JPH023063B2 - - Google Patents
Info
- Publication number
- JPH023063B2 JPH023063B2 JP9233682A JP9233682A JPH023063B2 JP H023063 B2 JPH023063 B2 JP H023063B2 JP 9233682 A JP9233682 A JP 9233682A JP 9233682 A JP9233682 A JP 9233682A JP H023063 B2 JPH023063 B2 JP H023063B2
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- valve
- piston
- oil
- chamber
- 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 26
- 230000005284 excitation Effects 0.000 claims description 8
- 239000006096 absorbing agent Substances 0.000 claims description 7
- 230000035939 shock Effects 0.000 claims description 7
- 238000011144 upstream manufacturing Methods 0.000 claims description 2
- 230000007423 decrease Effects 0.000 claims 1
- 239000003921 oil Substances 0.000 description 20
- 239000010720 hydraulic oil Substances 0.000 description 5
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000000696 magnetic material Substances 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 239000010727 cylinder oil Substances 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000000945 filler Substances 0.000 description 1
- WABPQHHGFIMREM-UHFFFAOYSA-N lead(0) Chemical compound [Pb] WABPQHHGFIMREM-UHFFFAOYSA-N 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000003313 weakening effect 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vehicle Body Suspensions (AREA)
- Fluid-Damping Devices (AREA)
Description
【発明の詳細な説明】
本発明は減衰力を運転条件に応じて自由に調整
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 according to operating conditions.
車両の油圧緩衝器に要求される減衰特性は、運
転条件に応じて多様に変化するのであるが、通常
の油圧緩衝器では予め設定された固定的な特性し
か附与できない。 The damping characteristics required of a vehicle's hydraulic shock absorber vary in a variety of ways depending on driving conditions, but ordinary hydraulic shock absorbers can only provide preset fixed characteristics.
そこで本出願人により、特願昭56−55213号と
して、減衰バルブの開弁圧を電磁ソレノイドの励
磁吸着力により増減させ、減衰特性を外部からの
電流値に応じて任意に変化させるようにした油圧
緩衝器が提案された。 Therefore, the present applicant proposed, in Japanese Patent Application No. 56-55213, that the opening pressure of the damping valve is increased or decreased by the excitation attraction force of an electromagnetic solenoid, and the damping characteristics are arbitrarily changed according to the external current value. A hydraulic shock absorber was proposed.
ところが、この場合、ピストン部に設けた減衰
バルブを電磁ソレノイドで制御している関係上、
ソレノイドコイルに対する配線をピストンロツド
を貫通して行う必要があり、またピストン部の構
造に大幅な改造が要求されることもあつて、実用
的には耐久性、組立性、コストアツプなど、改良
すべき問題が多かつた。 However, in this case, because the damping valve installed in the piston is controlled by an electromagnetic solenoid,
The wiring for the solenoid coil must pass through the piston rod, and the structure of the piston may require major modifications, so in practical terms there are problems that need to be improved, such as durability, ease of assembly, and increased cost. There were many.
本発明はかかる問題を解決するために提案され
たものである。 The present invention was proposed to solve this problem.
そこで本発明は、複筒型の油圧緩衝器におい
て、上部油室と下部油室とを連通するパイプを、
シリンダ外周の油溜室を縦貫して設け、シリンダ
底部に励磁電流に応じて開弁圧が比例的に変化す
る電磁減衰弁を設け、該減衰弁を伸側作動時にパ
イプを介して流れ出る作動油を通過させることに
より、発生減衰力を任意に調整するとともに、電
磁減衰弁のソレノイドに対する配線を簡略化し、
かつピストンやピストンロツドの改造を不要にし
ている。 Therefore, the present invention provides a pipe that communicates the upper oil chamber and the lower oil chamber in a dual-tube hydraulic shock absorber.
An oil reservoir chamber is provided vertically on the outer circumference of the cylinder, and an electromagnetic damping valve whose opening pressure changes proportionally according to the excitation current is provided at the bottom of the cylinder, and hydraulic oil flows out through a pipe when the damping valve is operated on the extension side. By passing the
Moreover, it eliminates the need to modify the piston or piston rod.
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.
外筒１の内部にはシリンダ２が同心的に配設さ
れ、シリンダ２の内部にはピストン３が摺動自由
に収装され、ピストン３の上下に油室６と７を区
画形成するとともに、シリンダ２と外筒１との間
に環状の油溜室８を形成する。 A cylinder 2 is arranged concentrically inside the outer cylinder 1, and a piston 3 is housed inside the cylinder 2 so as to be freely slidable, and oil chambers 6 and 7 are defined above and below the piston 3. An annular oil reservoir chamber 8 is formed between the cylinder 2 and the outer cylinder 1.
ピストン３のピストンロツド４は、シリンダ上
部の軸受部５を貫通して外部へ突出する。 The piston rod 4 of the piston 3 passes through a bearing 5 at the top of the cylinder and projects to the outside.
ピストン３には圧側作動時にのみ開いて上下の
油室６と７を連通するチエツク弁１９が介装され
る。 A check valve 19 is installed in the piston 3, which opens only when the piston is operated on the pressure side and communicates the upper and lower oil chambers 6 and 7.
一方、シリンダ２の下部にはベースバルブ１３
が設けられ、このベースバルブ１３は、シリンダ
２の内周に取付けたベースプレート２４に、伸側
作動時にのみ開くチエツク弁２１と、圧側作動時
にたわんで減衰力を発生する圧力減衰弁２２が取
付けられる。 On the other hand, the base valve 13 is located at the bottom of the cylinder 2.
The base valve 13 has a check valve 21 that opens only when operating on the rebound side, and a pressure damping valve 22 that bends and generates a damping force when operating on the compression side, attached to a base plate 24 attached to the inner circumference of the cylinder 2. .
このベースバルブ１３の下方には電磁減衰弁１
２が支持軸２３に取付けられた状態で、同軸的に
配設される。 Below this base valve 13 is an electromagnetic damping valve 1.
2 is attached to the support shaft 23 and arranged coaxially.
電磁減衰弁１２は支持軸２３に挿入固着したボ
ビン１５にコイル１４が巻回されるとともに、ボ
ビン１５の上面に磁性材料でつくられた弁口１７
をもつシート部１６が取り付けられ、このシート
部１６に同様に磁性材料でつくられたバルブプレ
ート１８が圧着する。 The electromagnetic damping valve 12 has a coil 14 wound around a bobbin 15 that is inserted and fixed onto a support shaft 23, and a valve port 17 made of a magnetic material on the top surface of the bobbin 15.
A seat portion 16 having a diameter is attached to the seat portion 16, and a valve plate 18, which is also made of a magnetic material, is crimped onto this seat portion 16.
バルブプレート１８は前記ベースプレート２４
とボビン１５との間で挾み付けられ、シート部１
６に密着保持される。 The valve plate 18 is connected to the base plate 24.
and the bobbin 15, and the seat part 1
6 is held in close contact.
これらベースバルブ１３と電磁減衰弁１２の間
の弁室２５は、シリンダ２に設けた通口２０を介
して油溜室８と連通している。 A valve chamber 25 between the base valve 13 and the electromagnetic damping valve 12 communicates with the oil reservoir chamber 8 via a port 20 provided in the cylinder 2 .
そして、上記上部油室６の上方において、シリ
ンダ２には通口１０が設けられ、同様に下部油室
６の電磁減衰弁１２の上流側に位置してシリンダ
２に通口１１が形成され、これら通口１０と１１
とは油溜室８の内部を縦貫するパイプ９を介して
連結されるのである。 A vent 10 is provided in the cylinder 2 above the upper oil chamber 6, and a vent 11 is similarly formed in the cylinder 2 located upstream of the electromagnetic damping valve 12 in the lower oil chamber 6. These ports 10 and 11
and are connected via a pipe 9 that runs vertically through the interior of the oil reservoir chamber 8.
上記電磁減衰弁１２のコイル１４のリード線２
７は、シリンダ２の底部キヤツプ２９に貫通した
通孔２６に挿通され、かつ充填材２７により油密
的に封止されている。 Lead wire 2 of the coil 14 of the electromagnetic damping valve 12
7 is inserted into a through hole 26 penetrating the bottom cap 29 of the cylinder 2, and is oil-tightly sealed with a filler 27.
以上のように構成され、次に作用を説明する
と、ピストンロツド４がシリンダ２の内部へ進入
する圧側作動時には、拡大すると上部油室６に下
部油室７からの作動油がチエツク弁１９を介して
流入するとともに、ピストンロツド４の侵入体積
分の作動油はベースバルブ１３の圧側減衰弁２２
を押し拡いて弁室２５から通口２０を経て油溜室
８へと流れ込む。 The structure is constructed as described above, and its operation will be explained next. During pressure side operation when the piston rod 4 enters the inside of the cylinder 2, the hydraulic oil from the lower oil chamber 7 enters the upper oil chamber 6 via the check valve 19 when expanded. At the same time, the hydraulic oil corresponding to the intrusion volume of the piston rod 4 flows into the pressure side damping valve 22 of the base valve 13.
The oil is expanded and flows from the valve chamber 25 through the passage 20 into the oil reservoir chamber 8.
なおこのとき上部油室６とパイプ９を介して連
通する電磁減衰弁１２は、閉弁保持されるため、
パイプ９を経由して作動油が流入することはな
い。 At this time, the electromagnetic damping valve 12, which communicates with the upper oil chamber 6 via the pipe 9, is kept closed.
No hydraulic oil flows in through the pipe 9.
したがつて圧側作動時の減衰力は、ベースバル
ブ１３によつてのみ発生する。 Therefore, the damping force during the compression side operation is generated only by the base valve 13.
これに対して、ピストンロツド４が抜け出す伸
側作動時には、上部油室６が縮少して下部油室７
が拡大する。 On the other hand, when the piston rod 4 comes out of the extension side, the upper oil chamber 6 contracts and the lower oil chamber 7
expands.
ピストン３に設けた圧側チエツク弁１９は閉弁
保持されるため、上部油室６の作動油はパイプ９
を介して電磁減衰弁１２に流れ込み、バルブプレ
ート１８をたわませながら弁口１７より弁室２５
へと流出するのであり、このときバルブプレート
１８のたわみ抵抗に応じた減衰力が発生する。 Since the pressure side check valve 19 provided on the piston 3 is kept closed, the hydraulic oil in the upper oil chamber 6 flows into the pipe 9.
flows into the electromagnetic damping valve 12 through the valve port 17 while bending the valve plate 18.
At this time, a damping force corresponding to the deflection resistance of the valve plate 18 is generated.
ところでこのバルブプレート１８はシート部１
６が磁化されると、これによる吸着力が閉弁方向
に働くため、減衰力は吸着力に比例して増大す
る。 By the way, this valve plate 18 is the seat part 1.
6 is magnetized, the resulting attraction force acts in the valve closing direction, so the damping force increases in proportion to the attraction force.
シート部１６はソレノイドコイル１４に対する
励磁電流に比例して磁化され、その吸着力を増加
するため、結局開弁特性はソレノイド励磁電流に
比例して変化するのである。 The seat portion 16 is magnetized in proportion to the excitation current applied to the solenoid coil 14, increasing its attractive force, so that the valve opening characteristic ultimately changes in proportion to the solenoid excitation current.
例えば、車両の高速走行時など励磁電流を増加
して減衰力を高めてやれば、高速運転時の操安性
が向上するし、低速の市街地走行時などに逆に励
磁力を弱めることにより、減衰力を小さくして乗
心地を改善できるのである。 For example, if the excitation current is increased to increase the damping force when the vehicle is running at high speeds, handling stability at high speeds will be improved, and conversely, by weakening the excitation force when driving at low speeds in the city, By reducing the damping force, ride comfort can be improved.
なお、これらの制御については、運転条件を検
出するセンサからの信号にもとづいてマイクロコ
ンピユータなどにより、最適に励磁電流をコント
ロールすればよい。 Regarding these controls, the excitation current may be optimally controlled by a microcomputer or the like based on a signal from a sensor that detects the operating conditions.
以上のように本発明によれば、運転条件に応じ
て伸側減衰力を自由に制御でき、操安性や乗心地
の改善がはかれる一方、電磁減衰弁はシリンダ下
部に固定されるため、ソレノイドコイルに対する
配線が容易となり、またピストンやピストンロツ
ドは既存のものをそのまま用いることができ、生
産性や組立性がよく、さらにコストダウンがはか
られるなど実用的価値がすこぶる高い。 As described above, according to the present invention, the rebound damping force can be freely controlled according to the operating conditions, improving steering stability and riding comfort. Wiring to the coil is easy, existing pistons and piston rods can be used as they are, productivity and assembly are good, and costs can be reduced, which is of great practical value.
図面は本発明の実施例を示す断面図である。
１……外筒、２……シリンダ、３……ピスト
ン、４……ピストンロツド、６，７，……油室、
８……油溜室、９……パイプ、１０，１１……通
口、１２……電磁減衰弁、１３……ベースバル
ブ、１４……ソレノイドコイル、１６……シート
部、１８……バルブプレート、２０……通口。
The drawings are cross-sectional views showing embodiments of the present invention. 1... Outer cylinder, 2... Cylinder, 3... Piston, 4... Piston rod, 6, 7,... Oil chamber,
8...Oil reservoir chamber, 9...Pipe, 10, 11...Port, 12...Solenoid damping valve, 13...Base valve, 14...Solenoid coil, 16...Seat portion, 18...Valve plate , 20...Douguchi.
Claims (1)
シリンダに対してピストンを摺動自由に収装し、
シリンダ内部のピストンの上下面に油室を、外筒
とシリンダの間に油溜室を画成した複筒型油圧緩
衝器において、上記ピストンに圧側でのみ開いて
上下の油室を連通するチエツク弁を設ける一方、
下部油室の底部に位置して励磁電流に応じて開弁
圧が比例的に増減する電磁減衰弁を設け、上部油
室と下部油室の電磁減衰弁上流との間を連通する
パイプを、油溜室を縦貫して配設したことを特徴
とする油圧緩衝器。1 The cylinder is fixed concentrically inside the outer cylinder,
The piston is slidably housed in the cylinder,
In a double-tube hydraulic shock absorber that has oil chambers on the upper and lower surfaces of the piston inside the cylinder and an oil reservoir chamber between the outer cylinder and the cylinder, there is a check that opens only on the pressure side of the piston to communicate the upper and lower oil chambers. While providing a valve,
An electromagnetic damping valve is provided at the bottom of the lower oil chamber and the opening pressure increases or decreases proportionally in accordance with the excitation current, and a pipe is connected between the upper oil chamber and the upstream side of the electromagnetic damping valve in the lower oil chamber. A hydraulic shock absorber characterized by having an oil reservoir chamber installed vertically.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9233682A JPS58211043A (en) | 1982-05-31 | 1982-05-31 | Hydraulic damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9233682A JPS58211043A (en) | 1982-05-31 | 1982-05-31 | Hydraulic damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58211043A JPS58211043A (en) | 1983-12-08 |
| JPH023063B2 true JPH023063B2 (en) | 1990-01-22 |
Family
ID=14051547
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9233682A Granted JPS58211043A (en) | 1982-05-31 | 1982-05-31 | Hydraulic damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58211043A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2530132Y2 (en) * | 1991-07-08 | 1997-03-26 | 利春 高橋 | One-touch mounting vent |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6959796B2 (en) * | 2003-09-22 | 2005-11-01 | Tenneco Automotive Operating Company Inc. | Adjustable damper with valve mounted in-line |
-
1982
- 1982-05-31 JP JP9233682A patent/JPS58211043A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2530132Y2 (en) * | 1991-07-08 | 1997-03-26 | 利春 高橋 | One-touch mounting vent |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58211043A (en) | 1983-12-08 |
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