JPH0444130B2 - - Google Patents
Info
- Publication number
- JPH0444130B2 JPH0444130B2 JP8471884A JP8471884A JPH0444130B2 JP H0444130 B2 JPH0444130 B2 JP H0444130B2 JP 8471884 A JP8471884 A JP 8471884A JP 8471884 A JP8471884 A JP 8471884A JP H0444130 B2 JPH0444130 B2 JP H0444130B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- stroke
- damping force
- piston rod
- hollow piston
- 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 41
- 230000002093 peripheral effect Effects 0.000 claims description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 239000006096 absorbing agent Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000035939 shock 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
- F16F9/50—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
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Description
【発明の詳細な説明】
本発明は、ダンパーが作動したときのピストン
の移動速度が低速域時の減衰力だけを可変させ
得、乗り心地や操縦安定性を向上し得る減衰力可
変ダンパーに関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a variable damping force damper that can vary only the damping force when the piston is in a low speed range when the damper operates, thereby improving ride comfort and handling stability. It is.
近時、自動車類における乗心地と操縦安定性の
両立を計るためにシヨツクアブゾーバの減衰力を
路面状態、車速、ユーザーの走り方などによつて
変え得るいわゆる減衰力可変ダンパーを装着した
車種が増加して来ている。 Recently, in order to achieve both ride comfort and handling stability, automobile models are equipped with so-called variable damping force dampers that can change the damping force of the shock absorber depending on road conditions, vehicle speed, the user's driving style, etc. It is increasing.
しかしながら、従来の減衰力可変ダンパーは、
コンスタントオリフイスを変えることによつて油
量を制御し、これによつて減衰力を変化させる方
式がとられている。すなわち、第１図に示すよう
に、図中ａ曲線は使用状態がソフトの場合の減衰
力変化を、ｂ曲線はミデイアムの場合、ｃ曲線は
ハードの場合を示すのであるが、ピストン速度が
遅い所から速い所まで比例して減衰力が変化する
ものである。しかしながら、車の姿勢制御でロー
ルを押えるなどの操縦安定性の向上を計るピスト
ン速度領域は0.3m／ｓ以下でもあるにかかわら
ず高速領域（1.0m／ｓ以上）まで減衰力が比例
して上つてしまう結果、悪路や高速走行の乗り心
地が悪くなり、高速道路上のギヤツプの乗り越し
時にダンパーのストロークがなく大きな突き上げ
感が生じたり、車体の落ちつきが悪くなるなどと
いつた不具合が生じた。 However, conventional variable damping force dampers
A method is used in which the amount of oil is controlled by changing the constant orifice, thereby changing the damping force. In other words, as shown in Figure 1, the curve a in the figure shows the change in damping force when the usage condition is soft, the curve b shows the damping force change when the usage condition is medium, and the curve c shows the change when the usage condition is hard, but the piston speed is slow. The damping force changes proportionally from high speed to high speed. However, even though the piston speed range, which improves steering stability such as suppressing roll by controlling the car's attitude, is 0.3 m/s or less, the damping force increases proportionally up to high speed ranges (1.0 m/s or more). As a result, the ride becomes uncomfortable on rough roads or at high speeds, and problems such as the lack of damper stroke and a strong thrusting feeling when driving over a gear on the highway, and poor vehicle stability occur. .
本発明者らは、このような従来の不具合を解決
するために研究を重ねた結果、第２図に示すよう
にピストン速度の低中速域の減衰力、主として低
速域の減衰力可変巾を多くし、高速域の減衰力変
化は一定とすることによつて、しなやかな乗り心
地と、したたかな走りを実現させ得ることを見出
して本発明をなしたものである。 As a result of repeated research to solve these conventional problems, the inventors of the present invention have developed a damping force in the low and medium speed range of the piston speed, mainly the damping force variable range in the low speed range, as shown in Figure 2. The present invention was developed based on the discovery that by increasing the damping force and keeping the change in damping force constant in the high speed range, it is possible to achieve a supple ride and a strong running performance.
次に、添付の図面に基づいて本発明の実施例を
説明する。第３図は、本発明の減衰力可変ダンパ
ーの一実施例を示す側断面要部図、第４図は、第
３図中Ａ−Ａ線上の断面図Ａ及びＢ−Ｂ線上の断
面図Ｂ、第５図は、第３図中Ｃ方向からみた側断
平面図Ｃ及びＤ方向からみた側断平面図である。 Next, embodiments of the present invention will be described based on the accompanying drawings. FIG. 3 is a side cross-sectional view showing an embodiment of the variable damping force damper of the present invention, and FIG. 4 is a cross-sectional view A along the line A-A and a cross-sectional view B along the line B-B in FIG. , FIG. 5 is a side sectional plan view seen from direction C in FIG. 3, and a side sectional plan view seen from direction C and D in FIG.
１は、ダンパーのシリンダであつて、有底円筒
状をしており、所定量の油が充填されている。２
は、中空ピストンロツドであつて、シリンダ１内
へ挿入され、周壁に引行程用油孔３及び押行程用
油孔４，４′が半径方向に設けられている。５は、
ピストンであつて、前記中空ピストンロツド２の
先端に前記シリンダ１内を自在に摺動し得るよう
に装着されて前記シリンダ１内の油室を前記ピス
トンロツド２の先端側の油室イと反対側の油室ロ
とに区画し、ピストン５には軸方向に油路７と９
が設けられ、油路７は、油室ロ側に開口する引行
程用高速二乗孔６と連通しかつ油室イ側に開口
し、中空ピストンロツド２の引行程用油孔３に連
通する円周溝７′を有し、一方、油路９は、油室
イ側に開口する押行程用高速二乗孔８と連通しか
つ油室ロ側に開口し、中空ピストンロツド２の押
行程用油孔４に連通する円周溝９′を有し、引行
程用油路７の開口側に配置された引行程用デイス
クバルブ１０及び押行程用流路９の開口側に配置
された押行程用デイスクバルブ１１がそれぞれの
油路の開口側に取付けられ、さらに、その外周に
ピストンリング１２が嵌着されている。１３は、
セレクトバルブであつて、円筒状をし、その周壁
に半径方向に、前記中空ピストンロツド２の引行
程用油孔３に連通する径違いの複数個の低速二乗
孔１４と、同様に押行程用油孔４，４′に連通す
る径違いの複数個の低速二乗孔１５とが穿設さ
れ、前記中空ピストンロツド２の中空部に貫設さ
れて外部に設けた回動手段（図示せず）によつて
自在に回動し得るアジヤストロツド１６に固着さ
れて前記中空ピストンロツド２内を自在に摺回動
し得る。１７は、引行程用チエツクバルブであつ
て、前記中空ピストンロツド２の先端開口部に、
引行程時にだけ開くようにばね１８によつて弾止
され、押行程時に前記引行程用の低速二乗孔１４
に連通する引行程用油路１９を閉止するように設
けられている。一方、２０は、押行程用チエツク
バルブであつて、前記中空ピストンロツド２の押
行程用油孔４′に連通するように設けた油路２１
を閉止し、押行程時にだけ開くようにばね２２に
よつて弾止され、前記引行程用チエツクバルブ１
７の反対側で前記中空ピストンロツド２に固着さ
れている。 Reference numeral 1 denotes a damper cylinder, which has a cylindrical shape with a bottom and is filled with a predetermined amount of oil. 2
is a hollow piston rod inserted into the cylinder 1, and has oil holes 3 for the pulling stroke and oil holes 4, 4' for the pushing stroke provided in the radial direction on the peripheral wall. 5 is
A piston, which is attached to the tip of the hollow piston rod 2 so as to be able to freely slide inside the cylinder 1, and connects the oil chamber in the cylinder 1 to the oil chamber on the opposite side from the oil chamber 1 on the tip side of the piston rod 2. The piston 5 has oil passages 7 and 9 in the axial direction.
The oil passage 7 is provided with a circumferential passage 7 that communicates with the high-speed square hole 6 for the pulling stroke that opens on the oil chamber RO side, and that opens on the oil chamber A side and communicates with the oil hole 3 for the pulling stroke of the hollow piston rod 2. On the other hand, the oil passage 9 communicates with the high-speed square hole 8 for the pushing stroke that opens on the oil chamber A side and opens on the oil chamber RO side, and connects to the oil hole 4 for the pushing stroke of the hollow piston rod 2. A disc valve 10 for the pulling stroke, which has a circumferential groove 9' communicating with the oil passage 7, and a disc valve 10 for the pushing stroke, which is arranged on the opening side of the oil passage 9 for the pushing stroke. A piston ring 11 is attached to the opening side of each oil passage, and a piston ring 12 is fitted around the outer periphery thereof. 13 is
The select valve has a cylindrical shape, and has a plurality of low-speed square holes 14 of different diameters communicating with the oil hole 3 for the pulling stroke of the hollow piston rod 2 in the radial direction on its peripheral wall, as well as oil holes for the pushing stroke. A plurality of low-speed square holes 15 of different diameters are bored and communicated with the holes 4 and 4', and are inserted through the hollow part of the hollow piston rod 2 and rotated by a rotating means (not shown) provided outside. The piston rod 16 is fixed to an adjuster rod 16 that can freely rotate, and can slide and rotate freely within the hollow piston rod 2. Reference numeral 17 is a check valve for the retraction stroke, which is provided at the tip opening of the hollow piston rod 2.
It is resiliently stopped by a spring 18 so as to open only during the pulling stroke, and the low-speed square hole 14 for the pulling stroke is held open during the pushing stroke.
It is provided so as to close the drawing stroke oil passage 19 that communicates with the. On the other hand, 20 is a check valve for the pushing stroke, and an oil passage 21 is provided so as to communicate with the oil hole 4' for the pushing stroke of the hollow piston rod 2.
The check valve 1 for the pull stroke is stopped by a spring 22 so as to be closed and opened only during the push stroke.
7 is fixed to the hollow piston rod 2 on the opposite side.
本発明の減衰力可変ダンパーはこのように構成
されているので、運転者が外部に設けてある回動
手段を操作してアジヤストロツド１６を回動させ
ることによつてセレクトバルブ１３を回動させ、
セレクトバルブ１３の引行程用の低速二乗孔１４
と押行程用の低速二乗孔１５を任意の径のものに
選定して、それぞれ中空ピストンロツド２の引行
程用油孔３及び押行程用油孔４に合致させ連通す
るようにしておくと、ダンパーが作動して、たと
えば、引行程の場合には、中空ピストンロツド２
がシリンダ１の外方へ引き出されるにつれて、ピ
ストン５の移動速度が0.3m／ｓ前後までの低速
域では、油室ロの油は、ピストン２の引行程用高
速二乗孔６−引行程用油路７−セレクトバルブ１
３の引行程用の低速二乗孔１４を通つて、引行程
用油路１９を通り引行程用チエツクバルブ１７を
押し開いて油室イ中に流入する。さらにピストン
５の移動速度が速くなると引行程用デイスクバル
ブ１０をも押し開いて油室イ中に流入するように
なり減衰力は、低速二乗孔１４の開口面積とデイ
スクバルブの剛性によつて決まる。さらにピスト
ン５の移動速度が高速域になると油の流れは前記
と同様であるが減衰力は、主として引行程用高速
二乗孔６の流路面積だけに影響されるようにな
る。したがつて、セレクトバルブ１３の引行程用
低速二乗孔１４を適宜選定することによつて、低
速域での減衰力を第２図の(a)ソフト、(b)ミデイア
ム、(c)ハードのように変え得、低速域の間は、そ
れぞれに応じた減衰力が変化するが、高速域での
減衰力はどの場合でも略同じになるものである。
すなわち、第２図中、（）の範囲では低速二乗
孔１４による減衰力、（）の範囲では引行程用
デイスクバルブ１０と引行程用低速二乗孔１４と
による減衰力、（）の範囲では引行程用高速二
乗孔６による減衰力のようになるものである。 Since the variable damping force damper of the present invention is configured as described above, the driver operates an external rotating means to rotate the adjuster rod 16, thereby rotating the select valve 13.
Low speed square hole 14 for the pull stroke of the select valve 13
If the low speed square hole 15 for the push stroke is selected to have an arbitrary diameter and is made to match and communicate with the oil hole 3 for the pull stroke and the oil hole 4 for the push stroke of the hollow piston rod 2, the damper is activated, for example, in the case of a retraction stroke, the hollow piston rod 2
As the piston 5 is pulled out of the cylinder 1, in the low-speed range where the piston 5 moves at a speed of around 0.3 m/s, the oil in the oil chamber B is transferred to the high-speed square hole 6 for the retraction stroke of the piston 2. Route 7-Select valve 1
It passes through the low-speed square hole 14 for the retraction stroke No. 3, passes through the oil passage 19 for the retraction stroke, pushes open the check valve 17 for the retraction stroke, and flows into the oil chamber. Furthermore, as the moving speed of the piston 5 increases, the disc valve 10 for the pulling stroke is also pushed open and the oil flows into the oil chamber I, and the damping force is determined by the opening area of the low speed square hole 14 and the rigidity of the disc valve. . Further, when the moving speed of the piston 5 reaches a high speed range, the oil flow is the same as described above, but the damping force is mainly influenced only by the flow path area of the high speed square hole 6 for the retraction stroke. Therefore, by appropriately selecting the low speed square hole 14 for the pull stroke of the select valve 13, the damping force in the low speed range can be adjusted to (a) soft, (b) medium, and (c) hard in Fig. 2. The damping force can be changed as shown in FIG.
That is, in Fig. 2, the damping force is due to the low speed square hole 14 in the range (), the damping force due to the pulling stroke disc valve 10 and the low speed square hole 14 for the pulling stroke, and the damping force is in the range () due to the low speed square hole 14. This is similar to the damping force produced by the high-speed square hole 6 for stroke.
又、押行程時も、前記と同様にして低速域の減
衰力を可変とし、高速域では一定とすることがで
きる。 Also, during the push stroke, the damping force can be made variable in the low speed range and constant in the high speed range in the same way as described above.
第６図は、本発明の減衰力可変ダンパーの別の
実施例を示す側断面要部図であり、第７図は、第
６図中のＥ−Ｅ線上断面図Ｅ及びＦ−Ｆ線上断面
図Ｆである。 FIG. 6 is a side cross-sectional view showing another embodiment of the variable damping force damper of the present invention, and FIG. This is Figure F.
しかして、この例では、引行程用チエツクバル
ブ１７及び押行程用チエツクバルブ２０をそれぞ
れ引行程用デイスクバルブ１０及び押行程用デイ
スクバルブ１１の中側に設けたものであり、減衰
力は、前例と同様にピストン速度が低速域では可
変とし、高速域では一定となし得るものである。 Therefore, in this example, the check valve 17 for the pull stroke and the check valve 20 for the push stroke are provided inside the disk valve 10 for the pull stroke and the disk valve 11 for the push stroke, respectively, and the damping force is different from that in the previous example. Similarly, the piston speed can be made variable in the low speed range and constant in the high speed range.
なお、本発明におけるセレクトバルブ１３に設
ける径違いの低速二乗孔は、引行程用及び押行程
用の両方をともに設けることは必ずしも必要では
なく、いずれか一方の径違いの低速二乗孔を設け
ることによつても同様に作動させ得、いずれか一
方の行程において同様な効果を得ることができる
ものである。 Note that it is not necessarily necessary to provide the low-speed square holes with different diameters in the select valve 13 in the present invention for both the pull stroke and the push stroke. The same effect can be obtained in either one of the strokes.
しかして、たとえば、引行程用に径違いの低速
二乗孔を設けた場合には、引行程用の部材の関係
はすべて前述と同様に設ければよく、押行程用の
減衰力可変部材、たとえば、中空ピストンロツド
２の押行程用油孔４、ピストン５の押行程用高速
二乗孔８、セレクトバルブ１３の押行程用の径違
いの複数個の低速二乗孔１５、押行程用チエツク
バルブ２０などを設けることなく、ピストン５の
押行程用油路９を油室イ及び油室ロの両方に開口
するように貫通し、この部分で一定の減衰力を発
生するようにすることができる。逆に、押行程に
だけ設置する場合には、前記に対応する引行程用
減衰力可変部材を設けることなく、たとえば、引
行程用油路７を油室イ及び油室ロにともに開口す
るように貫通し、この部分で一定の減衰力を発生
するようにすることもできる。 For example, if a low-speed square hole with a different diameter is provided for the pulling stroke, all the members for the pulling stroke may be provided in the same manner as described above, and a variable damping force member for the pushing stroke, such as , an oil hole 4 for the push stroke of the hollow piston rod 2, a high speed square hole 8 for the push stroke of the piston 5, a plurality of low speed square holes 15 of different diameters for the push stroke of the select valve 13, a check valve 20 for the push stroke, etc. Instead, the oil passage 9 for the pushing stroke of the piston 5 can be passed through so as to be open to both the oil chambers A and B, and a certain damping force can be generated in this portion. On the other hand, if it is installed only in the pushing stroke, the damping force variable member for the pulling stroke corresponding to the above is not provided, and for example, the oil passage 7 for the pulling stroke is opened in both oil chamber A and oil chamber B. It is also possible to penetrate through the area and generate a certain damping force in this part.
本発明は、セレクトバルブに径違いの複数個の
低速二乗孔を設けて任意の低速二乗孔を選定し得
るようにし、ピストンに一定径の高速二乗孔を設
けたので、ピストンの移動速度が低速域では発生
する減衰力を可変とし得、高速域ではどの場合で
も一定となるようになし得、路面状態、車速、ユ
ーザーの走り方などによつても常にしなやかな乗
り心地と、したたかな走りが得られ操縦安定性に
すぐれているなどすぐれた効果が認められる。 In the present invention, the select valve is provided with a plurality of low-speed square holes of different diameters so that any low-speed square hole can be selected, and the piston is provided with a high-speed square hole of a constant diameter, so that the moving speed of the piston is reduced to a low speed. The damping force generated can be made variable in the high-speed range, and constant in all cases in the high-speed range, resulting in a supple ride and strong driving, regardless of road conditions, vehicle speed, user driving style, etc. It has been recognized that it has excellent effects, such as improved steering stability and improved steering stability.
第１図は、従来の減衰力可変ダンパーの減衰力
特性曲線図、第２図は、本発明の減衰力可変ダン
パーの減衰力特性曲線図、第３図は、本発明の減
衰力可変ダンパーの一実施例を示す側断面要部
図、第４図は、第３図中Ａ−Ａ線上の断面図Ａ及
びＢ−Ｂ線上の断面図Ｂ、第５図は、第３図中Ｃ
方向からみた側断平面図Ｃ及びＤ方向からみた側
断平面図Ｄ、第６図は、本発明の減衰力可変ダン
パーの別の実施例を示す側断面要部図、第７図
は、第６図中Ｅ−Ｅ線上の断面図Ｅ及びＦ−Ｆ線
上の断面図Ｆである。
１…シリンダ、２…中空ピストンロツド、３…
引行程用油孔、４，４′…押行程用油孔、５…ピ
ストン、６…引行程用高速二乗孔、７…引行程用
油路、８…押行程用高速二乗孔、９…押行程用油
路、１２…ピストンリング、１０…引行程用デイ
スクバルブ、１１…押行程用デイスクバルブ、１
３…セレクトバルブ、１４…引行程用低速二乗
孔、１５…押行程用低速二乗孔、１６…アジヤス
トロツド、１７…引行程用チエツクバルブ、１
８，２２…ばね、１９…引行程用油路、２０…押
行程用チエツクバルブ、２１…油路、イ，ロ…油
室。
FIG. 1 is a damping force characteristic curve diagram of a conventional variable damping force damper, FIG. 2 is a damping force characteristic curve diagram of a variable damping force damper of the present invention, and FIG. 3 is a diagram of a damping force characteristic curve of a variable damping force damper of the present invention. FIG. 4 is a side cross-sectional view of the main part showing one embodiment, and FIG. 4 is a cross-sectional view A on the line A-A in FIG.
6 is a side sectional plan view showing another embodiment of the variable damping force damper of the present invention, and FIG. 7 is a side sectional plan view showing another embodiment of the variable damping force damper of the present invention. 6 is a cross-sectional view E taken along the line E-E and a cross-sectional view F taken along the line F-F in FIG. 6. 1...Cylinder, 2...Hollow piston rod, 3...
Oil hole for pull stroke, 4, 4'...Oil hole for push stroke, 5...Piston, 6...High speed square hole for pull stroke, 7...Oil passage for pull stroke, 8...High speed square hole for push stroke, 9...Push stroke Oil passage for stroke, 12... Piston ring, 10... Disc valve for pull stroke, 11... Disc valve for push stroke, 1
3... Select valve, 14... Low speed square hole for pull stroke, 15... Low speed square hole for push stroke, 16... Adjust stroke rod, 17... Check valve for pull stroke, 1
8, 22... Spring, 19... Oil passage for pulling stroke, 20... Check valve for pushing stroke, 21... Oil passage, A, B... Oil chamber.
Claims (1)
油孔を半径方向に設けかつシリンダ内に挿入され
た中空ピストンロツド、該中空ピストンロツドの
先端に前記シリンダ内を摺動自在に装着されると
ともに前記シリンダ内の油室を２つの油室に区画
し一方側は一方の油室に開口しかつ前記中空ピス
トンロツドに設けた油孔に連通し他方側は高速二
乗孔に連通して他方の油室に開口する油路を設け
該油路の開口側に配置されたデイスクバルブを設
けたピストン、前記中空ピストンロツド内にアジ
ヤストロツドに固着されて回動自在に摺設され前
記中空ピストンの油孔に連通する径違いの複数個
の低速二乗孔を周壁に半径方向に設けたセレクト
バルブ、引行程時又は押行程時にだけ開かれるよ
うに前記油路に設けられたチエツクバルブからな
ることを特徴とする減衰力可変ダンパー。1. A cylinder filled with a predetermined amount of oil, a hollow piston rod with oil holes provided in the radial direction on its circumferential wall and inserted into the cylinder, and a hollow piston rod fitted to the tip of the hollow piston rod so as to be able to slide freely within the cylinder. The inner oil chamber is divided into two oil chambers, one side opens into one oil chamber and communicates with an oil hole provided in the hollow piston rod, and the other side communicates with a high-speed square hole and opens into the other oil chamber. a piston provided with an oil passage and a disc valve disposed on the opening side of the oil passage, and a piston with a different diameter that is fixed to an adjusting rod within the hollow piston rod so as to be rotatable and communicates with the oil hole of the hollow piston. A variable damping force damper comprising a select valve having a plurality of low-speed square holes provided in the peripheral wall in the radial direction, and a check valve provided in the oil passage so as to be opened only during the pulling stroke or the pushing stroke. .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8471884A JPS60227031A (en) | 1984-04-26 | 1984-04-26 | Variable-damping force damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8471884A JPS60227031A (en) | 1984-04-26 | 1984-04-26 | Variable-damping force damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60227031A JPS60227031A (en) | 1985-11-12 |
| JPH0444130B2 true JPH0444130B2 (en) | 1992-07-20 |
Family
ID=13838457
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8471884A Granted JPS60227031A (en) | 1984-04-26 | 1984-04-26 | Variable-damping force damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60227031A (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61189338A (en) * | 1985-02-13 | 1986-08-23 | Kayaba Ind Co Ltd | Damping force adjusting structure of shock absorber |
| JPH0425548Y2 (en) * | 1986-08-13 | 1992-06-18 | ||
| JPH0519626Y2 (en) * | 1986-10-06 | 1993-05-24 | ||
| DE3925470C2 (en) * | 1988-08-02 | 1996-04-18 | Atsugi Motor Parts Co Ltd | Shock absorbers with a damping valve construction with a variable damping characteristic within a wide range |
| JPH0740746Y2 (en) * | 1989-02-14 | 1995-09-20 | 株式会社ユニシアジェックス | Variable damping force type hydraulic shock absorber |
| JP2578901Y2 (en) * | 1989-09-20 | 1998-08-20 | 株式会社ユニシアジェックス | Variable damping force type hydraulic shock absorber |
| KR100445985B1 (en) * | 2000-11-24 | 2004-08-25 | 주식회사 만도 | Valve structure for use in a shock absorber |
-
1984
- 1984-04-26 JP JP8471884A patent/JPS60227031A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60227031A (en) | 1985-11-12 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |