JPH023056B2 - - Google Patents
Info
- Publication number
- JPH023056B2 JPH023056B2 JP18333581A JP18333581A JPH023056B2 JP H023056 B2 JPH023056 B2 JP H023056B2 JP 18333581 A JP18333581 A JP 18333581A JP 18333581 A JP18333581 A JP 18333581A JP H023056 B2 JPH023056 B2 JP H023056B2
- Authority
- JP
- Japan
- Prior art keywords
- damping
- valve
- piston
- valves
- variable orifice
- 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 74
- 230000006835 compression Effects 0.000 claims description 19
- 238000007906 compression Methods 0.000 claims description 19
- 239000006096 absorbing agent Substances 0.000 claims description 5
- 230000035939 shock Effects 0.000 claims description 5
- 230000000149 penetrating effect Effects 0.000 claims 1
- 239000003921 oil Substances 0.000 description 26
- 239000010720 hydraulic oil Substances 0.000 description 6
- 230000007935 neutral effect Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
- F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
- F16F9/466—Throttling control, i.e. regulation of flow passage geometry
- F16F9/467—Throttling control, i.e. regulation of flow passage geometry using rotary valves
- F16F9/468—Throttling control, i.e. regulation of flow passage geometry using rotary valves controlling at least one bypass to main flow path
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Description
【発明の詳細な説明】
本発明は、減衰力を自由に調整できるようにし
た油圧緩衝器に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic shock absorber whose damping force can be freely adjusted.
車両に要求される減衰特性は運転条件によつて
大巾に変動する。 The damping characteristics required for a vehicle vary widely depending on driving conditions.
例えば、実開昭54−117486号公報には、このよ
うな減衰特性を自由に調整できる機構が開示され
ているが、これを第１図によつて説明する。 For example, Japanese Utility Model Application Publication No. 54-117486 discloses a mechanism that can freely adjust such damping characteristics, which will be explained with reference to FIG.
シリンダ１の内部に摺動自由に収装したピスト
ン２により、その上下に油室Ａ，Ｂを区画し、さ
らにピストン２の下方に収めたフリーピストン３
が、ガス室Ｃを画成する。 A piston 2 is slidably housed inside the cylinder 1, and oil chambers A and B are defined above and below the piston 2, and a free piston 3 is housed below the piston 2.
defines a gas chamber C.
ピストン２には伸側、圧側減衰弁４，５が並設
され、ピストンロツド６が抜け出す伸側作動時に
は伸側減衰弁４を通して縮小する油室Ａから拡大
する油室Ｂへ流れる作動油に抵抗を与え、逆にピ
ストンロツド６が侵入する圧側作動時には圧側減
衰弁５により油室ＢからＡに流れる作動油に抵抗
を与えて、それぞれ減衰力を発生させる。 The piston 2 is provided with expansion side and compression side damping valves 4 and 5 in parallel, and when the piston rod 6 is pulled out during the expansion side operation, the piston 2 resists the hydraulic oil flowing from the contracting oil chamber A to the expanding oil chamber B through the expansion side damping valve 4. On the other hand, during pressure side operation when the piston rod 6 enters, the pressure side damping valve 5 provides resistance to the hydraulic oil flowing from the oil chamber B to the oil chamber A, thereby generating a damping force.
フリーピストン３で仕切られたガス室Ｃは、圧
側でのピストンロツド６の侵入体積分の油の出入
りを補償する。 The gas chamber C delimited by the free piston 3 compensates for the inflow and outflow of oil corresponding to the volume of entry of the piston rod 6 on the pressure side.
そしてピストンロツド６には、これを貫通する
操作ロツド７の先端に、小孔９のあいたロータリ
バルブ８が設けられ、油室ＡからＢへピストン部
をバイパスする通路１０の通孔１１と、この小孔
９とにより油室ＡとＢを連絡する可変オリフイス
を形成している。 The piston rod 6 is provided with a rotary valve 8 having a small hole 9 at the tip of an operating rod 7 passing through it, and a through hole 11 of a passage 10 bypassing the piston section from oil chamber A to B. The hole 9 forms a variable orifice that communicates the oil chambers A and B.
操作ロツド７の突出端に設けたロータリソレノ
イド１３の駆動によりロツド７が回転してロータ
リバルブ８が通孔１１を閉じその逆転により通孔
１１が開く。 A rotary solenoid 13 provided at the protruding end of the operating rod 7 is driven to rotate the rod 7, causing the rotary valve 8 to close the through hole 11 and open the through hole 11 by reversing the rotary valve 8.
したがつて、市街地走行時などソフトな減衰特
性を望むときは、ロータリバルブ８を開いてやる
と、伸側、圧側減衰弁４，５に加えてオリフイス
をもつ通路１０により油室Ａ，Ｂが連通するの
で、作動油の流通抵抗が減り減衰力が低下する。 Therefore, when a soft damping characteristic is desired, such as when driving in a city, by opening the rotary valve 8, the oil chambers A and B are opened by the passage 10 having an orifice in addition to the expansion side and compression side damping valves 4 and 5. Since they are in communication, the flow resistance of hydraulic oil is reduced and the damping force is reduced.
これに対して車両高速域での操安性を確保する
ためにハードな減衰特性を得たいときは、ロータ
リバルブ８を閉じれば、伸側、圧側減衰弁４，５
のみによる相対的に高い減衰力が発生する。 On the other hand, if you want to obtain hard damping characteristics to ensure maneuverability in high-speed vehicle ranges, by closing the rotary valve 8, you can close the rebound and compression damping valves 4 and 5.
A relatively high damping force is generated only by
このようにして減衰力の切り換えが行えるので
あるが、第２図にも示すように、ロータリバルブ
８のオリフイスを開閉するだけでは、オリフイス
流量が大きな割合を占めるピストン低速域での減
衰特性は大きく変化させられても、オリフイスの
効きが一定となる中高速域では、減衰特性はほと
んど伸側、圧側減衰弁４，５にのみ存在し、それ
ほど大きな変化が得られないという欠点があつ
た。 The damping force can be switched in this way, but as shown in Figure 2, simply opening and closing the orifice of the rotary valve 8 will greatly affect the damping characteristics in the low piston speed range where the orifice flow rate is large. Even if the orifice is changed, in the medium and high speed range where the effectiveness of the orifice is constant, the damping characteristics exist almost only in the expansion side and compression side damping valves 4 and 5, and there is a drawback that a large change cannot be obtained.
本発明の目的は、ピストン低速域から高速域ま
で減衰特性を大巾に調整できるようにした油圧緩
衝器を提供することである。 An object of the present invention is to provide a hydraulic shock absorber whose damping characteristics can be adjusted over a wide range from a low piston speed range to a high speed range.
本発明は第１の伸側、圧側減衰弁と並列に可変
オリフイスを設け、さらにこれらと並列に第２の
伸側、圧側減衰弁を設け、第２の減衰弁の油路を
切換バルブによつて選択的に開閉するもので、切
換バルブと可変オリフイスを開いているときは第
１、第２の減衰弁及びこれと並列の可変オリフイ
スによる比較的低い減衰特性、そして可変オリフ
イスを閉じたときは第１、第２の減衰弁の並列回
路による比較的高い減衰特性、さらに切換バルブ
を閉じたときは第１の減衰弁のみによる高い減衰
特性がそれぞれ得られるようにしてある。 The present invention provides a variable orifice in parallel with the first expansion side and compression side damping valves, further provides a second expansion side and compression side damping valve in parallel with these, and connects the oil passage of the second damping valve with a switching valve. When the switching valve and variable orifice are open, the first and second damping valves and the variable orifice in parallel have relatively low damping characteristics, and when the variable orifice is closed, the damping characteristics are relatively low. Relatively high damping characteristics are obtained by the parallel circuit of the first and second damping valves, and when the switching valve is closed, high damping characteristics are obtained only by the first damping valve.
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３図において、ピストン２には第１の伸側、
圧側減衰弁４，５が並設される。 In FIG. 3, the piston 2 has a first extension side,
Compression side damping valves 4 and 5 are arranged in parallel.
ただし、この実施例では、伸側、圧側減衰弁
４，５は共に撓み型のリーフ弁４Ａ，５Ａであつ
て、それぞれポート４Ｂと５Ｂを開閉する。な
お、外側のポート５Ｂのシート部は、ポート開口
の周囲に環状に盛り上げられ、したがつて、内側
のポート４Ｂはリーフ弁５Ａがあつても油室Ａと
連通状態になつている。 However, in this embodiment, the expansion side and compression side damping valves 4 and 5 are both flexible leaf valves 4A and 5A, and open and close ports 4B and 5B, respectively. Note that the seat portion of the outer port 5B is raised in an annular shape around the port opening, so that the inner port 4B is in communication with the oil chamber A even when the leaf valve 5A is present.
そして、ピストン２に嵌められるピストンナツ
ト１５の内部には、可変オリフイス１３と切換バ
ルブ１６及び第２の伸側、圧側減衰弁１７，１８
が配設される。 Inside the piston nut 15 fitted into the piston 2, there are a variable orifice 13, a switching valve 16, and second expansion and compression damping valves 17, 18.
will be placed.
切換バルブ１６はピストン１の上部の油室Ａと
第２の減衰弁１７，１８との間の油路１９を開閉
するもので、ピストンロツド６を貫通する操作ロ
ツド７に取り付けられている。 The switching valve 16 opens and closes the oil passage 19 between the oil chamber A in the upper part of the piston 1 and the second damping valves 17 and 18, and is attached to the operating rod 7 passing through the piston rod 6.
可変オリフイス１３は油路１９と油室Ｂとを連
通している。 The variable orifice 13 communicates the oil passage 19 with the oil chamber B.
切換バルブ１６のポート２０と可変オリフイス
１３の通口１４は、ピストンナツト１５の筒部２
２の対向位置に設けられ、筒部２２の内周に切換
バルブ１６の弁部２３が摺接する。 The port 20 of the switching valve 16 and the port 14 of the variable orifice 13 are connected to the cylindrical portion 2 of the piston nut 15.
2, and the valve portion 23 of the switching valve 16 is in sliding contact with the inner periphery of the cylindrical portion 22.
切換バルブ１６は本実施例では、筒体の側壁に
形成した弁部２３にポート２０と連通する弁口２
４と、通口１４と連通する弁口２５とを有し、操
作ロツド７の回転に伴い弁部２３が回動してポー
ト２０と通口１４を開閉するようになつている。 In this embodiment, the switching valve 16 has a valve port 2 that communicates with the port 20 in a valve portion 23 formed on the side wall of the cylinder.
4 and a valve port 25 communicating with the port 14, and as the operating rod 7 rotates, the valve portion 23 rotates to open and close the port 20 and the port 14.
可変オリフイス１３と切換バルブ１６との開閉
関係は、操作ロツド７の中立時は両方が開き、右
回転時は可変オリフイス１３が閉じて切換バルブ
１６が開き、左回転時には両方が閉じるように設
定されている。 The opening/closing relationship between the variable orifice 13 and the switching valve 16 is set so that when the operating rod 7 is in the neutral position, both are open, when rotating to the right, the variable orifice 13 closes and the switching valve 16 opens, and when rotating to the left, both are closed. ing.
ポート２０は上記第２の伸側、圧側減衰弁１
７，１８を収装したガイド板２６の環状溝２７と
接続し、さらに通孔２８を介して弁室２９と連通
する。 The port 20 is connected to the second expansion side and compression side damping valve 1.
It is connected to an annular groove 27 of a guide plate 26 in which valves 7 and 18 are housed, and further communicates with a valve chamber 29 via a through hole 28.
第２の伸側、圧側減衰弁１７，１８は第１の減
衰弁４，５と同様に、ポート１７Ｂ，１８Ｂを開
閉するリーフ弁１７Ａ，１８Ａとから構成され、
かつそれぞれの減衰弁１７，１８のポート１７Ｂ
と１８Ｂの流入口は、リーフ弁１８Ａと１７Ａに
よつて互いに油の流入を妨げられないように形成
される。 The second expansion-side and compression-side damping valves 17 and 18, like the first damping valves 4 and 5, are composed of leaf valves 17A and 18A that open and close ports 17B and 18B,
and port 17B of each damping valve 17, 18
and 18B are formed so that the oil inflow into each other is not obstructed by the leaf valves 18A and 17A.
次に作用について説明する。 Next, the effect will be explained.
操作ロツド７の中立位置においては、可変オリ
フイス１３が開くとともに切換バルブ１６がポー
ト２０を開く。 In the neutral position of the operating rod 7, the variable orifice 13 is open and the switching valve 16 opens the port 20.
このため、例えば圧側作動時には油室Ｂの作動
油は、第２の圧側減衰弁１８を押し拡いてポート
２０から油路１９を経て油室Ａへ、またこれとは
別に第１の圧側減衰弁５を押し拡いて同様に油室
Ａへと流れ、さらに一部は可変オリフイス１３を
通り同じく油室Ａへ流れ、同様に伸側作動時には
油室Ａの作動油は第１並びに第２の伸側減衰弁
４，１７と可変オリフイス１３を経由して油室Ｂ
へと流出する。 Therefore, for example, during pressure side operation, the hydraulic oil in the oil chamber B expands the second pressure side damping valve 18 and flows from the port 20 through the oil passage 19 to the oil chamber A, and separately from the first pressure side damping valve 18. 5 is expanded and similarly flows to the oil chamber A, and a part of it also flows to the oil chamber A through the variable orifice 13. Similarly, during the expansion side operation, the hydraulic oil in the oil chamber A flows into the first and second expansion side. Oil chamber B via side damping valves 4, 17 and variable orifice 13
flows out to.
したがつて、第１、第２の伸側、圧側減衰弁
４，５及び１７，１８と可変オリフイスとから大
流量が流れ、比較的ソフト（通常）な減衰特性が
得られる（第４図）。 Therefore, a large amount of flow flows from the first and second expansion side and compression side damping valves 4, 5 and 17, 18, and the variable orifice, and relatively soft (normal) damping characteristics are obtained (Fig. 4). .
次に作動ロツド７を右回転して切換バルブ１６
は開いたままで可変オリフイス１３を閉じると、
こんどは第１と第２の減衰弁４，５並びに１７，
１８を通して作動油が流れるようになる。 Next, rotate the operating rod 7 clockwise to remove the switching valve 16.
When the variable orifice 13 is closed while remaining open,
Next, the first and second damping valves 4, 5 and 17,
Hydraulic oil begins to flow through 18.
したがつて、上述の中立時に比べて可変オリフ
イス１３の流量分がそつくり第１と第２の伸側、
圧側減衰弁４，５並びに１７，１８へ流れるた
め、その分だけ減衰弁は相対的に増加する。 Therefore, compared to the above-mentioned neutral state, the flow rate of the variable orifice 13 is warped, and the first and second extension sides,
Since it flows to the compression side damping valves 4, 5 and 17, 18, the number of damping valves increases by that amount.
例えば高速走行時など操安性が重要視される運
転状態で、とくにピストン低速域での減衰力を高
めてやや硬めの減衰特性を得るのである（第４図
）。 For example, in driving conditions where handling stability is important, such as when driving at high speeds, the damping force is increased especially in the low piston speed range to obtain a slightly stiffer damping characteristic (Figure 4).
一方、操作ロツド７の左回転により可変オリフ
イス１３とともに切換バルブ１６を閉じると、第
２の減衰弁１７，１８と油室Ａの間の油路１９の
連通が遮断される。 On the other hand, when the operating rod 7 is rotated counterclockwise to close the switching valve 16 together with the variable orifice 13, communication of the oil passage 19 between the second damping valves 17, 18 and the oil chamber A is cut off.
その結果、全ての作動油は第１の伸側、圧側減
衰弁４，５のみを流れるのであり、このようにし
て第１の減衰弁４，５の流量が大幅に増えると大
きな抵抗を受け、高い減衰力を発生し、例えば悪
路行時など緩衝器の底突きや伸切りを防止する
（第４図）。 As a result, all the hydraulic fluid flows only through the first expansion and compression side damping valves 4 and 5, and when the flow rate of the first damping valves 4 and 5 increases significantly in this way, it encounters a large resistance. It generates a high damping force and prevents the shock absorber from bottoming out or stretching out, for example when driving on rough roads (Figure 4).
これらの減衰特性関係を示したのが第４図であ
り、第１、第２の減衰弁を４，５と１７，１８及
び可変オリフイス１３の有効径を変えることによ
り、ピストン低速域から高速域まで減衰力の調整
巾は非常に大きくとることができる。 Figure 4 shows these damping characteristic relationships, and by changing the first and second damping valves 4, 5 and 17, 18 and the effective diameter of the variable orifice 13, the piston can be adjusted from a low speed range to a high speed range. The damping force can be adjusted over a very wide range.
第５図は本発明の他の実施例を示すものである
が、第３図と異なるのは、第１の圧側減衰弁５を
ノンリターンバルブとした点で、環状弁３０をコ
ーンスプリング３１で閉弁方向に付勢するように
構成している。 FIG. 5 shows another embodiment of the present invention, which differs from FIG. 3 in that the first pressure side damping valve 5 is a non-return valve, and the annular valve 30 is replaced by a cone spring 31. The valve is configured to be biased in the valve closing direction.
したがつて、この場合には第１の圧側減衰弁５
が開きやすいため、圧側減衰力が伸側に比べて低
くなる特性をもつ。 Therefore, in this case, the first pressure side damping valve 5
Because it opens easily, the damping force on the compression side is lower than that on the rebound side.
以上のように本発明は、第１、第２の減衰弁と
可変オリフイスとの並列回路によるソフトな減衰
特性と、第１、第２の減衰弁によるややハードな
減衰特性と、第１の減衰弁のみによる非常にハー
ドな減衰特性とが自由に選択でき、ピストン低速
域から高速域まで減衰力の張整巾を車両の使用条
件に応じて大きく変化させられ、車両の乗り心地
と操安性の両条件を共に満足させうるという効果
がある。 As described above, the present invention provides a soft damping characteristic by the parallel circuit of the first and second damping valves and the variable orifice, a slightly hard damping characteristic by the first and second damping valves, and a first damping characteristic. You can freely select extremely hard damping characteristics using only the valve, and the damping force range can be changed greatly depending on the vehicle usage conditions from low piston speed range to high speed range, improving vehicle ride comfort and handling. This has the effect of satisfying both conditions.
第１図は従来装置の断面図、第２図はその減衰
特性図である。第３図は本発明の実施例を示す要
部断面図、第４図は本発明の減衰特性図、第５図
は他の実施例の要部断面図である。
１……シリンダ、２……ピストン、４……第１
の伸側減衰弁、５……第１の圧側減衰弁、６……
ピストンロツド、７……操作ロツド、８……ロー
タリバルブ、１３……可変オリフイス、１５……
ピストンナツト、１６……切換バルブ、１７……
第２の伸側減衰弁、１８……第２の圧側減衰弁、
１９……油路。
FIG. 1 is a sectional view of a conventional device, and FIG. 2 is a diagram showing its damping characteristics. FIG. 3 is a sectional view of a main part showing an embodiment of the present invention, FIG. 4 is a diagram of attenuation characteristics of the present invention, and FIG. 5 is a sectional view of a main part of another embodiment. 1...Cylinder, 2...Piston, 4...First
Rebound side damping valve, 5... First compression side damping valve, 6...
Piston rod, 7... Operating rod, 8... Rotary valve, 13... Variable orifice, 15...
Piston nut, 16...Switching valve, 17...
Second rebound damping valve, 18... second compression damping valve,
19...Oil road.
Claims (1)
ンを収装して上下油室を形成し、ピストンに第１
の伸側、圧側減衰弁を並列的に配設するととも
に、上下油室を短絡する可変オリフイスを設け、
さらにピストンに上記第１の伸側、圧側減衰弁と
並列に第２の伸側、圧側減衰弁を配設し、第２の
減衰弁の油路を選択的に開閉する切換バルブを設
けたことを特徴とする減衰力調整式油圧緩衝器。 ２ 切換バルブは可変オリフイスと連動して、ピ
ストンロツドを貫通する操作ロツドを介して外部
から回転駆動されるようになつている特許請求の
範囲第１項に記載の減衰力調整式油圧緩衝器。[Claims] 1. A piston connected to a piston rod is housed in a cylinder to form upper and lower oil chambers, and a first oil chamber is provided in the piston.
The expansion side and compression side damping valves are arranged in parallel, and a variable orifice is installed to short-circuit the upper and lower oil chambers.
Further, a second expansion side, compression side damping valve is arranged in parallel with the first expansion side, compression side damping valve on the piston, and a switching valve is provided for selectively opening and closing the oil passage of the second damping valve. A hydraulic shock absorber with adjustable damping force. 2. The damping force adjustable hydraulic shock absorber according to claim 1, wherein the switching valve is rotatably driven from the outside via an operating rod penetrating the piston rod in conjunction with the variable orifice.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18333581A JPS5884241A (en) | 1981-11-16 | 1981-11-16 | Hydraulic buffer of damping force adjustment type |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP18333581A JPS5884241A (en) | 1981-11-16 | 1981-11-16 | Hydraulic buffer of damping force adjustment type |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5884241A JPS5884241A (en) | 1983-05-20 |
| JPH023056B2 true JPH023056B2 (en) | 1990-01-22 |
Family
ID=16133916
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP18333581A Granted JPS5884241A (en) | 1981-11-16 | 1981-11-16 | Hydraulic buffer of damping force adjustment type |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5884241A (en) |
Families Citing this family (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5911932U (en) * | 1982-07-14 | 1984-01-25 | トキコ株式会社 | Variable damping force hydraulic shock absorber |
| DE3446133A1 (en) * | 1984-12-18 | 1986-06-19 | Fichtel & Sachs Ag, 8720 Schweinfurt | VIBRATION DAMPER WITH VARIABLE DAMPING FORCE |
| JPS61126126U (en) * | 1985-01-29 | 1986-08-08 | ||
| JPH043140Y2 (en) * | 1985-03-22 | 1992-01-31 | ||
| JPS61168339U (en) * | 1985-04-08 | 1986-10-18 | ||
| JPS61172232U (en) * | 1985-04-15 | 1986-10-25 | ||
| JPH0324911Y2 (en) * | 1985-08-16 | 1991-05-30 | ||
| DE3542846A1 (en) * | 1985-12-04 | 1987-06-11 | Fichtel & Sachs Ag | Actuating device for a vibration damper with adjustable damping force |
| JPH0439480Y2 (en) * | 1986-04-01 | 1992-09-16 | ||
| JPS62162429U (en) * | 1986-04-03 | 1987-10-15 | ||
| JPH0518509Y2 (en) * | 1986-10-06 | 1993-05-17 | ||
| JPH0519626Y2 (en) * | 1986-10-06 | 1993-05-24 | ||
| JPS6399046U (en) * | 1986-12-18 | 1988-06-27 | ||
| JPH0160043U (en) * | 1987-10-13 | 1989-04-17 | ||
| GB2220726B (en) * | 1988-06-07 | 1992-07-08 | Tokico Ltd | A hydraulic damper of adjustable damping force type |
| JPH0579526A (en) * | 1991-09-20 | 1993-03-30 | Tokico Ltd | Damping force adjusting type hydraulic buffer |
-
1981
- 1981-11-16 JP JP18333581A patent/JPS5884241A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5884241A (en) | 1983-05-20 |
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