rod 4.
The electromagnetic solenoid 18 is taken out through the wiring passages 27A and 27B provided at the center of the lead wire 29 through a guide hole 30 cut out in the upper bracket 5 of the piston rod 4, and by inputting a control signal (current) to this lead wire 29, The excitation force, in other words, the set load (valve opening pressure) of the expansion-side damping valve 20 can be adjusted continuously.
なお、リード線２９の導孔３０への取り出部に
は、合成樹旨などのシール材３２が封入してあ
り、油室C1，C2の作動油が配線通路２７Ａ，２
７Ｂから外部へとリークするのを防いでいる。 In addition, a sealing material 32 such as synthetic resin is sealed in the lead wire 29 to the guide hole 30, so that the hydraulic oil in the oil chambers C 1 and C 2 flows into the wiring passages 27A and 2.
This prevents leakage from 7B to the outside.
一方、シリンダ１の底部には別置のタンク３３
に連通する通孔３４が形成され、この通孔３４と
タンク３３と連通パイプ３５が接続している。 On the other hand, a separate tank 33 is installed at the bottom of the cylinder 1.
A through hole 34 is formed which communicates with the tank 33, and a communication pipe 35 is connected to the through hole 34.
タンク３３は内部にフリーピストン３６が摺動
自由に収装され、油溜室C3とガス室C4とを画成
する。 A free piston 36 is slidably housed inside the tank 33, and defines an oil reservoir chamber C3 and a gas chamber C4 .
ガス室C4には所定圧力で不活性なガス（空気）
が封入されており、フリーピストン３６を介して
油溜室C3の作動油を加圧する。 Gas chamber C 4 contains inert gas (air) at a specified pressure
is enclosed, and pressurizes the hydraulic oil in the oil reservoir chamber C3 via the free piston 36.
本発明は以上のように構成され、次にその制御
動作を含めて作用について説明する。 The present invention is constructed as described above, and its operation including its control operation will be explained next.
まず、第１図の状態からピストンロツド４がシ
リンダ１の内部へと進入する圧側作動時は、ピス
トン２の下降に伴い拡大する上部油室C1には縮
少する下部油室C2からの作動油が、ピストン２
の圧側バルブ孔２５から圧側チエツク弁２６を押
拡いてほとんど抵抗なく流入し、このとき伸側減
衰バルブ２０は油圧及びバルブスプリング２３力
でシート部２２に押圧されて密閉している。 First, during the pressure side operation when the piston rod 4 enters the inside of the cylinder 1 from the state shown in Fig. 1, the upper oil chamber C1 expands as the piston 2 descends, and the lower oil chamber C2 contracts. Oil is piston 2
The pressure side check valve 26 is pushed open from the compression side valve hole 25 of the valve 25 and flows in with almost no resistance, and at this time, the rebound side damping valve 20 is pressed against the seat portion 22 by the hydraulic pressure and the force of the valve spring 23 and is sealed.
一方、ピストンロツド４の進入体積分の作動油
は、下部油室C2からタンク３３の油溜室C3へと
流入する。 On the other hand, the hydraulic oil corresponding to the volume entered by the piston rod 4 flows from the lower oil chamber C 2 into the oil reservoir chamber C 3 of the tank 33 .
次に、ピストンロツド４が伸び出す伸側作動時
は、ピストン２の上昇に伴い縮少する上部油室
C1から拡大する下部油室C2に作動油が流入する
とともに、ピストンロツド４の抜け出し分の体積
に相当する作動油がタンク３３の油溜室C3から
補充される。 Next, during the extension side operation where the piston rod 4 extends, the upper oil chamber contracts as the piston 2 rises.
Hydraulic oil flows into the expanding lower oil chamber C 2 from C 1 and is replenished from the oil reservoir chamber C 3 of the tank 33 with hydraulic oil corresponding to the volume of the piston rod 4 that has slipped out.
このとき、タンク３３からの作動油は連通路３
５を介してほとんど抵抗なく下部油室C2に流入
するが、上部油室C1からの作動油には、ピスト
ン２の伸側減衰バルブ２０の設定荷重に応じての
流出抵抗が附与され、これが伸側減衰力として働
き、ピストンロツド４の伸側振動を減衰する。 At this time, the hydraulic oil from the tank 33 is transferred to the communication path 3.
5 into the lower oil chamber C2 with almost no resistance, but the hydraulic oil from the upper oil chamber C1 is given outflow resistance according to the set load of the expansion side damping valve 20 of the piston 2. , this acts as a rebound damping force and damps the vibration of the piston rod 4 on the rebound side.
この際、この伸側減衰バルブ２０の設定荷重
（バルブ開弁圧）は、前述したようにバルブスプ
リング２３の弾性力とこの弾性力に抗して伸側減
衰バルブ２０を吸引する電磁ソレノイド１８の吸
引力によつて決定される。つまり、電磁ソレノイ
ド１８の吸引力でバルブスプリングの弾性力（バ
ルブ設定圧力）を低減するのである。 At this time, the set load (valve opening pressure) of the expansion damping valve 20 is determined by the elastic force of the valve spring 23 and the electromagnetic solenoid 18 that attracts the expansion damping valve 20 against this elastic force, as described above. Determined by suction power. In other words, the attractive force of the electromagnetic solenoid 18 reduces the elastic force of the valve spring (valve setting pressure).
従つて、電磁ソレノイド１８のソレノイドコイ
ル１７に対する励磁電流に応じて上記吸引力は変
化し、これに伴つて伸側減衰バルブ２０の設定荷
重も連続的に変化して、結局第３図に示すよう
に、制御電流値に応じて減衰力を無段階に増減さ
せることができる。 Therefore, the above-mentioned attraction force changes in accordance with the excitation current applied to the solenoid coil 17 of the electromagnetic solenoid 18, and accordingly, the set load of the expansion-side damping valve 20 also changes continuously, and as a result, as shown in FIG. Furthermore, the damping force can be increased or decreased steplessly according to the control current value.
ここで、電磁ソレノイド１８に対しては、例え
ば、車速検出センサ、積載荷重検出センサ、緩衝
器変位検出センサ、制動検出センサ、発進加速検
出センサなどからの検出信号を演算処理する制御
回路を介して制御電流を供給し、運転状態に応じ
て最適な減衰力が得られるようにソレノイド吸引
力を制御すればよい。 Here, the electromagnetic solenoid 18 is controlled via a control circuit that calculates and processes detection signals from, for example, a vehicle speed detection sensor, a load detection sensor, a shock absorber displacement detection sensor, a braking detection sensor, and a starting acceleration detection sensor. It is sufficient to supply a control current and control the solenoid attraction force so as to obtain the optimum damping force according to the operating state.
ここで、第２図に示したように電磁ソレノイド
１８は、ボビン１６の中心部を貫通してピストン
ロツド４の先端部に螺着する固定軸１５を磁芯と
して、当該固定軸１５の端部からボビン１６を包
囲して減衰バルブ２０に至るカバー体１９により
閉磁路を形成するので、減衰バルブ２０に対して
効果的にソレノイドコイル１７の磁力を作用させ
ることができ、このため連続的に変化する励磁電
流に応じて高精度な減衰力の可変制御御が可能に
にる。 Here, as shown in FIG. 2, the electromagnetic solenoid 18 has a fixed shaft 15 that passes through the center of the bobbin 16 and is screwed onto the tip of the piston rod 4 as a magnetic core, and is formed from the end of the fixed shaft 15. Since a closed magnetic path is formed by the cover body 19 that surrounds the bobbin 16 and extends to the damping valve 20, the magnetic force of the solenoid coil 17 can be effectively applied to the damping valve 20, so that the magnetic force of the solenoid coil 17 changes continuously. This enables highly accurate variable control of the damping force in accordance with the excitation current.
そして、伸側減衰バルブ２０は、そのバルブ設
定圧力を電磁ソレノイド１８の電磁吸引力で低減
することにより、バルブ開弁圧を変化させるもの
であるから、従来のようないわゆる機械的な可動
部分がなく、そのため、ピストン２が激しく上下
動を繰り返したとしても、その慣性力で伸側減衰
バルブ２０の減衰力が変動するようなことがほと
んどないうえ、減衰力の変更を制御信号に応じて
連動的かつ正確に行えるのである。 Since the expansion-side damping valve 20 changes the valve opening pressure by reducing the valve setting pressure using the electromagnetic attraction force of the electromagnetic solenoid 18, there are no so-called mechanical moving parts as in the past. Therefore, even if the piston 2 repeatedly moves up and down violently, the damping force of the rebound damping valve 20 will hardly fluctuate due to its inertia force, and changes in the damping force are linked in accordance with the control signal. It can be done accurately and accurately.
尚、第２図では中心線を境にして図中下方に、
伸縮減衰バルブ２０を、前述した板バネからなる
バルブスプリング２３に代えて、その基端部がピ
ストン２の内壁面にスプリング受け３８を介して
担持されたコイルスプリング２３Ａによつて閉じ
側に付勢された他の例を示してある。 In addition, in Figure 2, below the center line,
The telescopic damping valve 20 is biased toward the closing side by a coil spring 23A whose base end is supported on the inner wall surface of the piston 2 via a spring receiver 38, instead of the valve spring 23 made of the above-described plate spring. Other examples are shown below.
更に上記実施例では伸側減衰力について説明し
たが、圧側減衰力においてもこの発明を適用でき
ることは言う迄もない。 Furthermore, although the above embodiments have been described with respect to the rebound damping force, it goes without saying that the present invention can also be applied to the compression damping force.
以上説明したように本発明によれば、車体の運
転状態に応じて時々刻々と変化する要求緩衝特性
を附与することができ、車両の乗心地を良好に保
ちつつ操安性の向上がはかれる。 As explained above, according to the present invention, it is possible to provide the required shock absorbing characteristics that change from moment to moment according to the driving condition of the vehicle body, and it is possible to improve the steering stability while maintaining the ride comfort of the vehicle. .
伸側、圧側の板状減衰バルブに閉磁路構成の電
磁ソレノイドの吸引力を及ぼしてその設定荷重を
連続的に調整するので、要求通りの特性を精度よ
く附与でき、また、とくに電磁ソレノイドの励磁
に伴つて機械的に作動する部分がないので、ピス
トン振動などの影響を受けずに、常に安定した動
作が保証できる。 The set load is continuously adjusted by applying the attractive force of the electromagnetic solenoid with a closed magnetic circuit to the plate-shaped damping valves on the expansion side and compression side. Since there are no parts that operate mechanically with excitation, stable operation can be guaranteed at all times without being affected by piston vibrations.
第１図は本発明の実施例の縦断面図、第２図は
そのピストン部の拡大断面図である。第３図は本
発明の作動特性を示す説明図である。
１……シリンダ、２……ピストン、４……ピス
トンロツド、１３……ピストンロツド段付部、１
６……ボビン、１７……ソレノイドコイル、１８
……電磁ソレノイド、２０……伸側減衰バルブ、
２１……バルブ孔、２２……シート部、１９……
カバー体、１９ａ……吸着部、１５……固定軸、
２３，２３Ａ……バルブスプリング。
FIG. 1 is a longitudinal sectional view of an embodiment of the present invention, and FIG. 2 is an enlarged sectional view of the piston portion thereof. FIG. 3 is an explanatory diagram showing the operating characteristics of the present invention. 1... Cylinder, 2... Piston, 4... Piston rod, 13... Piston rod stepped part, 1
6...Bobbin, 17...Solenoid coil, 18
...Electromagnetic solenoid, 20...Rebound side damping valve,
21... Valve hole, 22... Seat part, 19...
Cover body, 19a...Adsorption part, 15...Fixed shaft,
23, 23A...Valve spring.
Claims (1)
ストンの両面に油室を形成する一方、ピストンに
連結したピストンロツドの進入体積の変動分を吸
収するガス室を備えた油圧緩衝器において、ピス
トンの移動に伴つて作動油の流れる流路にバルブ
ボデイを固定し、このバルブボデイの内部に該バ
ルブボデイに設けたバルブ孔のシート部を開閉す
る磁性材からなる板状の減衰バルブを配設すると
共に、この減衰バルブを上記シート部から離間す
る方向にバルブスプリング力に抗して吸引する電
磁ソレノイドを収設し、かつこの電磁ソレノイド
は、ソレノイドコイルを巻き付けたボビンを該ボ
ビン及びバルブボデイを貫通する固定軸を介して
ピストンロツドの一端に締め付けた構成とすると
共に、前記固定軸の端部にソレノイドコイルを包
囲するカバー体を設けて固定軸を磁芯として該カ
バー体から減衰バルブにわたる閉磁路を形成し、
当該減衰バルブの開弁圧を電磁ソレノイドの吸引
力に応じて連続的に増減させるようにしたことを
特徴とする油圧緩衝器。1. In a hydraulic shock absorber, a piston is housed in a cylinder so that it can freely slide and oil chambers are formed on both sides of the piston, while a gas chamber is provided to absorb fluctuations in the entering volume of a piston rod connected to the piston. A valve body is fixed in a flow path through which hydraulic oil flows as it moves, and a plate-shaped damping valve made of a magnetic material is disposed inside the valve body to open and close the seat of a valve hole provided in the valve body. An electromagnetic solenoid is installed that attracts the damping valve in a direction away from the seat part against the force of the valve spring, and the electromagnetic solenoid connects a bobbin around which a solenoid coil is wound, and a fixed shaft passing through the bobbin and the valve body. and a cover body surrounding the solenoid coil is provided at the end of the fixed shaft to form a closed magnetic path from the cover body to the damping valve with the fixed shaft as a magnetic core,
A hydraulic shock absorber characterized in that the opening pressure of the damping valve is continuously increased or decreased in accordance with the suction force of an electromagnetic solenoid.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5802481A JPS57173630A (en) | 1981-04-17 | 1981-04-17 | Hydraulic buffer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5802481A JPS57173630A (en) | 1981-04-17 | 1981-04-17 | Hydraulic buffer |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57173630A JPS57173630A (en) | 1982-10-26 |
| JPS645174B2 true JPS645174B2 (en) | 1989-01-30 |
Family
ID=13072375
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5802481A Granted JPS57173630A (en) | 1981-04-17 | 1981-04-17 | Hydraulic buffer |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS57173630A (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4527676A (en) * | 1982-02-13 | 1985-07-09 | Atsugi Motor Parts Co., Ltd. | Variable-damping-force shock absorber |
| DE3422092A1 (en) * | 1984-06-14 | 1985-12-19 | Boge Gmbh, 5208 Eitorf | HYDRAULIC, ADJUSTABLE SINGLE TUBE SHOCK ABSORBER |
| US5217095A (en) * | 1986-06-05 | 1993-06-08 | Monroe Auto Equipment Company | Method and apparatus for absorbing mechanical shock |
| CA1263414A (en) * | 1986-06-05 | 1989-11-28 | Magnus Lizell | Restriction valve device for hydraulic pressure fluids in vehicle shock absorbing mechanisms |
| US4890858A (en) * | 1988-02-16 | 1990-01-02 | Monroe Auto Equipment Company | Method and apparatus for controlling shock absorbers |
| US4867475A (en) * | 1988-02-16 | 1989-09-19 | 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 |
| US5123671A (en) * | 1989-03-13 | 1992-06-23 | Monroe Auto Equipment Company | Method and apparatus for controlling shock absorbers |
| US5152379A (en) * | 1990-04-16 | 1992-10-06 | Monroe Auto Equipment Company | Adjustable shock absorber assembly |
| WO2013086761A1 (en) | 2011-12-14 | 2013-06-20 | Beijingwest Industries Co., Ltd. | Shock absorber system and method |
| DE102014106401A1 (en) * | 2014-05-07 | 2015-11-12 | Stabilus Gmbh | Infinitely lockable adjusting device |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4830793U (en) * | 1971-08-20 | 1973-04-14 | ||
| JPS6037477Y2 (en) * | 1979-12-03 | 1985-11-08 | トヨタ自動車株式会社 | buffer |
-
1981
- 1981-04-17 JP JP5802481A patent/JPS57173630A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS57173630A (en) | 1982-10-26 |
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