JPS63270935A - Oil damper - Google Patents
Oil damperInfo
- Publication number
- JPS63270935A JPS63270935A JP10317287A JP10317287A JPS63270935A JP S63270935 A JPS63270935 A JP S63270935A JP 10317287 A JP10317287 A JP 10317287A JP 10317287 A JP10317287 A JP 10317287A JP S63270935 A JPS63270935 A JP S63270935A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- oil
- cylinder
- damping force
- wall surface
- 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.)
- Pending
Links
- 238000013016 damping Methods 0.000 abstract description 25
- 230000006835 compression Effects 0.000 abstract description 6
- 238000007906 compression Methods 0.000 abstract description 6
- 238000010586 diagram Methods 0.000 description 4
- 239000000725 suspension Substances 0.000 description 4
- 230000035939 shock Effects 0.000 description 3
- 239000006096 absorbing agent Substances 0.000 description 2
- 230000003139 buffering effect Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- 238000007789 sealing Methods 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
- F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
- F16F9/483—Arrangements for providing different damping effects at different parts of the stroke characterised by giving a particular shape to the cylinder, e.g. conical
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Description
【発明の詳細な説明】 （産業上の利用分野） 本考案はオイルダンパーに関するものである。[Detailed description of the invention] (Industrial application field) The present invention relates to an oil damper.
さらに詳しく言えば、一般車両又は玩具用のオイルダン
パ一式ショックアブソーバの改良に関するものである。More specifically, the present invention relates to an improvement of a shock absorber with an oil damper set for general vehicles or toys.
（従来技術）
従来のショックアブソーバとして使用されるオイルダン
パーには種々な構造のものがあるが、基本的にはシリン
ダ内にオイルが入りその中をピストンが往復運動する事
によって、シリンダ内のピストンの上部又は下部を高圧
にして減衰力を発生させるものであった。そして減衰力
はピストンの往復速度や油温によって変化するという不
具合があった。又これを車のサスペンションに取付けた
場合、そのダンパーの全ストロークで減衰力が略一定で
作動するということはこれ又芳ばしいことではなかった
。(Prior art) Oil dampers used as conventional shock absorbers have various structures, but basically, oil enters the cylinder and the piston reciprocates inside it, causing the piston inside the cylinder to The damping force was generated by applying high pressure to the upper or lower part of the cylinder. Another problem was that the damping force varied depending on the reciprocating speed of the piston and the oil temperature. Furthermore, when this damper is attached to a car suspension, the damping force remains approximately constant throughout the entire stroke of the damper, which is not a good thing.
本出願人は先に昭和６２年４月９日付で、模型玩具用ダ
ンパーと９題する考案について実用新案登録出願した。The applicant previously filed an application for utility model registration on April 9, 1986, for a nine-titled damper for model toys.
これについて第１０図と第１１図を参照して概略説明す
る。１はシリンダで一端に取付孔１ａを有している。２
はシリンダ１の他端の開口の閉塞体で、ピストン組立体
３の通る中心孔２ａ及びシール装置２ｂを有している。This will be briefly explained with reference to FIGS. 10 and 11. A cylinder 1 has a mounting hole 1a at one end. 2
is a closing body for the opening at the other end of the cylinder 1, and has a center hole 2a through which the piston assembly 3 passes and a sealing device 2b.
ピストン組立体３はピストン４と中空のピストンロッド
５と、ピストンロッド５と同心のロッド６を備えた油量
調整板７を有している。８はピストンヘッダーで該ヘッ
ダーにピストンロッド５の一端が固着されている。又ロ
ッド６の一端はこのヘッダー８の頂部に設けた凹孔に螺
入可能な取付金具９に結合されている。The piston assembly 3 has a piston 4, a hollow piston rod 5, and an oil amount adjusting plate 7 having a rod 6 concentric with the piston rod 5. 8 is a piston header to which one end of the piston rod 5 is fixed. Further, one end of the rod 6 is connected to a mounting fitting 9 which can be screwed into a recess provided at the top of the header 8.
ピストン４は皿状をなし、底板４ａの部分に油孔１０が
、又環状部４ｂの部分に軸方向の油溝１１が設けられて
いる。なお、ピストン４は油量調整板７に対し接離可能
で、ピストン４の底板４ａが調整板に密着した状態では
油孔１０を完全に閉じるような大きさである。The piston 4 is dish-shaped and has an oil hole 10 in the bottom plate 4a and an axial oil groove 11 in the annular portion 4b. The piston 4 can move toward and away from the oil amount adjustment plate 7, and has a size that completely closes the oil hole 10 when the bottom plate 4a of the piston 4 is in close contact with the adjustment plate.
１２はロッド６とピストンロッド５の間に設けた０リン
グで、これによりロッド６を伝っての漏油を防止する。Reference numeral 12 denotes an O-ring provided between the rod 6 and the piston rod 5, which prevents oil from leaking along the rod 6.
さて取付金具９とシリンダ１の取付孔１ａとを所定の取
付個所に取付ける。又ピストンヘッダー８をねじってピ
ストンロッド５を軸方向にずらしてピストン４と油量調
整板７との距離を調整する。Now, attach the mounting bracket 9 and the mounting hole 1a of the cylinder 1 to the predetermined mounting locations. Further, the distance between the piston 4 and the oil amount adjusting plate 7 is adjusted by twisting the piston header 8 and shifting the piston rod 5 in the axial direction.
第４図の上半分の如く両者間が空いているときは。When there is a gap between the two, as shown in the upper half of Figure 4.
ピストン４の底板４ａに設けた油孔１０は開放され、ピ
ストン４が矢印ａ方向に移動したときは、油室Ａ内の油
は油孔１０及び環状部４ｂに設けた油溝１１の両方から
油室Ｂに流入する。The oil hole 10 provided in the bottom plate 4a of the piston 4 is opened, and when the piston 4 moves in the direction of arrow a, the oil in the oil chamber A flows from both the oil hole 10 and the oil groove 11 provided in the annular portion 4b. It flows into oil chamber B.
又ピストンヘッダー８を逆にねじって調整板７をピスト
ン４の底板４ａに密着させると油の通路は環状部の油溝
１１のみとなる。If the piston header 8 is twisted in the opposite direction and the adjustment plate 7 is brought into close contact with the bottom plate 4a of the piston 4, the oil passage becomes only the oil groove 11 in the annular portion.
このときピストン４がａ方向に動くと、油圧は大となる
がロッド６とピストンロッド５との間に０リング１２が
あるので、ロッド６を伝っての漏油は完全に防がれる。At this time, when the piston 4 moves in the direction a, the oil pressure increases, but since there is an O-ring 12 between the rod 6 and the piston rod 5, oil leakage along the rod 6 is completely prevented.
上にのべたような本出願人による先考案によると、緩衝
性能の調整ができるが、この緩衝性能もピストンの速度
、ストロークに関係なく、油の粘性を変えないで油の通
過量を制御することのみで減衰性能を変えていた。According to the prior invention by the present applicant as mentioned above, the buffering performance can be adjusted, and this buffering performance also controls the amount of oil passing without changing the viscosity of the oil, regardless of the speed and stroke of the piston. This alone changed the damping performance.
（発明により解決しようとする問題点）路面の小さな不
整を走行する場合は減衰力が小さい方がダンパーの動き
が速く、又サスペンションの動きも速いので、路面に対
しての追従性が良くなり、安定して走らせる事ができる
。しかし大きなギャップを高速で走破する様な場合には
、大きな減衰力が必要になる。それを上述したような１
本のダンパーで機能させるにはピストンのストローク量
とスピードに関係し、シリンダとピストンのクリアラン
スが大きい場合はオイルの通過が速く、圧縮も上らない
ので減衰力も小さくなる。(Problem to be solved by the invention) When driving over small irregularities in the road surface, the smaller the damping force, the faster the damper moves, and the faster the suspension moves, so the ability to follow the road surface is better. It can run stably. However, when driving across large gaps at high speed, a large damping force is required. 1 as mentioned above
For a real damper to function properly, it is related to the stroke amount and speed of the piston; if the clearance between the cylinder and piston is large, the oil passes through quickly, and compression does not increase, so the damping force will be small.
又クリアランスが小さく、オイルの通過が遅い場合はピ
ストン上部の圧縮が上り、減衰力も大きくなる。そこで
本発明は基本的には減衰力を変化させるのであるが、ピ
ストンの動く量即ちシリンダー内のピストンのストロー
ク量に応じて減衰力を変化させることのできるような連
続自動可調整ダンパーを得ようとするものである。Also, if the clearance is small and the oil passes slowly, the compression at the top of the piston will increase and the damping force will also increase. Therefore, the present invention basically changes the damping force, but the aim is to provide a continuously automatically adjustable damper that can change the damping force according to the amount of movement of the piston, that is, the amount of stroke of the piston in the cylinder. That is.
（発明による解決手段）
シリンダの内壁面にその軸方向に移動するピストンの移
動量に応じて油通過量が変化する手段、例えばシリンダ
の軸心と平行に設けられかつ軸心方向の長さが異る溝を
一定ピッチで設けたものや。(Solving Means by the Invention) A means for changing the amount of oil passing according to the amount of movement of the piston that moves in the axial direction on the inner wall surface of the cylinder, for example, a means that is provided parallel to the axis of the cylinder and whose length in the axial direction is Something with different grooves at a constant pitch.
シリンダの軸心と平行に設けたテーパ溝あるいはテーバ
孔等を設けて、減衰力を漸次・変化可能とした。By providing a tapered groove or hole parallel to the axis of the cylinder, it is possible to gradually change the damping force.
（実施例）
第１図は本発明の詳細な説明する図である。１３はシリ
ンダ、１４はこの中を往復動するピストンである。シリ
ンダ１３の内壁面１５には先細のテーパーが付されてい
る。(Example) FIG. 1 is a diagram for explaining the present invention in detail. 13 is a cylinder, and 14 is a piston that reciprocates within the cylinder. The inner wall surface 15 of the cylinder 13 is tapered.
第１図において、ピストン１４がａ位置付近にある場合
は、ピストン１４と内壁面１５間のクリアランスδ、が
大きいので、油１６の通過速度が大で、圧縮比も上らな
いので減衰力も自ずと小となる。In Fig. 1, when the piston 14 is near position a, the clearance δ between the piston 14 and the inner wall surface 15 is large, so the passage speed of the oil 16 is high, and the compression ratio does not increase, so the damping force naturally decreases. becomes small.
これに対し第１図のｂ位置近傍になると、ピストン１４
と内壁面１５間のクリアランスδ２は非常に小となり、
同時に油の通過量が小さくなり。On the other hand, near position b in FIG. 1, the piston 14
The clearance δ2 between and the inner wall surface 15 becomes very small,
At the same time, the amount of oil passing through becomes smaller.
圧縮比が大となって減衰力を大きくすることができる。The compression ratio is increased and the damping force can be increased.
さて、本発明は以上の原理に基くもので、その第１実施
例を第２図〜第３図を参照して説明する。Now, the present invention is based on the above principle, and a first embodiment thereof will be described with reference to FIGS. 2 and 3.
第２図の場合はシリンダ１３の内壁面にシリンダの軸方
向長さｈの異る溝１７ａ〜１７ｅが一定のピッチで平行
に穿設されている。In the case of FIG. 2, grooves 17a to 17e having different lengths h in the axial direction of the cylinder are bored in parallel at a constant pitch on the inner wall surface of the cylinder 13.
この構成のシリンダ内でピストン１４が軸方向に移動す
ると、油１６の通過量が漸増し、減衰性能を変化させる
。When the piston 14 moves in the axial direction within the cylinder having this configuration, the amount of oil 16 passing therethrough gradually increases, changing the damping performance.
第４図〜第５図の場合は、シリンダ１３内に軸心と平行
であるが、その半径方向深さが直線的に変化するテーパ
溝１８を穿設しである。これによりピストン１４の移動
と共に油の通過量を漸増させることができる。In the case of FIGS. 4 and 5, a tapered groove 18 is bored in the cylinder 13, parallel to the axis, but whose radial depth varies linearly. As a result, the amount of oil passing through can be gradually increased as the piston 14 moves.
第６図の場合には、シリンダの内壁面１９をテーパ面と
したものである。この場合はこの内壁面内を往復動する
ピストン１４の直径は、内壁面の最小内径ｄ１よりやＮ
小としておくことは勿論である。この例でも同様にピス
トン１４の移動と共に、油の通過量を漸増させることが
できる。In the case of FIG. 6, the inner wall surface 19 of the cylinder is a tapered surface. In this case, the diameter of the piston 14 reciprocating within this inner wall surface is smaller than the minimum inner diameter d1 of the inner wall surface.
Of course, keep it small. In this example as well, the amount of oil passing through can be gradually increased as the piston 14 moves.
さて１以上のような構成のシリンダを備えたダンパーＤ
を例えば第７図の如く玩具用車両の本体２０とタイヤ２
１を支持するサスペンションアーム２２間に取付けて使
用する。Now, a damper D equipped with a cylinder configured as above 1
For example, as shown in FIG. 7, the main body 20 and tires 2 of a toy vehicle are
It is used by being attached between suspension arms 22 that support 1.
（作用）
シリンダ内壁面が第１図のような場合には、油の通過量
はピストンの左行と共に減少し、減衰力はこれに比例し
て大となる（第８図参照）。(Function) When the cylinder inner wall surface is as shown in FIG. 1, the amount of oil passing through decreases as the piston moves to the left, and the damping force increases in proportion to this (see FIG. 8).
これに反し従来のものはピストンのストロークと減衰力
の関係は直線的であるが、油孔の調整によって段階的に
変化する（第９図）。On the other hand, in the conventional type, the relationship between the stroke of the piston and the damping force is linear, but it changes stepwise by adjusting the oil hole (Figure 9).
（効果）
シリンダの内壁面にピストンの移動量に応じて油通過量
が変化する手段を講じたので、ピストンの移動量に応じ
て減衰力を変化させることができるようになった。(Effects) Since a means is provided on the inner wall surface of the cylinder to change the amount of oil passing according to the amount of movement of the piston, it is now possible to change the damping force according to the amount of movement of the piston.
この為、大きな減衰力を必要とするときはそれに応じて
大となり、これに反し、比較的小さな減衰力で良い場合
にも、具合よくこれに対処し得るようにしたので、特に
衝撃の激しい車両や玩具用車両等過酷な条件下で使用す
る車両用のダンパーとして好適である。For this reason, when a large damping force is required, the damping force increases accordingly, and on the other hand, even when a relatively small damping force is sufficient, it can be dealt with appropriately, so it can be used for vehicles subject to particularly severe shocks. It is suitable as a damper for vehicles used under harsh conditions, such as cars and toy vehicles.
第１図は本発明の原理図。
第２図は本発明の第１実施例。
第３図は第１図の展開図。
第４図は本発明の第２実施例。
第５図はテーパ溝の詳細図。
第６図は本発明の第３実施例。
第７図はダンパーの取付状態を示す。
第８図は本発明ダンパーのピストンスドロークー減衰力
線図。
第９図は先出願型のダンパーのピストンスドロークー減
衰力線図。
第１０図は先出願ダンパーの断面図。
第１１図は同じく要部拡大図。
図において；
１ シリンダ ｌａ 取付孔
２ （シリンダの）閉塞体
２ａ 中心孔 ２ｂ シール装置３ ピス
トン組立体 ４ ピストン
４ａ 底板 ４ｂ 環状部５ ピストン
組立体 ６ ロッド
７ 油量調整板 ８ ピストンヘッダー９ 取付
金具 ｌＯ油孔
１１ 油溝 １２０リング１３ シリン
ダ １４ ピストン１５ 内壁面
１６ 油
１７（１７ａ〜１７ｅ） 溝 １８ テーパ溝１
９ 内壁面 ２０ 本体２１ タイヤ
２２ サスペンションアーム
以上FIG. 1 is a diagram showing the principle of the present invention. FIG. 2 shows a first embodiment of the present invention. Figure 3 is a developed view of Figure 1. FIG. 4 shows a second embodiment of the present invention. FIG. 5 is a detailed view of the tapered groove. FIG. 6 shows a third embodiment of the present invention. FIG. 7 shows how the damper is installed. FIG. 8 is a piston stroke damping force diagram of the damper of the present invention. FIG. 9 is a piston stroke damping force diagram of the damper of the earlier application type. FIG. 10 is a sectional view of the damper of the earlier application. Figure 11 is also an enlarged view of the main parts. In the figure: 1 Cylinder la Mounting hole 2 Closure body 2a (of the cylinder) Center hole 2b Seal device 3 Piston assembly 4 Piston 4a Bottom plate 4b Annular part 5 Piston assembly 6 Rod 7 Oil amount adjustment plate 8 Piston header 9 Mounting bracket lO Oil hole 11 Oil groove 120 Ring 13 Cylinder 14 Piston 15 Inner wall surface
16 Oil 17 (17a to 17e) Groove 18 Taper groove 1
9 Inner wall surface 20 Main body 21 Tire 22 Above suspension arm
Claims (1)
の移動量に応じて油通過量を変化させる手段を設けたこ
とを特徴とするオイルダンパー。 ２）前記手段がシリンダの軸心と平行に設けられ、かつ
軸心方向の長さが異る溝を一定ピッチで設けたものであ
ることを特徴とする特許請求の範囲第１項載のオイルダ
ンパー。 ３）前記手段がシリンダの軸心と平行に設けたテーパー
溝であることを特徴とする特許請求の範囲第１項記載の
オイルダンパー。 ４）前記手段がテーパ孔であることを特徴とする特許請
求の範囲第１項記載のオイルダンパー。[Scope of Claims] 1) An oil damper characterized in that means is provided on the inner wall surface of the cylinder for changing the amount of oil passing according to the amount of movement of a piston that moves in the axial direction. 2) The oil according to claim 1, wherein the means is provided with grooves provided parallel to the axial center of the cylinder and having different lengths in the axial direction at a constant pitch. damper. 3) The oil damper according to claim 1, wherein the means is a tapered groove provided parallel to the axis of the cylinder. 4) The oil damper according to claim 1, wherein the means is a tapered hole.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10317287A JPS63270935A (en) | 1987-04-28 | 1987-04-28 | Oil damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10317287A JPS63270935A (en) | 1987-04-28 | 1987-04-28 | Oil damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63270935A true JPS63270935A (en) | 1988-11-08 |
Family
ID=14347086
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10317287A Pending JPS63270935A (en) | 1987-04-28 | 1987-04-28 | Oil damper |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS63270935A (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001030845A (en) * | 1999-06-08 | 2001-02-06 | Illinois Tool Works Inc <Itw> | Damping device with plastic strand |
| DE10324479A1 (en) * | 2003-05-30 | 2004-12-16 | Contitech Vibration Control Gmbh | Vibration damper has piston consisting of flexible ring mounted between lower support plate and upper clamping plate, adjusting screw moving clamping plate to adjust degree of compression of ring and its radial expansion |
| JP2006258147A (en) * | 2005-03-16 | 2006-09-28 | Daiwa House Ind Co Ltd | Viscous body damper |
| DE102010030542A1 (en) * | 2010-06-25 | 2011-12-29 | Thomas Ossadnik | Hydraulic shock absorber for decelerating moved mass in e.g. industrial machine, has piston displaceably arranged in work chamber, and opening formed as interstice between piston and inside wall of work chamber |
| DE202011101946U1 (en) | 2011-06-15 | 2012-11-23 | Thomas Ossadnik | shock absorber |
| KR101310686B1 (en) * | 2011-04-01 | 2013-09-25 | 에스엠시 가부시키가이샤 | Hydraulic shock absorber |
| DE102011104552A1 (en) | 2011-06-15 | 2014-05-08 | Thomas Ossadnik | Shock absorber for deceleration of moved-component e.g. propelled movable carriage, of e.g. handling machine, has hollow piston whose throttle opening is formed at exterior wall of stamper in work chamber |
| CN104100668A (en) * | 2013-04-12 | 2014-10-15 | 拓基轴承株式会社 | Speed control device |
| US10393211B2 (en) | 2017-02-08 | 2019-08-27 | Beijingwest Industries Co., Ltd. | Hydraulic damper with a hydraulic stop arrangement |
-
1987
- 1987-04-28 JP JP10317287A patent/JPS63270935A/en active Pending
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001030845A (en) * | 1999-06-08 | 2001-02-06 | Illinois Tool Works Inc <Itw> | Damping device with plastic strand |
| DE10324479A1 (en) * | 2003-05-30 | 2004-12-16 | Contitech Vibration Control Gmbh | Vibration damper has piston consisting of flexible ring mounted between lower support plate and upper clamping plate, adjusting screw moving clamping plate to adjust degree of compression of ring and its radial expansion |
| JP2006258147A (en) * | 2005-03-16 | 2006-09-28 | Daiwa House Ind Co Ltd | Viscous body damper |
| DE102010030542A1 (en) * | 2010-06-25 | 2011-12-29 | Thomas Ossadnik | Hydraulic shock absorber for decelerating moved mass in e.g. industrial machine, has piston displaceably arranged in work chamber, and opening formed as interstice between piston and inside wall of work chamber |
| DE102010030542B4 (en) * | 2010-06-25 | 2014-08-28 | Thomas Ossadnik | shock absorber |
| KR101310686B1 (en) * | 2011-04-01 | 2013-09-25 | 에스엠시 가부시키가이샤 | Hydraulic shock absorber |
| DE102012006147B4 (en) * | 2011-04-01 | 2015-10-15 | Smc Corp. | Hydraulic shock absorber |
| DE202011101946U1 (en) | 2011-06-15 | 2012-11-23 | Thomas Ossadnik | shock absorber |
| DE102011104552A1 (en) | 2011-06-15 | 2014-05-08 | Thomas Ossadnik | Shock absorber for deceleration of moved-component e.g. propelled movable carriage, of e.g. handling machine, has hollow piston whose throttle opening is formed at exterior wall of stamper in work chamber |
| CN104100668A (en) * | 2013-04-12 | 2014-10-15 | 拓基轴承株式会社 | Speed control device |
| JP2014206210A (en) * | 2013-04-12 | 2014-10-30 | トックベアリング株式会社 | Speed control device |
| US10393211B2 (en) | 2017-02-08 | 2019-08-27 | Beijingwest Industries Co., Ltd. | Hydraulic damper with a hydraulic stop arrangement |
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