JPS6222018B2 - - Google Patents
Info
- Publication number
- JPS6222018B2 JPS6222018B2 JP16108679A JP16108679A JPS6222018B2 JP S6222018 B2 JPS6222018 B2 JP S6222018B2 JP 16108679 A JP16108679 A JP 16108679A JP 16108679 A JP16108679 A JP 16108679A JP S6222018 B2 JPS6222018 B2 JP S6222018B2
- Authority
- JP
- Japan
- Prior art keywords
- spring
- coil spring
- damper
- cylinder
- receiver
- 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
- 239000000725 suspension Substances 0.000 claims description 12
- 230000001105 regulatory effect Effects 0.000 claims description 3
- 238000007906 compression Methods 0.000 claims description 2
- 230000000750 progressive effect Effects 0.000 description 6
- 230000035939 shock Effects 0.000 description 3
- 238000013016 damping Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G15/00—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type
- B60G15/02—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring
- B60G15/06—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper
- B60G15/062—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper the spring being arranged around the damper
- B60G15/065—Resilient suspensions characterised by arrangement, location or type of combined spring and vibration damper, e.g. telescopic type having mechanical spring and fluid damper the spring being arranged around the damper characterised by the use of a combination of springs
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vehicle Body Suspensions (AREA)
- Combined Devices Of Dampers And Springs (AREA)
- Vibration Prevention Devices (AREA)
- Fluid-Damping Devices (AREA)
Description
【発明の詳細な説明】
本発明は油圧ダンパとコイルバネを併用した車
両用懸架バネ装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a suspension spring device for a vehicle that uses both a hydraulic damper and a coil spring.
更に詳細には、バネ定数の異る異径の二種のコ
イルバネをダンパと並設し、累進比率の大きいバ
ネ特性を得ることができるようにした車両用懸架
バネ装置に関する。 More specifically, the present invention relates to a suspension spring device for a vehicle in which two types of coil springs having different spring constants and different diameters are arranged in parallel with a damper to obtain spring characteristics with a large progressive ratio.
油圧ダンパとコイルバネとを組み合せた車両用
の懸架用バネ装置は知られている。この種バネ装
置の特性は、乗員の乗心地性を考慮するとバネ上
振動数を低く抑制することのできるバネ定数の低
いバネ特性が好ましい。一方、車両の積載時の特
性を考慮すると荷重をできるだけで大きくとる必
要があるためバネ定数の高いバネ特性が好まし
い。このように相反する要求をともに満足させる
ため、従来のこの種バネ装置のバネ特性は乗員一
人のみのときと積載時との両方の乗心地を適切な
ものにするために中庸なものにならざるを得ない
のが現状である。 2. Description of the Related Art A suspension spring device for a vehicle that combines a hydraulic damper and a coil spring is known. This type of spring device preferably has spring characteristics with a low spring constant that can suppress the sprung mass frequency to a low level in consideration of riding comfort for the occupant. On the other hand, considering the loading characteristics of the vehicle, it is necessary to increase the load as much as possible, so spring characteristics with a high spring constant are preferable. In order to satisfy both of these conflicting demands, the spring characteristics of conventional spring devices of this type have to be moderate in order to provide appropriate riding comfort both when there is only one occupant and when the vehicle is loaded. The current situation is that we do not get any.
そこで上記を改善すべくバネ特性を累進的に得
るべく二段バネ、三段バネ等の多段バネが懸架装
置に用いられている。この種の装置は、バネ定数
及び密着荷重が異る複数のバネを直列に用いてい
るため、懸架装置及びこれの取付部の限られたス
ペース内でバネ特性の累進率を大きくとることは
実際上極めて困難であり、実用上上記を充分に解
決するものは未だ提案されていない。 Therefore, in order to improve the above-mentioned problem, multi-stage springs such as two-stage springs and three-stage springs are used in suspension systems in order to progressively obtain spring characteristics. This type of device uses multiple springs with different spring constants and contact loads in series, so it is difficult to achieve a large progressive rate of spring characteristics within the limited space of the suspension device and its mounting area. This is extremely difficult, and nothing that satisfactorily solves the above problems has yet been proposed.
本発明者は従来の上記問題点及び累進式装置の
上間問題点を有効に、且つ合理的に解決すべく本
発明をなしたものである。 The present inventor has devised the present invention in order to effectively and rationally solve the above-mentioned conventional problems and the intermediate problems of progressive type devices.
本発明の目的は、バネ定数の異る異径の二種の
コイルバネをダンパと並設し、ダンパのストロー
クに応じて各コイルバネを直列に接続し、或は一
方のコイルバネのみのバネ特性を得、更には各バ
ネを並列に接続した特性を得る如くし、各バネ固
有の特性と併せて累進率の大きいバネ特性を得る
ことができ、積載の有無にかかわらず乗心地性を
実用上充分に満足し得るものを得ることができる
ようにした車両用懸架バネ装置を提供するところ
にある。 The object of the present invention is to install two types of coil springs with different spring constants and different diameters in parallel with a damper, and to connect each coil spring in series according to the stroke of the damper, or to obtain the spring characteristics of only one coil spring. Furthermore, by connecting each spring in parallel, it is possible to obtain spring characteristics with a large progressive rate in conjunction with the characteristics unique to each spring, and to achieve sufficient riding comfort for practical use regardless of whether there is a load or not. An object of the present invention is to provide a suspension spring device for a vehicle that can provide a satisfactory product.
次に本発明の好適一実施例を添付図面を参照し
つつ詳述する。これにより本発明の更なる目的及
び利点を明らかにする。 Next, a preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings. This will reveal further objects and advantages of the invention.
第１図は本発明の具体的一実施例としての装置
を示し、図示は二輪車用のリヤクツシヨンユニツ
トを示しているが、自動車の懸架バネ装置として
具体的構造を若干変更して実施することができる
ことは当然である。 FIG. 1 shows a device as a specific embodiment of the present invention, and although the illustration shows a rear suspension unit for a two-wheeled vehicle, it can also be implemented as a suspension spring device for an automobile by slightly changing the specific structure. Of course it can be done.
懸架バネ装置１は、ピストンおよびバルブ等を
内装したシリンダ２ａにロツド３が摺動自在に嵌
挿された油圧ダンパ２を備え、該油圧ダンパ２の
シリンダ２ａの下端部がジヨイント４を介して車
輪側部材に、また、シリンダ２ａの上端部がジヨ
イント５を介して車体側部材に支持される。 The suspension spring device 1 includes a hydraulic damper 2 in which a rod 3 is slidably fitted into a cylinder 2a containing a piston, a valve, etc., and the lower end of the cylinder 2a of the hydraulic damper 2 is connected to the wheel via a joint 4. The upper end of the cylinder 2a is supported by the side member, and the upper end of the cylinder 2a is supported by the vehicle body side member via a joint 5.
ロツド３のジヨイント５は大径のフランジ部５
ａを備え、フランジ部５ａの下面中央部にはロツ
ド３の上端部を囲繞する如く上部ストツパラバー
６が設けられる。フランジ部５ａ下面周辺部には
シリンダ２ａの外径より内径が充分大きい筒状の
カバー７が所定長さ軸方向に延出され、ロツド３
及びシリンダ２ａの上部を囲繞する。シリンダ２
ａの外周には摺動ジヨイント８が摺動自在に配設
され、ジヨイント８はシリンダ２ａの外周とその
内周との間に隙間を形成する如く筒状体からな
り、下端のバネ受部８ａの内径部でシリンダ２ａ
外径部と摺合している。ジヨイント８の上端部に
は外方に折曲したリング状の係止フランジ部８ｂ
が形成され、該フランジ部８ｂは断面内向チヤン
ネル型でリング状の規制部材たる中間部材９に軸
方向に摺動し得る如く係合している。中間部材９
の下片９ａとフランジ部８ｂ間には中間ラバー１
０を介設し、フランジ部８ｂと上片９ｂとは軸方
向に所定の長さ離間せしめ、中間部材９の外周は
カバー７の内周壁に摺合案内される如くし、軸方
向に摺動する。 Joint 5 of rod 3 is a large diameter flange 5
An upper stop lever 6 is provided at the center of the lower surface of the flange portion 5a so as to surround the upper end portion of the rod 3. A cylindrical cover 7 having an inner diameter sufficiently larger than the outer diameter of the cylinder 2a extends in the axial direction for a predetermined length around the lower surface of the flange portion 5a.
and surrounds the upper part of the cylinder 2a. cylinder 2
A sliding joint 8 is slidably disposed on the outer periphery of the cylinder 2a, and the joint 8 is made of a cylindrical body so as to form a gap between the outer periphery of the cylinder 2a and its inner periphery. At the inner diameter of cylinder 2a
It slides against the outer diameter part. The upper end of the joint 8 has a ring-shaped locking flange 8b bent outward.
The flange portion 8b has an inward channel cross section and is engaged with an intermediate member 9, which is a ring-shaped regulating member, so as to be able to slide in the axial direction. Intermediate member 9
There is an intermediate rubber 1 between the lower piece 9a and the flange part 8b.
0 is interposed, the flange portion 8b and the upper piece 9b are separated by a predetermined length in the axial direction, and the outer periphery of the intermediate member 9 is slidably guided by the inner peripheral wall of the cover 7 so as to slide in the axial direction. .
カバー７内のフランジ部５ａ下面中間段部５ｂ
は第２の固定ばね受を構成し、該中間段部と筒状
の摺動ジヨイント８のバネ受部８ａ間にはロツド
３及びシリンダ２ａの上部乃至中間部を囲繞する
如く小径の第１のコイルバネ１１を縮装し、バネ
１１の中間部乃至下部はシリンダ２ａ外周とジヨ
イント８の内周との間の隙間に収納される。一
方、カバー７内周とジヨイント８外周との間には
該ジヨイント８外周及びシリンダ２ａ外周を囲繞
する如く大径の第２のコイルバネ１２を縮装し、
コイルバネ１２の一端はシリンダ２ａ下部外周の
第１の固定バネ受１３で支持され、他端はジヨイ
ント８と係止フランジ部８ｂを介して係合する中
間部材９の下片９ａに支持される。尚図面中１４
は摺動ジヨイント８の下部ストツパラバーであ
る。 Flange portion 5a inside cover 7 Lower middle step portion 5b
constitutes a second fixed spring receiver, and between the intermediate stage portion and the spring receiver portion 8a of the cylindrical sliding joint 8 is a small-diameter first spring receiver that surrounds the upper to middle portions of the rod 3 and the cylinder 2a. The coil spring 11 is compressed, and the middle or lower part of the spring 11 is housed in the gap between the outer periphery of the cylinder 2a and the inner periphery of the joint 8. On the other hand, a second coil spring 12 having a large diameter is compressed between the inner circumference of the cover 7 and the outer circumference of the joint 8 so as to surround the outer circumference of the joint 8 and the outer circumference of the cylinder 2a.
One end of the coil spring 12 is supported by a first fixed spring receiver 13 on the lower outer periphery of the cylinder 2a, and the other end is supported by a lower piece 9a of an intermediate member 9 that engages with the joint 8 via a locking flange portion 8b. 14 in the drawing
is the lower stop lever of the sliding joint 8.
以上のコイルバネの内側の第１のバネ１１は例
えばバネ定数の低いものとし、外側の第２のバネ
１２はこれよりもバネ定数の高いものを用いるも
のとする。又前記摺動ジヨイント８と前記中間部
材９の長手方向の長さはダンパーの圧縮工程時に
前記摺動ジヨイント８下端が第１の固定バネ受１
３に当接した後にコイルバネ１１とコイルバネ１
２とを同時に圧縮する寸法に設定する。 The first spring 11 on the inside of the coil springs described above has a low spring constant, for example, and the second spring 12 on the outside has a higher spring constant. Further, the length in the longitudinal direction of the sliding joint 8 and the intermediate member 9 is such that the lower end of the sliding joint 8 is connected to the first fixed spring receiver 1 during the compression process of the damper.
3, the coil spring 11 and the coil spring 1
2 and 2 to be compressed at the same time.
図は車両に取リ付けられ、無負荷状態か、或は
乗員の荷重のみが負荷されている状態としよう。 In the figure, it is assumed that the vehicle is attached to a vehicle and is in an unloaded state or in a state where only the load of the occupant is applied.
バネ装置１は路面の凹突等による反力でダンパ
２のロツド３がシリンダ２ａに対して軸方向に摺
動し、衝撃及び振動を吸収、減衰し、また、ロツ
ドのストロークでバネがたわみ、衝撃、振動を吸
収、減衰する。 In the spring device 1, the rod 3 of the damper 2 slides in the axial direction with respect to the cylinder 2a due to the reaction force caused by irregularities in the road surface, absorbing and damping shocks and vibrations, and the spring deflects due to the stroke of the rod. Absorbs and dampens shock and vibration.
ところでストロークの初期、即ちロツド３がシ
リンダ２ａに対して相対的にストロークするａの
領域ではバネは第１及び第２のバネ１１，１２が
直列に接続され、第１のバネ１１が主に軸方向に
たわみ、これのバネ定数が低いためストロークの
小さい領域ａ内での路面の小凹突に起因する微振
動を吸収することができ、この領域で微振動を車
体側に伝えないようにバネ定数を充分に低く設定
し、効果的な微振動吸収、減衰を行い、ストロー
ク初期での効果のあるバネ特性を得ることができ
る。 By the way, at the beginning of the stroke, that is, in the region a where the rod 3 strokes relative to the cylinder 2a, the first and second springs 11 and 12 are connected in series, and the first spring 11 is mainly connected to the shaft. Because it has a low spring constant, it can absorb minute vibrations caused by small bumps in the road surface within the small stroke region a, and the spring By setting the constant sufficiently low, effective micro-vibration absorption and damping can be achieved, and effective spring characteristics can be obtained at the initial stage of the stroke.
ロツド３のストロークの進行でこれが中期に達
すると第２のコイルバネ１２の上端を係止した中
間部材９の上片９ｂとロツド側であるフランジ部
５ａが干渉する。従つて摺動ジヨイント８のバネ
受部８ａが下部ストツパラバー１４に接する迄の
ストロークｂの領域ではストロークａで第１のバ
ネ１１がたわんだままの状態で摺動ジヨイント８
がシリンダ２ａの外周上を軸方向に摺動するため
第２のバネ１２がたわみ、第２のバネ１２のみの
バネ特性を得る。第２のバネ１２の特性を第１の
バネ１１のバネ定数より高くし、振動等の吸収
と、適度のバネ上振動数を確保する如くバネ定数
を設定することにより中期のストロークでは双方
をともに満足させる特性が得られる。 When the stroke of the rod 3 reaches the middle stage, the upper piece 9b of the intermediate member 9, which locks the upper end of the second coil spring 12, interferes with the flange portion 5a on the rod side. Therefore, in the region of stroke b until the spring receiving part 8a of the sliding joint 8 comes into contact with the lower stopper lever 14, the sliding joint 8 remains bent during the stroke a.
slides in the axial direction on the outer periphery of the cylinder 2a, the second spring 12 is deflected, and the spring characteristics of the second spring 12 alone are obtained. By making the characteristics of the second spring 12 higher than the spring constant of the first spring 11 and setting the spring constant so as to absorb vibrations and ensure an appropriate sprung mass frequency, both springs can be used together during the middle stroke. Satisfied characteristics can be obtained.
ロツド３の更なるストロークの進行で中間部材
９の上片９ｂと摺動ジヨイント８の係止フランジ
部８ｂとは衝合し、以後のストロークは摺動ジヨ
イント８と中間部材９との摺動でなされ、これに
よりバネ１１，１２は協働して並列に接続された
状態でたわむこととなる。従つてストローク領域
ｃでは第１のバネ１１、第２のバネ１２の合算さ
れたバネ定数が得られ、バネ定数は急に高くな
り、大荷重によるロツド３のストロークの進行を
弾性的に抑制し、フルバンプを可及的に抑制する
ことができる。 As the stroke of the rod 3 further advances, the upper piece 9b of the intermediate member 9 and the locking flange portion 8b of the sliding joint 8 collide, and the subsequent stroke is caused by the sliding between the sliding joint 8 and the intermediate member 9. As a result, the springs 11 and 12 are deflected together in a parallel connected state. Therefore, in the stroke region c, the spring constant is the sum of the first spring 11 and the second spring 12, and the spring constant suddenly becomes high, elastically suppressing the progress of the stroke of the rod 3 due to a large load. , full bumps can be suppressed as much as possible.
これを第２図のグラフで示すと、縦軸は荷重
を、又横軸はストロークで、ストロークの初期、
荷重の小さい範囲ではバネ特性は線Ａで示される
如く柔かく、路面の小凹突に起因する微振動を効
果的に吸収、減衰し、ストロークの中期、荷重の
ある程度の範囲ではバネ特性はＢで示される如く
振動、衝撃に対し満足させ得る如く中庸なものと
し、ストロークの後期、大荷重の場合にはバネ特
性はＣで示される如くバネ定数が立ち上がり、硬
い特性を得、積載時においてもフルバンプを防止
することができることとなる。このように積載の
有無にかかわらず乗心地性を充分に満足せしめ得
る累進比率の大きいバネ特性を得ることができる
こととなる。 This is shown in the graph of Figure 2. The vertical axis is the load, and the horizontal axis is the stroke.
In the low load range, the spring characteristics are soft as shown by line A, effectively absorbing and attenuating minute vibrations caused by small bumps in the road surface, and in the middle of the stroke and within a certain load range, the spring characteristics are soft as shown by line A. As shown in the figure, the spring characteristics are moderate enough to satisfy vibration and shock, and in the later stages of the stroke and under large loads, the spring constant rises as shown in C, resulting in hard characteristics, and even when loaded, there is no full bump. This means that this can be prevented. In this way, it is possible to obtain spring characteristics with a large progressive ratio that can fully satisfy ride comfort regardless of whether the vehicle is loaded or not.
以上の説明では第２図に示す如く三段にバネ特
性が累進的に変化する例として述べたが、個々の
バネ１１，１２の固有のバネ特性を変化せしめる
ことにより、バネ１１，１２の直列接続、バネ１
２のみの特性、バネ１１，１２の並列接続により
４段、５段、或はそれ以上に累進的にバネ特性を
変化させることができる。 The above explanation has been given as an example in which the spring characteristics change progressively in three stages as shown in FIG. Connection, spring 1
By connecting the springs 11 and 12 in parallel, the spring characteristics can be changed progressively in four, five, or more stages.
以上で明らかな如く本発明によれば、二種の異
径のコイルバネを用いてストロークに応じて各コ
イルバネの直列接続、一方のコイルバネのみの作
用、各コイルバネの並列接続の各特性を得、バネ
特性の累進比率を大きく設定することができ、微
振動から大荷重迄ストローク全領域において満足
すべき乗心地性を確保することができる懸架バネ
装置を得ることができる。 As is clear from the above, according to the present invention, two types of coil springs with different diameters are used to obtain the characteristics of series connection of each coil spring, action of only one coil spring, and parallel connection of each coil spring according to the stroke. It is possible to obtain a suspension spring device that can set a large progressive ratio of characteristics and can ensure satisfactory riding comfort in the entire stroke range from slight vibrations to large loads.
又以上を二種の異径のコイルバネを上記の如く
配設するだけで達成し、構造簡単で且つ装置自体
もコンパクトで、狭いスペースに取り付けること
ができ、スペース上も極めて有利である等実用的
効果頗る顕著である。 In addition, the above can be achieved by simply arranging two types of coil springs with different diameters as described above, and the structure is simple and the device itself is compact, so it can be installed in a narrow space, and is extremely advantageous in terms of space. The effect is remarkable.
図面は本発明の一実施例を示すもので、第１図
は装置の縦断面図、第２図は本発明を説明するグ
ラフである。
尚図中２はダンパ、２ａはシリンダ、３はロツ
ド、８はジヨイント、１１は第１のコイルバネ、
１２は第２のコイルバネである。
The drawings show one embodiment of the present invention, and FIG. 1 is a longitudinal sectional view of the device, and FIG. 2 is a graph explaining the present invention. In the figure, 2 is a damper, 2a is a cylinder, 3 is a rod, 8 is a joint, 11 is a first coil spring,
12 is a second coil spring.
Claims (1)
れたピストン、及び該ピストンに取着されシリン
ダ上方へ延出するピストンロツドとから成るダン
パと、 前記シリンダの外周に設けた第１の固定バネ受
と、 前記ピストンロツドに設けた第２の固定バネ受
と、 前記第１の固定バネ受と前記第２の固定バネ受
との間に設けたコイルバネとから成る車両用懸架
バネ装置に於いて、 前記コイルバネを上端が第２の固定バネ受に当
接する第１のコイルバネと、下端が第１の固定バ
ネ受に当接し、上部に前記第１のコイルバネの下
部が挿通し、且つ第１のコイルバネよりもバネ定
数の高い第２のコイルバネとで構成し、 前記第１のコイルバネの下端と、前記第２のコ
イルバネの上端とをダンパの長手方向に摺動する
摺動ジヨイントで連結し、 前記第２のコイルバネ上端と前記第２の固定バ
ネ受間にダンパの長手方向に摺動自在で、上端が
第２の固定バネ受に当接することにより、或いは
下端が摺動ジヨイント上部に係合することにより
第２のコイルバネの上限を規制する規制部材を設
け、 前記摺動ジヨイントと前記規制部材のダンパ長
手方向の長さを、ダンパの圧縮工程時に前記摺動
ジヨイント下端が第１の固定バネ受に当接した後
に第１のコイルバネと第２のコイルバネとを同時
に圧縮する寸法に設定したことを特徴とする車両
用懸架バネ装置。[Scope of Claims] 1. A damper comprising a cylinder, a piston slidably provided in the cylinder, and a piston rod attached to the piston and extending upward from the cylinder; A vehicle suspension spring device comprising: a first fixed spring receiver; a second fixed spring receiver provided on the piston rod; and a coil spring provided between the first fixed spring receiver and the second fixed spring receiver. The coil spring has a first coil spring whose upper end abuts a second fixed spring receiver, a lower end abuts the first fixed spring receiver, and a lower part of the first coil spring inserted into the upper part, and and a second coil spring having a higher spring constant than the first coil spring, and the lower end of the first coil spring and the upper end of the second coil spring are connected by a sliding joint that slides in the longitudinal direction of the damper. The damper is slidable in the longitudinal direction of the damper between the upper end of the second coil spring and the second fixed spring receiver, and the upper end is in contact with the second fixed spring receiver, or the lower end is in contact with the upper part of the sliding joint. A regulating member is provided that regulates the upper limit of the second coil spring by engagement, and the length of the sliding joint and the regulating member in the longitudinal direction of the damper is set such that the lower end of the sliding joint is in the first position during the compression process of the damper. 1. A suspension spring device for a vehicle, characterized in that the first coil spring and the second coil spring are dimensioned to compress simultaneously after coming into contact with a fixed spring receiver.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16108679A JPS5683633A (en) | 1979-12-12 | 1979-12-12 | Suspension spring device for vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16108679A JPS5683633A (en) | 1979-12-12 | 1979-12-12 | Suspension spring device for vehicle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5683633A JPS5683633A (en) | 1981-07-08 |
| JPS6222018B2 true JPS6222018B2 (en) | 1987-05-15 |
Family
ID=15728342
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16108679A Granted JPS5683633A (en) | 1979-12-12 | 1979-12-12 | Suspension spring device for vehicle |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5683633A (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS593035U (en) * | 1982-06-30 | 1984-01-10 | カヤバ工業株式会社 | Shock absorber spring retainer structure |
| US4828237A (en) * | 1988-03-01 | 1989-05-09 | Trw Inc. | Reduced length MacPherson strut |
| DE4112254A1 (en) * | 1991-04-15 | 1992-10-22 | Stabilus Gmbh | GAS SPRING WITH NON-CONTINUOUS FORCE CHARACTERISTICS |
| US7350774B2 (en) | 2004-09-07 | 2008-04-01 | Danly Iem, Llc | Long travel, high force combination spring |
| US7108111B2 (en) * | 2004-10-25 | 2006-09-19 | Enidine Incorporated | Semi-active isolator |
| DE102007015888A1 (en) * | 2007-04-02 | 2008-10-09 | Bayerische Motoren Werke Aktiengesellschaft | Spring arrangement with adjustable spring rate and strut |
| JP4725748B2 (en) * | 2007-10-15 | 2011-07-13 | 村田機械株式会社 | Parallel link mechanism |
| DE102008004887A1 (en) * | 2008-01-17 | 2009-07-23 | Bayerische Motoren Werke Aktiengesellschaft | Suspension strut with screw pot |
| US10315479B2 (en) | 2013-07-11 | 2019-06-11 | Kpit Technologies Ltd. | Dynamically adjustable suspension device |
| JP7157703B2 (en) * | 2019-06-03 | 2022-10-20 | 本田技研工業株式会社 | Vehicle driving training device |
| JP7323585B2 (en) | 2021-09-29 | 2023-08-08 | 本田技研工業株式会社 | Estimation device, vehicle and estimation method |
-
1979
- 1979-12-12 JP JP16108679A patent/JPS5683633A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5683633A (en) | 1981-07-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6296237B1 (en) | Bump stopper | |
| US3984119A (en) | Suspension for two-wheeled vehicle | |
| US4518154A (en) | Pneumatic spring, especially for motor vehicles | |
| US8037982B2 (en) | Hydraulic shock absorber for vehicle | |
| US5454550A (en) | Dampening shock absorber | |
| US6352145B1 (en) | Stroke dependent damping | |
| US5308104A (en) | Steer-sensitive jounce bumper and bump plate | |
| US4838393A (en) | Hydro-mechanical stop having a restrictive passage | |
| US4798370A (en) | Upper support for a suspension of a vehicle | |
| JPS6222018B2 (en) | ||
| GB2349681A (en) | Stroke dependent bypass | |
| US20030051957A1 (en) | Shock absorber with a floating piston | |
| US5224689A (en) | Shock absorbing device allowing reducing the vehicle weight | |
| US3682462A (en) | Shock absorbers for vehicles | |
| WO2019015604A1 (en) | Dual-spring damper assembly | |
| US10704636B2 (en) | Elastomer spring for vehicle | |
| EP0063016B1 (en) | Suspension assembly for an automotive vehicle | |
| US10131196B2 (en) | Spring-damper assembly | |
| US3447797A (en) | Telescoping,spring-loaded,hydraulically damped shock absorber | |
| US5186439A (en) | Friction compensating automotive suspension strut | |
| EP3517802B1 (en) | Tunable suspension limiters for suspension arrangements | |
| JPH11153171A (en) | Shock absorber structure | |
| US11685212B2 (en) | Hydraulic jounce bumper with improved installation | |
| JPS6128526B2 (en) | ||
| EP0076339A1 (en) | Telescopic shock absorber |