JPH0516424Y2 - - Google Patents
Info
- Publication number
- JPH0516424Y2 JPH0516424Y2 JP1987068600U JP6860087U JPH0516424Y2 JP H0516424 Y2 JPH0516424 Y2 JP H0516424Y2 JP 1987068600 U JP1987068600 U JP 1987068600U JP 6860087 U JP6860087 U JP 6860087U JP H0516424 Y2 JPH0516424 Y2 JP H0516424Y2
- Authority
- JP
- Japan
- Prior art keywords
- stopper
- adjuster
- cylinder
- spring
- outer periphery
- 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 - Lifetime
Links
- 230000035939 shock Effects 0.000 claims description 9
- 239000006096 absorbing agent Substances 0.000 claims description 8
- 238000003825 pressing Methods 0.000 claims description 4
- 239000000725 suspension Substances 0.000 description 13
- 230000002093 peripheral effect Effects 0.000 description 5
- 239000003921 oil Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000009826 distribution Methods 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Landscapes
- Fluid-Damping Devices (AREA)
- Axle Suspensions And Sidecars For Cycles (AREA)
- Springs (AREA)
Description
【考案の詳細な説明】
(産業上の利用分野)
本考案は緩衝器のシリンダ外周に設けたバネ受
けをシリンダの軸方向に移動させることで懸架バ
ネの荷重を調整するバネ荷重調整機構に関する。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a spring load adjustment mechanism that adjusts the load of a suspension spring by moving a spring receiver provided on the outer periphery of a cylinder of a shock absorber in the axial direction of the cylinder.
(従来の技術)
例えば自動二輪車のリアクシヨン等に用いられ
る油圧緩衝器において、車高調整のため、あるい
は路面状況に応じた適正な緩衝作用を得るために
懸架バネの荷重調整を行なうバネ荷重調整機構が
知られている。(Prior art) For example, in a hydraulic shock absorber used for the reaction of a motorcycle, etc., a spring load adjustment mechanism adjusts the load of a suspension spring in order to adjust the vehicle height or to obtain an appropriate shock absorbing effect according to road surface conditions. It has been known.
従来のバネ荷重調整機構は、第6図に示すよう
に、シリンダ51の外周に図示しない懸架バネを
受けるバネ受けを兼ねた調整カム筒52を回動自
在に嵌装し、この調整カム筒52に下端面には段
階的なカム面53を形成し、シリンダ51の外周
にこの段階的カム面53に係合するストツパピン
54を固着して、調整カム筒52を回動させて段
階的カム面53をストツパピン54に選択的に係
止させることにより、調整カム筒52をシリンダ
51の軸方向に移動して懸架バネの荷重を調整す
るようにしている。 In the conventional spring load adjustment mechanism, as shown in FIG. 6, an adjustment cam cylinder 52 which also serves as a spring receiver for receiving a suspension spring (not shown) is rotatably fitted on the outer periphery of a cylinder 51. A stepwise cam surface 53 is formed on the lower end surface of the cylinder 51, and a stopper pin 54 that engages with the stepwise cam surface 53 is fixed to the outer periphery of the cylinder 51, and the adjusting cam cylinder 52 is rotated to form a stepwise cam surface. 53 is selectively engaged with the stopper pin 54, the adjustment cam cylinder 52 is moved in the axial direction of the cylinder 51 to adjust the load of the suspension spring.
(考案が解決しようとする問題点)
上述したバネ荷重調整機構においては、シリン
ダ51の外周に固定したストツパピン54で懸架
バネの全反力をうけるため、荷重調整に際しては
この強い反力に抗して調整カム筒52を移動、回
転せしめる必要があり、しかもストツパピンと係
合するカム面53は段階的であるので、懸架バネ
のセツト荷重が高いときには回転トルクが高くな
つて調整カム筒を回すために多大の労力を要し、
操作性が悪い。(Problem to be solved by the invention) In the spring load adjustment mechanism described above, the stopper pin 54 fixed to the outer periphery of the cylinder 51 receives the full reaction force of the suspension spring, so when adjusting the load, it is necessary to resist this strong reaction force. It is necessary to move and rotate the adjusting cam cylinder 52, and since the cam surface 53 that engages with the stopper pin is stepped, when the set load of the suspension spring is high, the rotational torque becomes high to turn the adjusting cam cylinder. It takes a lot of effort to
Poor operability.
また、調整カム筒52に段階的カム面53を形
成するための加工が面倒であり、更に段階的カム
面53の各々のカム面はストツパピン54が確実
に係合できなければならないためにカム数が少な
く、バネ荷重を細かに調整することができない。 Further, the processing for forming the stepped cam surfaces 53 on the adjustment cam cylinder 52 is troublesome, and each cam surface of the stepped cam surfaces 53 must be able to engage with the stopper pin 54 reliably, so the number of cams is required. is small, making it impossible to finely adjust the spring load.
(問題点を解決するための手段)
上記問題点を解決すべく本考案は、環状のスト
ツパの各テーパ面の勾配を一様とし、このテーパ
面と当接するテーパ面を環状のアジヤスタにそれ
ぞれ形成するとともに、このアジヤスタにはスト
ツパの外周に面する円筒状の回動リングを固着
し、この回動リングの分周位置にストツパの軸方
向の移動長さをなす複数の長孔を貫通し、この長
孔に選択的に係合してアジヤスタの回動を規制す
るとともに、係合している長孔の外方からの押圧
力によつて係合が解除されるストツパピンを前記
ストツパに進退自在に設けた。(Means for Solving the Problems) In order to solve the above problems, the present invention makes the slope of each tapered surface of the annular stopper uniform, and forms the tapered surfaces that come into contact with each of the tapered surfaces on the annular adjuster. At the same time, a cylindrical rotating ring facing the outer periphery of the stopper is fixed to this adjuster, and a plurality of elongated holes forming the axial movement length of the stopper are penetrated at the dividing positions of the rotating ring. A stopper pin that selectively engages with this elongated hole to restrict the rotation of the adjuster and is released from the engagement by a pressing force from the outside of the engaged elongated hole can be moved forward and backward into the stopper. It was established in
(作用)
進退可能なストツパピンを押圧後退させつつ回
動リングを回動させれば、各テーパ面の一様な勾
配と面接触による当接面の荷重の分散とによつて
アジヤスタは小さな力で滑らかに回動され、スト
ツパ位置はシリンダの軸方向に移動されてバネ荷
重が調整され、また、ストツパ側のストツパピン
がアジヤスタ側の回動リングの長孔に係合するこ
とによつてアジヤスタの回動が規制され、当接し
ているテーパ面がストツパとして作用するので一
定のバネ荷重が維持される。(Function) If the rotary ring is rotated while pressing and retracting the movable stopper pin, the adjuster can be moved with a small force due to the uniform slope of each tapered surface and the distribution of the load on the contact surface due to surface contact. The stopper position is moved in the axial direction of the cylinder to adjust the spring load, and the adjuster is rotated by engaging the stopper pin on the stopper side with the long hole in the rotating ring on the adjuster side. The movement is restricted, and the abutting tapered surface acts as a stopper, so a constant spring load is maintained.
(実施例)
以下に本考案の実施例を添付図面に基づいて説
明する。(Example) An example of the present invention will be described below based on the accompanying drawings.
第1図は本考案にかかるバネ荷重調整機構を備
えた油圧緩衝器の半断面図、第2図は第1図のバ
ネ荷重調整機構の要部拡大断面図、第3図は第2
図のバネ荷重調整機構の平断面図、第4図はバネ
荷重調整機構の要部展開図、第5図はバネ荷重調
整機構による荷重調整の説明に供する平断面図で
ある。 Fig. 1 is a half-sectional view of a hydraulic shock absorber equipped with a spring load adjustment mechanism according to the present invention, Fig. 2 is an enlarged sectional view of main parts of the spring load adjustment mechanism of Fig.
FIG. 4 is a developed view of essential parts of the spring load adjustment mechanism, and FIG. 5 is a plane sectional view for explaining load adjustment by the spring load adjustment mechanism.
油圧緩衝器1は、内部に作動油を充填したシリ
ンダ2を筒体3内に摺動自在に嵌装し、筒体3の
上端部外周面にはシールカバー3aを装着し、シ
ールカバー3aの上部はシリンダ2の外周部に摺
接している。そして、筒体3の底面にはキヤツプ
4を装着し、キヤツプ4の上面にはバンプラバー
5を取付けている。 The hydraulic shock absorber 1 includes a cylinder 2 filled with hydraulic oil, which is slidably fitted into a cylindrical body 3, and a seal cover 3a is attached to the outer peripheral surface of the upper end of the cylindrical body 3. The upper part is in sliding contact with the outer peripheral part of the cylinder 2. A cap 4 is attached to the bottom surface of the cylinder 3, and a bump rubber 5 is attached to the top surface of the cap 4.
また、筒体3の下側からキヤツプ4を介してロ
アーブラケツト6に後端部を固定したピストンロ
ツド7を挿通して固定し、このピストンロツド7
の先端部にはシリンダ2の内周面に摺接するピス
トン8を取付けてシリンダ2内周を上部油室と下
部油室に画成し、更にピストン8の下面及び上面
にはそれぞれ板バルブ9,10を設けている。 Further, a piston rod 7 whose rear end is fixed to the lower bracket 6 is inserted and fixed from the lower side of the cylinder 3 via the cap 4.
A piston 8 is attached to the tip of the cylinder 2 to slide on the inner circumferential surface of the cylinder 2 to define the inner circumference of the cylinder 2 into an upper oil chamber and a lower oil chamber.Furthermore, plate valves 9 and 9 are attached to the lower and upper surfaces of the piston 8, respectively. There are 10.
更に、シリンダ2の下端部にはシリンダキヤツ
プ11を嵌着し、シリンダキヤツプ11の上方に
はガイド12を嵌装し、このガイド12の内周面
にはピストンロツド7外周に摺接するオイルシー
ル13を嵌装し、更にまたシリンダ2の上端部に
はアツパーメタル14を取付けている。 Furthermore, a cylinder cap 11 is fitted to the lower end of the cylinder 2, a guide 12 is fitted above the cylinder cap 11, and an oil seal 13 that slides on the outer circumference of the piston rod 7 is provided on the inner peripheral surface of the guide 12. Furthermore, an upper metal 14 is attached to the upper end of the cylinder 2.
そして、シリンダ2の上部外周にはスプリング
シート16を嵌着し、筒体3の中程外周部にはバ
ネ受けとしてのスプリングシート17をシリンダ
の軸方向及び周方向に移動可能に嵌装して、これ
らのスプリングシート16とスプリングシート1
7との間に懸架バネ18を張架し、更にスプリン
グシート17の下部にバネ荷重調整機構20を設
けている。 A spring seat 16 is fitted on the upper outer periphery of the cylinder 2, and a spring seat 17 as a spring receiver is fitted on the middle outer periphery of the cylinder 3 so as to be movable in the axial and circumferential directions of the cylinder. , these spring seats 16 and spring seats 1
A suspension spring 18 is stretched between the spring seat 17 and the spring seat 17, and a spring load adjustment mechanism 20 is provided below the spring seat 17.
このバネ荷重調整機構20は、スプリングシー
ト17の下面にアジヤスタ21を固着して筒体3
の外周に回動自在に嵌装し、このアジヤスタ21
の下端面には180°の位相で勾配が一様な二つのテ
ーパ面22,22を形成し、更にテーパ面22,
22の始端部には下方に膨出したストツパ部2
3,23を形成している。 This spring load adjustment mechanism 20 is constructed by fixing an adjuster 21 to the lower surface of the spring seat 17 and
The adjuster 21 is rotatably fitted around the outer circumference of the adjuster 21.
Two tapered surfaces 22, 22 with a uniform gradient at a phase of 180° are formed on the lower end surface of the
At the starting end of 22, there is a stopper part 2 that bulges downward.
3,23 are formed.
また、筒体3の外周面にはアジヤスタ21の下
側にストツパ25を固着し、このストツパ25の
上端面には180°の位相で二つのテーパ面26,2
6を形成し、このテーパ面26,26上にアジヤ
スタ21のテーパ面22,22の一部をなすスト
ツパ部23,23のテーパ面を当接させている。
更に、このストツパ25のテーパ面26,26の
終端部にはアジヤスタ25のストツパ部23,2
3と係合可能な上方に膨出したストツパ部27,
27を形成している。 Further, a stopper 25 is fixed to the outer peripheral surface of the cylinder 3 below the adjuster 21, and the upper end surface of this stopper 25 has two tapered surfaces 26, 2 with a phase of 180°.
6, and the tapered surfaces of stopper portions 23, 23, which form part of the tapered surfaces 22, 22 of the adjuster 21, are brought into contact with the tapered surfaces 26, 26.
Further, the stopper portions 23, 2 of the adjuster 25 are provided at the terminal ends of the tapered surfaces 26, 26 of the stopper 25.
3, an upwardly bulging stopper portion 27 that can be engaged with
27 is formed.
そして、このストツパ25の外周部には外側に
突出して円筒状の筒体28を固着し、この筒体2
8内にストツパピン29を摺動自在に挿通し、更
にストツパピン29と筒体3の外周面との間にコ
イルスプリング30を縮装して、このスプリング
30によつてストツパピン29を突出方向に付勢
している。ストツパピン29には底部にフランジ
を形成し、筒体28の開口端にもフランジを形成
して、ストツパピン29が筒体28から抜け落ち
ないようにしている。 A cylindrical body 28 is fixed to the outer periphery of the stopper 25 so as to protrude outward.
The stopper pin 29 is slidably inserted into the inside of the cylinder 8, and a coil spring 30 is compressed between the stopper pin 29 and the outer peripheral surface of the cylinder 3, and the spring 30 urges the stopper pin 29 in the projecting direction. are doing. A flange is formed at the bottom of the stopper pin 29, and a flange is also formed at the open end of the cylindrical body 28 to prevent the stopper pin 29 from falling out from the cylindrical body 28.
更に、スプリングシート17の下面にはアジヤ
スタ21及びストツパ25の外側に位置して回動
リング32を固着している。この回動リング32
には周囲に所定の間隔でストツパ25のストツパ
ピン29が係合可能な複数の長孔33を形成して
いる。また、この回動リング32の外周面には各
長孔33の下側にバネ荷重の初期セツト位置を表
示する数字34を刻設している。 Further, a rotating ring 32 is fixed to the lower surface of the spring seat 17, located outside the adjuster 21 and the stopper 25. This rotating ring 32
A plurality of elongated holes 33 are formed around the periphery at predetermined intervals so that the stopper pins 29 of the stopper 25 can engage with each other. Further, on the outer circumferential surface of the rotary ring 32, a number 34 is engraved below each elongated hole 33 to indicate the initial set position of the spring load.
以上において、バネ荷重を調整するときには、
第5図に示すように、例えばアーム41の基部及
び先端部にそれぞれ回動リング32の長孔33に
挿入可能な突起42,43を形成し、アーム41
の基部に把持部44を形成してなる工具40を使
用し、この工具40にて回動リング32を回動し
てアジヤスタ21を回動する。 In the above, when adjusting the spring load,
As shown in FIG. 5, for example, protrusions 42 and 43 that can be inserted into the elongated hole 33 of the rotation ring 32 are formed at the base and tip of the arm 41, respectively.
A tool 40 having a grip portion 44 formed at the base thereof is used to rotate the rotary ring 32 and rotate the adjuster 21.
つまり、工具40のアーム41の突起42をス
トツパピン29が嵌入している回動リング32の
長孔33に挿入し、アーム41の突起43を回動
リング32の他の所要の長孔33に係合すること
によつて工具40と回動リング32とが固定さ
れ、このとき工具40の突起42によつてストツ
パピン29がスプリング30の付勢力に抗して押
されて筒体28内に押込まれ、ストツパ25のス
トツパピン29と回動リング32の長孔33との
係合が外れて、回動リング32はストツパ25に
対して自由に回動できるようになる。 That is, the protrusion 42 of the arm 41 of the tool 40 is inserted into the elongated hole 33 of the rotating ring 32 into which the stopper pin 29 is fitted, and the protrusion 43 of the arm 41 is engaged with the other required elongated hole 33 of the rotating ring 32. By fitting together, the tool 40 and the rotation ring 32 are fixed, and at this time, the stopper pin 29 is pushed by the protrusion 42 of the tool 40 against the urging force of the spring 30 and pushed into the cylinder body 28. , the engagement between the stopper pin 29 of the stopper 25 and the elongated hole 33 of the rotating ring 32 is disengaged, and the rotating ring 32 can freely rotate relative to the stopper 25.
そこで、工具40を例えば第5図で矢示A方向
に回動操作することによつて、回動リング32も
矢示A方向に回動する。この場合、アジヤスタ2
1とストツパ25との位置関係が第4図に示す状
態(最低荷重状態)であるとすると、回動リング
32と一体のアジヤスタ21は第4図の矢示B方
向に回動し、このときアジヤスタ25のストツパ
部23の下端面はストツパ25のテーパ面26上
を滑らかに移動するので、アジヤスタ21は回動
しながら筒体3の軸方向すなわちシリンダ2の軸
方向に上方向に移動する。 Therefore, by rotating the tool 40, for example, in the direction of arrow A in FIG. 5, the rotation ring 32 is also rotated in the direction of arrow A. In this case, adjuster 2
1 and the stopper 25 is in the state shown in FIG. 4 (minimum load state), the adjuster 21 integrated with the rotating ring 32 rotates in the direction of arrow B in FIG. Since the lower end surface of the stopper portion 23 of the adjuster 25 moves smoothly on the tapered surface 26 of the stopper 25, the adjuster 21 moves upward in the axial direction of the cylinder 3, that is, in the axial direction of the cylinder 2, while rotating.
このアジヤスタ25の上方向への移動によつて
スプリングシート17が筒体3の外周を上昇する
ので、懸架バネ18が圧縮されて、懸架バネ18
のバネ荷重が高く調整される。 Due to the upward movement of the adjuster 25, the spring seat 17 rises on the outer periphery of the cylindrical body 3, so the suspension spring 18 is compressed.
The spring load of is adjusted higher.
このようにバネ荷重を高く調整するときに、バ
ネ荷重が最高になつた状態ではアジヤスタ21の
ストツパ部23がストツパ25のストツパ部27
と係合してアジヤスタ21をそれ以上回動するこ
とができなくなり、したがつてアジヤスタ21が
最高荷重位置から最低荷重位置へ急激に移動して
ストツパ25との間で衝撃を発生することがなく
なる。 When adjusting the spring load to a high value in this way, when the spring load is at its maximum, the stopper part 23 of the adjuster 21 is moved to the stopper part 27 of the stopper 25.
This prevents the adjuster 21 from rotating any further, and therefore prevents the adjuster 21 from suddenly moving from the highest load position to the lowest load position and generating an impact between it and the stopper 25. .
また、バネ荷重を高く調整した状態から工具4
0を逆方向に回動操作することによつて、上述と
は逆にスプリングシート17が筒体3の外周を下
降して、懸架バネ18が伸びて、懸架バネ18の
バネ荷重が低く調整される。 Also, from the state where the spring load is adjusted high, the tool 4
0 in the opposite direction, the spring seat 17 moves down the outer periphery of the cylindrical body 3 contrary to the above, the suspension spring 18 is extended, and the spring load of the suspension spring 18 is adjusted to be low. Ru.
そして、回動リング32の所要バネ荷重に対応
する長孔33がストツパ25のストツパピン29
と係合する位置までアジヤスタ21を回動してバ
ネ荷重を調整した後、工具40を回動リング32
から外すことによつて、工具40の突起42によ
るストツパピン29の押圧が解かれて、ストツパ
ピン29はスプリング30の付勢力で突出して対
応する回動リング32の長孔33内に嵌入して係
合する。 The long hole 33 corresponding to the required spring load of the rotation ring 32 is located on the stopper pin 29 of the stopper 25.
After adjusting the spring load by rotating the adjuster 21 to the position where it engages with the
By removing it from the tool 40, the pressure on the stopper pin 29 by the protrusion 42 of the tool 40 is released, and the stopper pin 29 protrudes by the biasing force of the spring 30 and fits into the elongated hole 33 of the corresponding rotary ring 32 to engage. do.
それによつて、回動リング32はストツパピン
29で係止されてそのときの位置に保持されるの
で、アジヤスタ21も回動が止められ、懸架バネ
18の荷重が維持される。このとき、アジヤスタ
21とストツパ25とはストツパ部23のテーパ
面とストツパ25のテーパ面26とで当接し、こ
の当接部分が幅広であるので、アジヤスタ21に
かかる懸架バネ18の反力はアジヤスタ21のス
トツパ部23を介してストツパ25全体で受けら
れる。また、この場合ストツパピン29が係合し
ている長孔33の下側に付した数字34を見るこ
とによつてそのときのバネ荷重の程度を容易に知
ることができる。 As a result, the rotation ring 32 is locked by the stopper pin 29 and held at the current position, so that the adjuster 21 is also stopped from rotating and the load on the suspension spring 18 is maintained. At this time, the adjuster 21 and the stopper 25 come into contact with the tapered surface of the stopper portion 23 and the tapered surface 26 of the stopper 25, and since this contact portion is wide, the reaction force of the suspension spring 18 applied to the adjuster 21 is transferred to the adjuster 21. It is received by the entire stopper 25 via the stopper part 23 of 21. Further, in this case, by looking at the number 34 attached to the lower side of the elongated hole 33 with which the stopper pin 29 is engaged, the degree of the spring load at that time can be easily determined.
(考案の効果)
以上説明したように本考案によれば、ストツパ
とアジヤスタのテーパ面の勾配を一様とし、長孔
を貫通した回動リングをアジヤスタに固着し、そ
の長孔に選択的に係合するとともに、係合してい
る長孔の外方からの押圧力によつて係合が解除さ
れるストツパピンを進退自在に設けることによ
り、ストツパピンを押圧後退させればアジヤスタ
は小さな力で滑らかに回動され、ストツパ位置は
シリンダの軸方向に移動されてバネ荷重が調整さ
れ、また、ストツパピンが回動リングの長孔に係
合することによつてアジヤスタの回動が規制さ
れ、当接しているテーパ面がストツパとして作用
するので一定のバネ荷重が維持される。(Effects of the invention) As explained above, according to the invention, the slopes of the taper surfaces of the stopper and adjuster are made uniform, the rotary ring passing through the elongated hole is fixed to the adjuster, and the elongated hole is selectively attached to the adjuster. By providing a stopper pin that can move forward and backward as it engages and is disengaged by the pressing force from the outside of the engaged elongated hole, the adjuster can be moved smoothly with a small force by pushing the stopper pin back. The stopper position is moved in the axial direction of the cylinder to adjust the spring load, and the stopper pin engages with the long hole of the rotary ring to restrict rotation of the adjuster and prevent contact. Since the tapered surface acts as a stopper, a constant spring load is maintained.
したがつて、従来型の段階的カム面でなる調整
機構の操作に比較して小さな力で容易に調整操作
を行うことができ、操作性が大幅に向上し、ま
た、勾配が一様なテーパ面の形成は、段階的カム
面に較べて加工が極めて容易であり、生産コスト
の低減を図ることができる。 Therefore, compared to the operation of a conventional adjustment mechanism consisting of a stepwise cam surface, adjustment can be easily performed with a small force, greatly improving operability. Forming a surface is much easier to process than a stepped cam surface, and production costs can be reduced.
第1図は本考案にかかるバネ荷重調整機構を備
えた油圧緩衝器の半断面図、第2図は第1図のバ
ネ荷重調整機構の要部拡大断面図、第3図は第2
図のバネ荷重調整機構の平断面図、第4図はバネ
荷重調整機構の要部展開図、第5図はバネ荷重調
整機構による荷重調整の説明に供する平断面図、
第6図は従来のバネ荷重調整機構の要部側面図で
ある。
尚、図面中1油圧緩衝器、2はシリンダ、3は
筒体、16,17はスプリングシート、18は懸
架バネ、21はアジヤスタ、22はテーパ面、2
3はストツパ部、25はストツパ、26はテーパ
面、27はストツパ部、29はストツパピン、3
2は回動リング、33は長孔である。
FIG. 1 is a half-sectional view of a hydraulic shock absorber equipped with a spring load adjustment mechanism according to the present invention, FIG. 2 is an enlarged sectional view of the main part of the spring load adjustment mechanism of FIG. 1, and FIG.
4 is a developed view of the main parts of the spring load adjustment mechanism, and FIG. 5 is a plane sectional view for explaining load adjustment by the spring load adjustment mechanism.
FIG. 6 is a side view of essential parts of a conventional spring load adjustment mechanism. In the drawing, 1 is a hydraulic shock absorber, 2 is a cylinder, 3 is a cylindrical body, 16, 17 are spring seats, 18 is a suspension spring, 21 is an adjuster, 22 is a tapered surface, 2
3 is a stopper part, 25 is a stopper, 26 is a tapered surface, 27 is a stopper part, 29 is a stopper pin, 3
2 is a rotating ring, and 33 is a long hole.
Claims (1)
周、又はピストンロツドに係合する筒体の外周
に、上面に少なくとも2以上の同一円周方向のテ
ーパ面を形成した環状のストツパを固着し、又、
前記シリンダ又は筒体の外周に前記ストツパーの
テーパ面と当接し、かつ、180度以下の角度範囲
内の回動に対応してその軸方向位置を変化させる
ことによりバネ荷重を調節する環状のアジヤスタ
を回動自在に嵌装したバネ荷重調整機構におい
て、 前記ストツパの各テーパ面はその勾配を一様と
し、このテーパ面とそれぞれ当接するテーパ面を
前記環状のアジヤスタに形成するとともに、この
アジヤスタにはストツパの外周に面する円筒状の
回動リングを固着し、この回動リングの分周位置
にストツパの軸方向の移動長さをなす複数の長孔
を貫通し、この長孔に選択的に係合してアジヤス
タの回動を規制するとともに、係合している長孔
の外方からの押圧力によつて係合を解除するスト
ツパピンを前記ストツパに進退自在に設けたこと
を特徴とする緩衝器のバネ荷重調整機構。[Claims for Utility Model Registration] An annular shape in which at least two or more tapered surfaces in the same circumferential direction are formed on the upper surface on the outer periphery of a cylinder of a shock absorber that is vertically expandable or retractable, or on the outer periphery of a cylindrical body that engages with a piston rod. Fix the stopper of the
an annular adjuster that comes into contact with the tapered surface of the stopper on the outer periphery of the cylinder or cylindrical body and adjusts the spring load by changing its axial position in response to rotation within an angular range of 180 degrees or less; In the spring load adjustment mechanism in which the stopper is rotatably fitted, each tapered surface of the stopper has a uniform slope, and the annular adjuster is formed with a tapered surface that comes into contact with each of the tapered surfaces, and a A cylindrical rotating ring facing the outer periphery of the stopper is fixed, and a plurality of elongated holes corresponding to the axial movement length of the stopper are penetrated at dividing positions of the rotating ring, and selective holes are inserted into the elongated holes. The stopper pin is provided in the stopper so as to be movable forward and backward, the stopper pin being engaged with the adjuster to restrict the rotation of the adjuster and releasing the engagement by a pressing force from the outside of the engaged elongated hole. Shock absorber spring load adjustment mechanism.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1987068600U JPH0516424Y2 (en) | 1987-05-08 | 1987-05-08 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1987068600U JPH0516424Y2 (en) | 1987-05-08 | 1987-05-08 |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS63177336U JPS63177336U (en) | 1988-11-17 |
JPH0516424Y2 true JPH0516424Y2 (en) | 1993-04-30 |
Family
ID=30908566
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP1987068600U Expired - Lifetime JPH0516424Y2 (en) | 1987-05-08 | 1987-05-08 |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0516424Y2 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5000943B2 (en) * | 2006-07-28 | 2012-08-15 | 日本ワイパブレード株式会社 | Wiper arm |
JP7198131B2 (en) * | 2019-03-22 | 2022-12-28 | Kybモーターサイクルサスペンション株式会社 | suspension system |
EP4269136B1 (en) * | 2022-04-26 | 2024-06-05 | Volvo Car Corporation | Adjustment assembly for compensating a length variation of a spring element and wheel suspension assembly for a vehicle |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4330512Y1 (en) * | 1966-10-25 | 1968-12-12 | ||
JPS5281824A (en) * | 1975-05-28 | 1977-07-08 | Girling Ltd | Suspension unit for vehicle |
JPS5811150B2 (en) * | 1978-11-18 | 1983-03-01 | クラリオン株式会社 | TV signal identification device |
JPS5820741B2 (en) * | 1978-10-14 | 1983-04-25 | ファナック株式会社 | Machining center tool change mechanism |
JPS58146741A (en) * | 1982-02-25 | 1983-09-01 | Yamaha Motor Co Ltd | Spring adjuster of shock absorber |
JPS59113335A (en) * | 1982-12-20 | 1984-06-30 | Yamaha Motor Co Ltd | Spring force adjuster of cylindrical cushion unit |
JPS61140633A (en) * | 1984-12-08 | 1986-06-27 | Showa Seisakusho:Kk | Rear wheel suspension spring force adjusting device for vehicle |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5811150U (en) * | 1981-07-14 | 1983-01-24 | カヤバ工業株式会社 | Suspension spring load adjustment device for hydraulic shock absorbers |
JPS5820741U (en) * | 1981-08-03 | 1983-02-08 | 株式会社昭和製作所 | Spring load adjustment device for hydraulic shock absorbers |
JPS58163740U (en) * | 1982-04-28 | 1983-10-31 | カヤバ工業株式会社 | Initial setting load adjustment device for suspension springs in hydraulic shock absorbers |
JPS58165352U (en) * | 1982-04-30 | 1983-11-04 | 株式会社昭和製作所 | Hydraulic shock absorber spring load adjustment device |
JPS58196444U (en) * | 1982-06-25 | 1983-12-27 | 株式会社昭和製作所 | Hydraulic shock absorber spring load adjustment device |
JPS6085643U (en) * | 1983-11-11 | 1985-06-13 | ヤマハ発動機株式会社 | Buffer spring adjustment device in hydraulic shock absorber |
JPS61128433U (en) * | 1985-01-30 | 1986-08-12 |
-
1987
- 1987-05-08 JP JP1987068600U patent/JPH0516424Y2/ja not_active Expired - Lifetime
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS4330512Y1 (en) * | 1966-10-25 | 1968-12-12 | ||
JPS5281824A (en) * | 1975-05-28 | 1977-07-08 | Girling Ltd | Suspension unit for vehicle |
JPS5820741B2 (en) * | 1978-10-14 | 1983-04-25 | ファナック株式会社 | Machining center tool change mechanism |
JPS5811150B2 (en) * | 1978-11-18 | 1983-03-01 | クラリオン株式会社 | TV signal identification device |
JPS58146741A (en) * | 1982-02-25 | 1983-09-01 | Yamaha Motor Co Ltd | Spring adjuster of shock absorber |
JPS59113335A (en) * | 1982-12-20 | 1984-06-30 | Yamaha Motor Co Ltd | Spring force adjuster of cylindrical cushion unit |
JPS61140633A (en) * | 1984-12-08 | 1986-06-27 | Showa Seisakusho:Kk | Rear wheel suspension spring force adjusting device for vehicle |
Also Published As
Publication number | Publication date |
---|---|
JPS63177336U (en) | 1988-11-17 |
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