JP2986867B2 - Damping force adjustment device - Google Patents
Damping force adjustment deviceInfo
- Publication number
- JP2986867B2 JP2986867B2 JP2202283A JP20228390A JP2986867B2 JP 2986867 B2 JP2986867 B2 JP 2986867B2 JP 2202283 A JP2202283 A JP 2202283A JP 20228390 A JP20228390 A JP 20228390A JP 2986867 B2 JP2986867 B2 JP 2986867B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- damping force
- damping
- pressure
- flexible
- 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 - Fee Related
Links
Landscapes
- Vehicle Body Suspensions (AREA)
- Fluid-Damping Devices (AREA)
Description
【発明の詳細な説明】 （産業上の利用分野） この発明は車両のダンパの減衰力調整装置に関する。The present invention relates to a damping force adjusting device for a vehicle damper.
（従来の技術） 車両のダンパにあっては、圧側と伸側作動時の少なく
とも一方で作動油の流れる通路にリリーフ弁を設け、そ
の設定荷重を外部からの制御圧力に応じて変化させるこ
とにより、通常走行時の乗り心地や操安性を良好に維持
するための減衰特性の調整にとどまらず、例えば旋回走
行時や制動時でのアンチロールやアンチダイブ制御のた
めの高い減衰力を発生させることができるようにしたも
のが知られている（特開昭57−95281号公報など）。(Related Art) In a vehicle damper, a relief valve is provided in a passage through which hydraulic oil flows at least at one of a compression side operation and an extension side operation, and a set load thereof is changed according to an external control pressure. In addition to adjusting the damping characteristics to maintain good riding comfort and maneuverability during normal driving, it generates high damping force for anti-roll and anti-dive control during turning and braking, for example. There is known a device capable of performing such a process (Japanese Patent Application Laid-Open No. 57-95281).
（発明が解決しようとする課題） ところでこの場合、リリーフ弁の設定荷重は単に外部
からの制御圧力に比例して変化するにすぎず、したがっ
て車両の旋回走行時や制動の時などで通常走行時に較べ
てリリーフ弁に供給する制御圧力を大幅に変化させるこ
とが必要で、そのため制御圧力の回路構成が複雑なもの
となり、装置全体の大型化やコストの上昇を招くという
問題点があった。(Problems to be Solved by the Invention) In this case, the set load of the relief valve merely changes in proportion to the control pressure from the outside, and therefore, during normal running such as when the vehicle is turning or braking. In comparison, the control pressure to be supplied to the relief valve must be greatly changed, so that the circuit configuration of the control pressure becomes complicated, and there is a problem that the whole apparatus becomes large and the cost increases.
この発明はこのような問題点を解決することを目的と
する。An object of the present invention is to solve such a problem.
（課題を解決するための手段） そのため、この発明はダンパの圧側と伸側作動時の少
なくとも一方で作動油の流れる通路に板状の可撓弁をバ
ルブシートに向けて移動可能に設けると共に、この可撓
弁を外部からの制御圧力に応じて移動させる調整手段を
設け、可撓弁がバルブシートと離間する移動範囲で可変
絞り弁として、バルブシートに接触する移動範囲で設定
荷重の変化する圧力制御弁として、さらに弁の可撓量が
制限される位置で閉止弁として機能するように構成した
ものである。(Means for Solving the Problems) Therefore, the present invention provides a plate-shaped flexible valve movably toward a valve seat in a passage in which hydraulic oil flows in at least one of the pressure side and the expansion side of the damper, Adjusting means for moving the flexible valve in accordance with an external control pressure is provided. The variable valve is a variable throttle valve in a moving range in which the flexible valve is separated from the valve seat, and a set load changes in a moving range in contact with the valve seat. The pressure control valve is further configured to function as a closing valve at a position where the amount of flexibility of the valve is limited.
（作用） 板状の可撓弁は外部からの制御圧力に応じて移動し、
これに伴って可変絞り弁から設定荷重の変化する圧力制
御弁、さらに閉止弁と機能変化するため、制御圧力を大
きく変化させることなく、発生減衰力の大幅な調整が可
能となる。(Operation) The plate-shaped flexible valve moves in response to an external control pressure,
Accordingly, the function changes from the variable throttle valve to the pressure control valve in which the set load changes, and further to the shutoff valve, so that the generated damping force can be largely adjusted without greatly changing the control pressure.
（実施例） 第１〜３図において、ダンパ１はシリンダ20に挿入し
たピストンロッド21の先端にピストン22が取付けられ、
シリンダ20の内部を２つの油室23A、23Bに画成してい
る。(Embodiment) In FIGS. 1 to 3, a damper 1 has a piston 22 attached to the tip of a piston rod 21 inserted into a cylinder 20,
The inside of the cylinder 20 is defined by two oil chambers 23A and 23B.
シリンダ20の外側にはアウターチューブ24が同心的に
配設され、シリンダ20との間に環状の油溜室25を形成す
る。An outer tube 24 is arranged concentrically outside the cylinder 20 and forms an annular oil reservoir 25 between the outer tube 24 and the cylinder 20.
前記ピストン22には油室23Bから23Aに向けてのみ作動
油の流通を許容するチェックバルブ26が、またシリンダ
20の底部には油溜室25から油室23Bへのみ作動油の流通
を許容するチェックバルブ27が設けられる。The piston 22 is provided with a check valve 26 that permits the flow of hydraulic oil only from the oil chambers 23B to 23A, and a cylinder.
At the bottom of 20, a check valve 27 is provided which allows the flow of hydraulic oil only from oil reservoir 25 to oil chamber 23B.
一方、油室23Aと油溜室25とを結ぶ通路30の途中に
は、減衰力調整バルブ３が設けられ、作動油の流れに抵
抗を付与することにより圧側、伸側作動に対する減衰力
を発生させる。On the other hand, a damping force adjustment valve 3 is provided in the middle of the passage 30 connecting the oil chamber 23A and the oil reservoir chamber 25, and generates a damping force for the compression side and the expansion side operation by imparting resistance to the flow of the hydraulic oil. Let it.
つまり、ピストン22が下方に移動する圧側作動時に
は、圧縮される油室23Bの作動油はピストン22のチェッ
クバルブ26を経由して拡大する油室23Aに流れ込み、さ
らにピストンロッド21の侵入体積分に相当する作動油は
通路30から油溜室25へと流出し、また、ピストン22が上
方に移動する伸側作動時にはピストン22のチェックバル
ブ26が閉じるので、圧縮される油室23Aの作動油は通路3
0から油溜室25へと流れ、拡大する油室23Bに対しては底
部のチェックバルブ27を介して油溜室25から作動油が補
充されるのであり、圧側、伸側のいずれの作動に対して
も作動油は通路30を経由して油溜室25へと循環するよう
になっていて、この通路30の途中の減衰力調整バルブ３
の抵抗に応じて所定の圧側、伸側減衰力を発生させるの
である。That is, when the piston 22 moves downward on the pressure side, the hydraulic oil in the oil chamber 23B to be compressed flows into the expanding oil chamber 23A via the check valve 26 of the piston 22, and further into the invading volume of the piston rod 21. The corresponding hydraulic oil flows out from the passage 30 into the oil reservoir 25, and when the piston 22 moves upward, the check valve 26 of the piston 22 is closed. Passage 3
The oil flows from 0 to the oil sump chamber 25, and the expanding oil chamber 23B is replenished with hydraulic oil from the oil sump chamber 25 via the check valve 27 at the bottom. On the other hand, the hydraulic oil is circulated to the oil reservoir 25 via the passage 30, and the damping force adjusting valve 3
A predetermined damping force on the compression side and on the extension side is generated in accordance with the resistance.
通路30はシリンダ20の上部のベアリング部31に設けた
通口32に接続し、シリンダ20を上下に貫通する管路とし
て形成され、減衰力調整バルブ３はアウターチューブ外
部から取付られている。The passage 30 is connected to a passage 32 provided in a bearing portion 31 at the upper part of the cylinder 20, and is formed as a pipe vertically penetrating the cylinder 20, and the damping force adjusting valve 3 is attached from the outside of the outer tube.
第３図に明らかなように、減衰力調整バルブ３は円筒
状のバルブボディ35の両端がキャップ36とロッドガイド
37でそれぞれ閉塞される。As is apparent from FIG. 3, the damping force adjusting valve 3 has a cylindrical valve body 35 having a cap 36 and a rod guide at both ends.
Each is closed at 37.
バルブボディ35の内部は隔壁部材38、39により３つの
室40A〜40Cに仕切られ、隔壁部材38に室40Aと40Bを連通
する通路41が、また隔壁部材39に室40Aと40Cを連通する
通路42が形成される。The inside of the valve body 35 is partitioned into three chambers 40A to 40C by partition members 38 and 39, and a passage 41 communicating the chambers 40A and 40B to the partition member 38 and a passage communicating the chambers 40A and 40C to the partition member 39. 42 is formed.
隔壁部材38、39にはこれらを貫通して室40Bと40Cを連
通する中空ボルト43が設けられ、そのボルト43頭部に後
述する第２の減衰バルブとしての板状の可撓弁44と対向
するシート部45が形成される。The partition members 38 and 39 are provided with hollow bolts 43 penetrating therethrough and communicating the chambers 40B and 40C, and the head of the bolt 43 faces a plate-shaped flexible valve 44 as a second damping valve described later. The sheet portion 45 is formed.
46はバルブボディ35内部の室40Aを油室23A側の通路30
に、47は同じく室40Cを油溜室25側の通路30にそれぞれ
接続する通孔を示す。Reference numeral 46 designates the passage 30 on the oil chamber 23A side with the chamber 40A inside the valve body 35.
Reference numeral 47 denotes a through hole for connecting the chamber 40C to the passage 30 on the oil reservoir 25 side.
隔壁部材38には通路41を開閉する第１の減衰バルブと
しての第１の可撓弁48が設けられ、そのシート部49を常
に開口する小さな切欠き50（オリフィス）が形成され
る。The partition member 38 is provided with a first flexible valve 48 as a first damping valve for opening and closing the passage 41, and has a small notch 50 (orifice) that always opens the seat portion 49 thereof.
第１の可撓弁48は中空ボルト43外周で隔壁部材38のシ
ート部49につき当て、スペーサ51との間にバネ受52とシ
ム53を挟み込むことにより内周部にて支持される。The first flexible valve 48 is abutted against the seat portion 49 of the partition member 38 at the outer periphery of the hollow bolt 43, and is supported at the inner periphery by sandwiching the spring receiver 52 and the shim 53 between the spacer 51 and the first flexible valve 48.
また、54は隔壁部材39の通路42を開閉するオーバロー
ド用のリリーフ弁で、中空ロッド43外周でバネ受55との
間に介装したセットスプリング56でシート部57に付勢さ
れる。58はバネ受55を支持するナットを示す。An overload relief valve 54 for opening and closing the passage 42 of the partition member 39 is urged toward the seat 57 by a set spring 56 interposed between the hollow rod 43 and the spring receiver 55. Reference numeral 58 denotes a nut that supports the spring receiver 55.
一方、ロッドガイド37には摺動自由なロッド59が設け
られ、その室40B内に突出する先端にカップ60が結合さ
れる。On the other hand, the rod guide 37 is provided with a freely slidable rod 59, and a cup 60 is coupled to a tip projecting into the chamber 40B.
カップ60内には第２の可撓弁44が外周部にて、一端を
バネ受52に担持したバランスバネ61によりシム62との間
で挟持される。In the cup 60, a second flexible valve 44 is clamped at an outer peripheral portion thereof between a shim 62 and a balance spring 61 having one end supported by a spring receiver 52.
ロッド59の後端はシート63を介してダイヤフラム64に
連結され、ダイヤフラム64の作動圧室65に外部から運転
状態に応じて変化する制御圧力（パイロット圧）が導入
される。66はダイヤフラム64の作動圧室65を外部の制御
圧回路に接続する導圧口67を持つプラグ、68はダイヤフ
ラム64の背圧室69を大気解放する通孔を示す。The rear end of the rod 59 is connected to a diaphragm 64 via a seat 63, and a control pressure (pilot pressure) that varies according to the operation state is introduced into the working pressure chamber 65 of the diaphragm 64 from outside. 66 is a plug having a pressure guiding port 67 for connecting the working pressure chamber 65 of the diaphragm 64 to an external control pressure circuit, and 68 is a through hole for releasing the back pressure chamber 69 of the diaphragm 64 to the atmosphere.
なお第１図において、ピストンロッド21の内部にはフ
リーピストン70によって仕切られたガス室71が形成さ
れ、フリーピストン70の端面には油室23Aの圧力が導か
れ、減衰力調整バルブ３が閉じているロック状態での急
激な荷重増大時にフリーピストン70が変位し、衝撃を吸
収するようになっている。In FIG. 1, a gas chamber 71 partitioned by a free piston 70 is formed inside the piston rod 21. The pressure of the oil chamber 23A is guided to the end face of the free piston 70, and the damping force adjusting valve 3 is closed. When the load suddenly increases in the locked state, the free piston 70 is displaced to absorb a shock.
以上のように構成され、次に作用について説明する。 The configuration is as described above. Next, the operation will be described.
ピストンロッド21の伸縮に伴い、いずれの方向につい
ても油室23Aから作動油が通路30を経由して油溜室25へ
と流れ、したがって伸側、圧側のいずれにも減衰力調整
バルブ３の抵抗に応じて減衰力が発生する。With the expansion and contraction of the piston rod 21, the hydraulic oil flows from the oil chamber 23A through the passage 30 to the oil reservoir 25 in any direction, and therefore the resistance of the damping force adjusting valve 3 is increased on both the extension side and the compression side. Generates a damping force.
第２の可撓弁44はダイヤフラム64の作動圧室65に導か
れる制御圧力が低圧のとき、ロッド59がバランスバネ61
の付勢力などにより押し出され、カップ60がロッドガイ
ド37につき当たる位置で作動油のフリーフローを許容す
る。When the control pressure guided to the working pressure chamber 65 of the diaphragm 64 is low, the second flexible valve 44 moves the rod 59 to the balance spring 61.
When the cup 60 comes into contact with the rod guide 37, the hydraulic oil is allowed to flow freely.
このとき、オリフィス50がピストンロッド21の作動初
期において油室23Aから油溜室25へと流れる作動油に所
定の減衰抵抗を付与すると共に、オリフィス50前後の差
圧が設定値以上になると第１の可撓弁48が開いて、撓み
量に応じた減衰力を発生させる。At this time, the orifice 50 imparts a predetermined damping resistance to the hydraulic oil flowing from the oil chamber 23A to the oil reservoir 25 in the early stage of the operation of the piston rod 21, and the first pressure is set when the differential pressure across the orifice 50 exceeds a set value. The flexible valve 48 opens to generate a damping force corresponding to the amount of bending.
これに対して、ダイヤフラム64の作動圧室65に導かれ
る制御圧力を高めると、ダイヤフラム64の推力を受けて
ロッド59が室40B内に押し込まれ、これにより第２の可
撓弁44が可変絞り弁として機能し、バルブシート45に接
近するに伴って発生減衰力を上昇させる。On the other hand, when the control pressure guided to the working pressure chamber 65 of the diaphragm 64 is increased, the rod 59 is pushed into the chamber 40B by receiving the thrust of the diaphragm 64, and thereby the second flexible valve 44 is moved to the variable throttle. It functions as a valve and increases the generated damping force as it approaches the valve seat 45.
さらに制御圧力を高めると、第２の可撓弁44はバルブ
シート45に接触する時点からロッド59の移動量に応じて
設定荷重（弁44のカップ60内への初期撓み量）の変化す
るリリーフ弁として機能し、高い減衰力を発生する。When the control pressure is further increased, the second flexible valve 44 is a relief whose set load (the amount of initial deflection of the valve 44 into the cup 60) changes according to the amount of movement of the rod 59 from the point of contact with the valve seat 45. Functions as a valve and generates high damping force.
第２の可撓弁44はロッド59がさらに移動すると、バル
ブシート45とカップ60との間で可撓量が制限される位置
で閉止弁として機能し、中空ボルト43を経由する作動油
の流れを遮断する。このとき、油室23Aの圧力が所定値
以上になると、オーバロード用のリリーフ弁54が開いて
油溜室25に作動油を逃がすのである。When the rod 59 moves further, the second flexible valve 44 functions as a shut-off valve at a position where the amount of flexibility between the valve seat 45 and the cup 60 is limited, and the flow of hydraulic oil via the hollow bolt 43 Cut off. At this time, when the pressure in the oil chamber 23A becomes equal to or higher than a predetermined value, the relief valve 54 for overload is opened and the hydraulic oil is released into the oil reservoir 25.
したがって、減衰力調整バルブ３は外部からの制御圧
力を加減することにより、第４図で示すように減衰特性
が変化するので、通常走行時の乗り心地や操安性を良好
に維持するための減衰力の調整にとどまらず、例えば旋
回走行時や制御時でのアンチロールやアンチダイブ制御
のための高い減衰力を発生させることができる。Accordingly, the damping force adjusting valve 3 changes the damping characteristic as shown in FIG. 4 by increasing or decreasing the control pressure from the outside, so that the riding comfort and the operability during normal running can be maintained well. In addition to the adjustment of the damping force, it is possible to generate a high damping force for anti-roll and anti-dive control, for example, during cornering and control.
この場合、第２の可撓弁44は外部からの制御圧力に応
じて移動し、これに伴って機能自体がフリーフローから
可変絞り弁、設定荷重の変化するリリーフ弁、さらに閉
止弁と変化するため、制御圧力を大きく加減することな
く、発生減衰力の大幅な調整が可能となる。In this case, the second flexible valve 44 moves according to the control pressure from the outside, and the function itself changes from free flow to a variable throttle valve, a relief valve with a set load changing, and further a closing valve. Therefore, it is possible to largely adjust the generated damping force without greatly increasing or decreasing the control pressure.
なお、第５図は第２の可撓弁44の減衰特性を示すもの
で、第２の可撓弁44は可変絞り域でバルブシート45に近
接するに伴って作動油圧力に押されてカップ60の内側に
撓むため、実際にはオリフィス開度（a1〜a5）と撓み量
Ｖとの合成特性（a1＋V2〜a5＋V2）として減衰力を発生
する。FIG. 5 shows the damping characteristic of the second flexible valve 44. The second flexible valve 44 is pushed by hydraulic oil pressure as it approaches the valve seat 45 in the variable throttle region, and Since it bends inside 60, a damping force is actually generated as a combined characteristic (a 1 + V 2 -a 5 + V 2 ) of the orifice opening (a 1 -a 5 ) and the amount of deflection V.
（発明の効果） 以上要するにこの発明によれば、ダンパの圧側と伸側
作動時の少なくとも一方で作動油の流れる通路に板状の
可撓弁をバルブシートに向けて移動可能に設けると共
に、この可撓弁を外部からの制御圧力に応じて移動させ
る調整手段を設け、可撓弁がバルブシートと離間する移
動範囲で可変絞り弁として、バルブシートに接触する移
動範囲で設定荷重の変化する圧力制御弁として、さらに
弁の可撓量が制限される位置で閉止弁として機能するよ
うに構成したので、外部からの制御圧力を大きく変化さ
せることなく発生減衰力の大幅な調整が可能となり、し
たがって制御圧力の回路構成の簡略化とコストダウンが
はかれるという効果が得られる。(Effects of the Invention) In summary, according to the present invention, a plate-shaped flexible valve is movably provided toward a valve seat in a passage in which hydraulic oil flows at least at one of a compression side operation and an extension side operation of a damper. An adjusting means for moving the flexible valve in accordance with an external control pressure is provided. The variable valve is a variable throttle valve in a moving range where the flexible valve is separated from the valve seat, and a pressure at which a set load changes in a moving range in contact with the valve seat. As a control valve, the valve is configured to function as a closing valve at a position where the amount of flexibility of the valve is limited, so that the generated damping force can be largely adjusted without greatly changing the control pressure from the outside. This has the effect of simplifying the circuit configuration of the control pressure and reducing the cost.
第１図はこの発明の実施例を示すダンパ全体の断面図、
第２図は同じく回路構成図、第３図は同じく減衰力調整
バルブの断面図、第４図と第５図はそれぞれ減衰力の特
性図である。 １……ダンパ、３……減衰力調整バルブ、44……板状可
撓弁、45……バルブシート、59……ロッド、61……バラ
ンスバネ、64……ダイヤフラム。FIG. 1 is a sectional view of an entire damper showing an embodiment of the present invention,
FIG. 2 is a circuit configuration diagram, FIG. 3 is a sectional view of the damping force adjusting valve, and FIGS. 4 and 5 are characteristic diagrams of the damping force, respectively. 1 damper, 3 damping force adjustment valve, 44 flexible plate valve, 45 valve seat, 59 rod, 61 balance spring, 64 diaphragm.
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭57−95281（ＪＰ，Ａ) 特開 昭58−128982（ＪＰ，Ａ) 特開 昭62−266242（ＪＰ，Ａ) 実開 平１−70698（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.6，ＤＢ名) F16F 9/00 - 9/58 B60G 17/08 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-57-95281 (JP, A) JP-A-58-128922 (JP, A) JP-A-62-266242 (JP, A) 70698 (JP, U) (58) Fields studied (Int. Cl. 6 , DB name) F16F 9/00-9/58 B60G 17/08
Claims (2)
方で作動油の流れる通路に板状の可撓弁をバルブシート
に向けて移動可能に設けると共に、この可撓弁を外部か
らの制御圧力に応じて移動させる調整手段を設け、可撓
弁がバルブシートと離間する移動範囲で可変絞り弁とし
て、バルブシートに接触する移動範囲で設定荷重の変化
する圧力制御弁として、さらに弁の可撓量が制限される
位置で閉止弁として機能するように構成したことを特徴
とする減衰力調整装置。1. A plate-shaped flexible valve is provided in a passage through which hydraulic oil flows at least on one of a compression side and an extension side of a damper so as to be movable toward a valve seat, and the flexible valve is controlled from outside. Adjusting means for moving in accordance with the pressure is provided, and as a variable throttle valve in a moving range in which the flexible valve is separated from the valve seat, as a pressure control valve in which a set load changes in a moving range in contact with the valve seat, and a valve is provided. A damping force adjusting device characterized in that it functions as a shut-off valve at a position where the amount of bending is limited.
置において、第１減衰弁と第２減衰弁を直列に、第１減
衰弁とリリーフ弁を並列に接続構成すると共に、第２減
衰弁としてダンパの圧側と伸側作動時の少なくとも一方
で作動油の流れる通路に板状の可撓弁をバルブシートに
向けて移動可能に設けると共に、この可撓弁を外部から
の制御圧力に応じて移動させる調整手段を設け、可撓弁
がバルブシートと離間する移動範囲で可変絞り弁とし
て、バルブシートに接触する移動範囲で設定荷重の変化
する圧力制御弁として、さらに弁の可撓量が制限される
位置で閉止弁として機能するように構成したことを特徴
とする減衰力調整装置。2. A damping force adjusting device installed outside a damper body, wherein a first damping valve and a second damping valve are connected in series, a first damping valve and a relief valve are connected in parallel, and a second damping valve is provided. A plate-shaped flexible valve is movably provided toward the valve seat in at least one of the pressure side and the extension side operation of the damper when the hydraulic oil flows, and the flexible valve is provided in response to an external control pressure. Providing an adjusting means for moving the valve, as a variable throttle valve in a moving range in which the flexible valve is separated from the valve seat, as a pressure control valve in which a set load changes in a moving range in contact with the valve seat, and further restricting the amount of valve flexibility. A damping force adjusting device configured to function as a closing valve at a position where the damping force is adjusted.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2202283A JP2986867B2 (en) | 1990-07-30 | 1990-07-30 | Damping force adjustment device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2202283A JP2986867B2 (en) | 1990-07-30 | 1990-07-30 | Damping force adjustment device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0488232A JPH0488232A (en) | 1992-03-23 |
| JP2986867B2 true JP2986867B2 (en) | 1999-12-06 |
Family
ID=16454974
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2202283A Expired - Fee Related JP2986867B2 (en) | 1990-07-30 | 1990-07-30 | Damping force adjustment device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2986867B2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6892865B2 (en) * | 2003-08-01 | 2005-05-17 | Arvin Technologies, Inc. | Monotube shock absorber remote reservoir fluid connection |
| JP2005110672A (en) * | 2003-09-19 | 2005-04-28 | Yanmar Agricult Equip Co Ltd | Threshing unit of general-purpose combine harvester |
| SE528985C2 (en) * | 2005-08-19 | 2007-04-03 | Oehlins Racing Ab | Method of applying partition plunger in space and device at such partition plunger |
| JP5357788B2 (en) * | 2009-01-19 | 2013-12-04 | カヤバ工業株式会社 | Front fork |
-
1990
- 1990-07-30 JP JP2202283A patent/JP2986867B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0488232A (en) | 1992-03-23 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |