JP3682940B2 - Vehicle height adjustment device - Google Patents

Vehicle height adjustment device Download PDF

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Publication number
JP3682940B2
JP3682940B2 JP17059896A JP17059896A JP3682940B2 JP 3682940 B2 JP3682940 B2 JP 3682940B2 JP 17059896 A JP17059896 A JP 17059896A JP 17059896 A JP17059896 A JP 17059896A JP 3682940 B2 JP3682940 B2 JP 3682940B2
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Prior art keywords
cylinder
vehicle height
spring
pressure
piston
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JPH09328007A (en
Inventor
建 水向
靖彦 原
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KYB Corp
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KYB Corp
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/027—Mechanical springs regulated by fluid means
    • B60G17/0272—Mechanical springs regulated by fluid means the mechanical spring being a coil spring
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/10—Type of spring
    • B60G2202/12—Wound spring
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2300/00—Indexing codes relating to the type of vehicle
    • B60G2300/02—Trucks; Load vehicles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2500/00—Indexing codes relating to the regulated action or device
    • B60G2500/20—Spring action or springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2500/00—Indexing codes relating to the regulated action or device
    • B60G2500/30—Height or ground clearance
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
    • B60G2800/90—System Controller type
    • B60G2800/91—Suspension Control
    • B60G2800/915—Suspension load distribution

Description

【０００１】
【発明の属する技術分野】
この発明は自動車等の車両における車体と車軸間に介装されて車体を懸架しながら車高を調整する車高調整装置に関するものである。
【０００２】
【従来の技術】
例えば、この種の車高調整装置にあっては、車高を検出するセンサ、パワ−ユニット、制御弁、左右の懸架装置、コントロ−ラとから構成されており、懸架装置は、図４に示すように、車体と車軸間に車体を懸架するに当たり、シリンダ４０と懸架ばね４１とからなり、懸架ばね４１は、車軸側に設けたばね座４７とシリンダ４０のフランジ部４０Ａ間に配設される。シリンダ４０にはシ−ル部材４６を介して摺動自在にピストン４３が嵌挿されており、シリンダ室４４を画成している。シリンダ室４４は、ピストン４３に設けた通路４５を介してパワ−ユニットに接続されている。車高を調整する場合、車高センサに基づいてコントロ−ラよりパワ−ユニットを作動して、懸架装置のシリンダ室４４に高圧油を供給、あるいはシリンダ室４４の圧油を排出し、ピストン４３を伸縮して車高を調整するようにしている。
【０００３】
【発明が解決しようとする課題】
ところで、上記車高調整装置における懸架装置にあっては、懸架装置のシリンダで車体にかかる荷重をすべてシリンダで支えなければならず、このため、シリンダ室に供給する油圧は高圧にする必要があり、パワ−ユニットで高圧油を発生させるため、省エネ化という点で大変不利になる。さらに、配管、シ−ル、バルブ、ポンプ等も高圧に耐えるものでなければならず、高価になり、ト−タル的にコストを下げることができない。また、供給圧力を下げるため、シリンダ径を大きくすることが考えられるが、シリンダ径を大きくすると、取り付けスペ−スに制限があって取り付けられなくなり、またシリンダへの油の供給も大容量のパワ−ユニットを用意する必要もあり、さらに、パワ−ユニット、シリンダの重量も増大してしまい、容易にシリンダの径を大きくすることができないという問題があった。
【０００４】
そこで、この発明は、懸架装置におけるシリンダの径を大きくすることなく、シリンダに油圧を供給するパワ−ユニットの供給圧力の低圧化が図れる車高調整装置を提供することである。
【０００５】
【課題を解決するための手段】
上記の目的を達成するため、本発明の手段は、車体と車軸との間に配設されるシリンダとばね部材とを有する懸架装置と、上記シリンダに連通して作動油を給排する制御弁を設けたパワ−ユニットと、パワ−ユニットと制御弁をセンサに基づいて制御する制御手段とを備えて車高を調整するようにした車高調整装置において、前記懸架装置をシリンダと、シリンダ内に摺動自在に嵌挿したピストンと、シリンダの上端部とピストンの外端部にそれぞれに形成したフランジ部と、車軸側に設けたばね座と、上記ピストンのフランジ部と上記ばね座との間に介在した第１のばね部材と、上記第１のばね部材の内側に二重に配設しながら上記シリンダのフランジ部と上記ばね座との間に介在した第２のばね部材とで構成したことを特徴とする。
【０００８】
【発明の実施の形態】
以下、図面に基づいて本発明の実施の形態について説明する。
本発明の一実施の形態に係る車高調整装置は、図１，図２，図３に示すように、車体１と車軸２との間に配設されるシリンダ３０とばね部材とを有する懸架装置４と、上記シリンダ３０に連通して作動油を給排する制御弁を設けたパワ−ユニット３と、パワ−ユニット３と制御弁を車高センサ５に基づいて制御する制御手段たるコントローラ６とを備えて車高を調整するようにするものである。そして、前記懸架装置４をシリンダ３０と、シリンダ３０内に摺動自在に嵌挿したピストン３３と、シリンダ３３の上端部とピストンの外端部にそれぞれに形成したフランジ部３０ A, ３３ A と、車軸２側に設けたばね座３７と、上記ピストン３３のフランジ部３３ A と上記ばね座３７との間に介在したコイルばね３１からなる第１のばね部材と、上記第１のばね部材の内側に二重に配設しながら上記シリンダ３０のフランジ部３０ A と上記ばね座３７との間に介在したコイルばね３２からなる第２のばね部材とで構成している。
以下、さらに詳しく説明する。
この実施の形態に関わるシステムの油圧回路は、図１に示すように、車体１と車軸２間に介装する左右の懸架装置４、パワ−ユニット３、ソレノイドバルブ７、車高センサ５、制御手段であるコントロ−ラ６とで構成されている。
【０００９】
パワ−ユニット３は、モ−タ１１で駆動されるポンプ１２、チェック弁１３、リリ−フ弁１４、プレッシャスイッチ１５、１６、フィルタ１７、タンク１８とが組み込まれて、モ−タ１１は、車高センサ５、プレッシャスイッチ１５、１６に基づいてコントロ−ラ５よりの信号で駆動されるようになっている。
【００１０】
ポンプ１２は、吐出側より分岐回路２１中にフィルタ１７、チェック弁を介してメイン回路２０に接続されている。
【００１１】
リリ−フ弁１４は、メイン回路２０の圧力を一定に保つようにメイン回路２０とタンク１８との間の分岐回路２３中に設けられている。
【００１２】
メイン回路２０中には、回路中の圧力を検出するプレッシャスイッチ１５、１６が設けられ、コントロ−ラ５に接続されている。
【００１３】
ソレノイドバルブ７は、チェック弁を内蔵した２ポ−ト２位置式バルブで、パワ−ユニット３におけるメイン回路２０とタンク１８との分岐回路２２中に設けられ、メイン回路２０とタンク１８とをコントロ−ラ５からの信号によってポ−トａ、ｂを切り換えて連通、遮断するようになっている。
【００１４】
懸架装置４は、車体１と車軸２との間に配設され、車体１を懸架する、図２に示すように、シリンダ３０と第１、第２のコイルばね３１、３２とからなり、シリンダ３０には、ピストン３３がシ−ル部材３６を介して摺動自在に嵌挿されるとともに、シリンダ室３４を画成している。尚、懸架装置４は、車体１と車軸２との間の他に、車軸１と図示しないサスペンションア−ムやリンクとの間にも配設される。
【００１５】
シリンダ室３４は、ピストン３３に穿設した通路３５を介して上記パワ−ユニット３のメイン回路２０に連通されている。
【００１６】
ピストン３３のフランジ部３３Ａと車軸２側に設けたばね座３７との間に第１のコイルばね３１が、シリンダ３０のフランジ部３０Ａと車軸２側に設けたばね座３７との間に上記の第１のコイルばね３１の内側にこれと同芯状（並列）にして二重に配設されながら第２のコイルばね３２が介装してある。
【００１７】
車高をアップする場合、車高センサ５に基づいて、コントロ−ラ６によりモ−タ１１を駆動してポンプ１２を回転させると、リリ−フ弁１４でセットされた圧力でメイン回路２０から通路３５を介してシリンダの室３４に圧油が供給されて、ピストン３３が伸長して車高を上げる。
【００１８】
また、車高をダウンする場合、同じく車高センサ５に基づいて、コントロ−ラ６によりソレノイドバルブ７をａポ−トからｂポ−ト側に作動させて、メイン回路２０をタンク１８に連通させて、シリンダ室３４内の圧力をメイン回路２０を介してタンク１８に逃がしてピストン３３を収縮して車高を下げる。
【００１９】
車高アップの時のメイン回路２０の圧は、プレッシャスイッチ１５で、車高ダウン時のメイン回路の圧は、プレッシャスイッチ１６で検出し、所定圧力になると、それぞれの信号でモ−タ１１とポンプ１２を停止し、車高を一定の高さに調整した後は、チェック弁１３、リリ−フ弁１４、ソレノイドバルブ７（ａポ−トに切り換わる）でメイン回路２０が閉じられ、車高が一定の高さに保持される。
【００２０】
ところで、図３に示す従来の上記懸架装置と図２に示す本実施例の懸架装置において、車体に掛かる荷重ＷがＷ＋Δｗに増大し、車高がΔｘだけ変位した場合に、車高を元の位置に戻すためにシリンダに供給される油圧についてみてみる。
【００２１】
従来の懸架装置にあっては、図５の（ａ）に示すように、作用する荷重Ｗ＋Δｗ、ばね４１のばね定数Ｋ、荷重Ｗの作用時のばねの撓みδ、車高の変位Δｘ、とすると、荷重とばねとの間には次のような関係が成り立ち、
Ｗ＋Δｗ＝Ｋ（δ＋Δｘ）となり、
荷重の増加分は、
Δｗ＝ＫΔｘとなる。
【００２２】
車高を元に戻すには、図５の（ｂ）に示すように、受圧面積Ａなるシリンダに圧力Ｐなる圧力をかけるとすると、荷重とシリンダとの間には次のような関係が成り立ち、

Figure 0003682940
車高を元に戻す圧力Ｐは、
Ｐ＝（Ｗ＋Δｗ）／Ａ となる。
【００２３】
次に、本実施例の懸架装置にあっては、図３の（ａ）に示すように、作用する荷重Ｗ＋Δｗ、ばね３１、３２のばね定数Ｋ1 、Ｋ2 、荷重Ｗの作用時のばね３１、３２のばね撓みδ1 、δ2 、車高の変位Δｘ、とすると、荷重とばねとの間には次のような関係が成り立ち、
Figure 0003682940
荷重の増加分Δｗは、
Δｗ＝（Ｋ1 ＋Ｋ2 ）Δｘ となる。
【００２４】
これより 車高を元に戻すには、図３の（ｂ）に示すように、受圧面積Ａ1 なるシリンダに圧力Ｐ1 なる圧力をかけるとすると、荷重とシリンダ３３に作用する力との間には次のような関係が成り立ち、
Ｗ＋Δｗ＝Ｋ1 （δ1 ＋Δｘ−Δｘ）＋Ｐ1 Ａ1 より
車高を元に戻す圧力Ｐ1 は、
Ｐ1 ＝（Ｗ＋Δｗ−Ｋ1 δ1 ）／Ａ1 となる。
【００２５】
そこで、上記ＰとＰ1 とから、両方の差をとると、
Ｐ−Ｐ1 ＝（Ｗ＋Δｗ）／Ａ−（Ｗ＋Δｗ−Ｋ1 δ1 ）／Ａ1 となり、
ここで、 Ａ＝Ａ1 とすると、
Ｐ−Ｐ1 ＝Ｋ1 δ1 ／Ａ となり、
Ｋ1 、δ1 、Ａ、＞０ であるから、
Ｐ−Ｐ1 ＞０となり、
車体に掛かる荷重ＷがＷ＋Δｗに増大し、車高がΔｘだけ変位した場合に、車高を元の位置に戻すためにシリンダ室３４に供給される油圧は、本実施例の懸架装置における圧力Ｐ1 が従来の上記懸架装置における圧力ＰよりＫ1 δ1 ／Ａだけ圧力が低くなる。
【００２６】
Figure 0003682940
コイルばねの２つのばね定数Ｋ1 、Ｋ2 の和を従来のばね定数Ｋと同じにすれば、従来の乗り心地と同様になって、ばねによる乗り心地の弊害はなくなる。
【００２７】
このように、懸架装置において、車体１と車軸２間にあって車軸２側に設けたばね座３７とピストン３３のフランジ部３３Ａとの間に第１のコイルばね３１と、車軸２側に設けたばね座３７とシリンダ３０のフランジ部３０Ａとの間に第２のコイルばね３２とをそれぞれ介装するようにしたから、車体１に荷重変化があって、車高が変位しても、車体１にかかる荷重の変化量だけが車高を元の位置に戻す調整荷重となるために、シリンダ室３４に供給する油の圧力を従来に比してＫ1 δ1 ／Ａだけ圧力を低くすることができ、従来のようにパワ−ユニットで高圧油を発生させる必要がなくなり、省エネ化という点で大変有利になる。
【００２８】
さらに、圧力を低くできるため、配管、シ−ル、ソレノイドバルブ、ポンプ等も低圧に耐え得るものを使用でき、加工精度も高精度を必要とせず、安価となり、ト−タル的にコストダウンを図ることができる。
【００２９】
また、第１、第２のコイルばね３１、３２を並列二重に配設したので、懸架装置の外形も大きくならず、コンパクトになる。
【００３０】
さらに、コイルばねの２つのばね定数Ｋ1 、Ｋ2 の和を従来のばね定数Ｋと同じにしたので、従来と同様の乗り心地にすることができる。
【００３１】
【発明の効果】
第１の発明によれば、懸架装置において、車軸と車体間にあって車軸側に設けたばね座とピストンのフランジ部との間に第１のばね部材と、車軸側に設けたばね座とシリンダのフランジ部との間に第２のばね部材とをそれぞれ介装するようにしたので、車体に荷重変化があって、車高が変位しても、車体にかかる荷重の変化量だけが車高を元の位置に戻す調整荷重となるために、シリンダに供給する油の圧力を従来の単一のみのコイルばねを使用したものに比べて、Ｋ1 δ1 ／Ａ（第１のばね部材のばね定数 K1, 同じく荷重作用時の撓みをδ 1 、ピストンの重圧面積を A）だけ圧力が低くすることができ、従来のようにパワ−ユニットで高圧油を発生させる必要がなくなり、省エネ化という点で大変有利になる。さらに、配管、シ−ル、切換バルブ、ポンプ等も低圧に耐え得るものを使用でき、加工精度も高精度を必要とせず、安価となり、ト−タル的にコストダウンを図ることができる。
更に、第１、第２のばね部材を二重に配設したので、懸架装置の外形は大きくならず、コンパクトにすることができる。
【図面の簡単な説明】
【図１】この発明の実施の形態を示す車高調整装置の構成図である。
【図２】同じく第１図の車高調整装置に使用するシリンダの拡大断面図である。
【図３】同じくシリンダの作用を説明する説明図である。
【図４】従来のシリンダの拡大断面図である。
【図５】同じくシリンダの作用を説明する説明図である。
【符号の説明】
１ 車体
２ 車軸
３ パワ−ユニット
４ 懸架装置
５ 車高センサ
６ コントロ−ラ
７ ソレノイドバルブ
１１ モ−タ
１２ ポンプ
１３ チェック弁
１４ リリ−フ弁
１５、１６ プレッシャスイッチ
１７ フィルタ
１８ タンク
２０ メイン回路
２１、２２、２３ 分岐回路
３０ シリンダ
３０Ａ フランジ部
３１ 第１のコイルばね
３２ 第２のコイルばね
３３ ピストン
３３Ａ フランジ部
３４ シリンダ室
３５ 通路
３６ シ−ル
３７ ばね座
４０ シリンダ
４０Ａ フランジ
４１ コイルばね
４３ ピストン
４４ シリンダ室
４５ 通路
４６ シ−ル
４７ ばね座
Ｗ 荷重
Δｗ 荷重の増加分
Δｘ 車高の変位
Ｋ、Ｋ1 、Ｋ2 ばね定数
δ、δ1 、δ2 ばねの撓み
Ｐ、Ｐ1 圧力
Ａ、Ａ1 受圧面積[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a vehicle height adjusting device that is interposed between a vehicle body and an axle of a vehicle such as an automobile and adjusts the vehicle height while suspending the vehicle body.
[0002]
[Prior art]
For example, this type of vehicle height adjusting device includes a sensor for detecting vehicle height, a power unit, a control valve, left and right suspension devices, and a controller. As shown, when the vehicle body is suspended between the vehicle body and the axle, the cylinder 40 and the suspension spring 41 are comprised, and the suspension spring 41 is disposed between the spring seat 47 provided on the axle side and the flange portion 40A of the cylinder 40. . A piston 43 is slidably inserted into the cylinder 40 via a seal member 46 to define a cylinder chamber 44. The cylinder chamber 44 is connected to the power unit via a passage 45 provided in the piston 43. When adjusting the vehicle height, the power unit is operated from the controller based on the vehicle height sensor, high pressure oil is supplied to the cylinder chamber 44 of the suspension device, or the pressure oil in the cylinder chamber 44 is discharged, and the piston 43 The vehicle height is adjusted by expanding and contracting.
[0003]
[Problems to be solved by the invention]
By the way, in the suspension device in the vehicle height adjusting device, all the load applied to the vehicle body must be supported by the cylinder by the cylinder of the suspension device. For this reason, the hydraulic pressure supplied to the cylinder chamber needs to be high. Because the power unit generates high-pressure oil, it is very disadvantageous in terms of energy saving. Furthermore, piping, seals, valves, pumps, etc. must be able to withstand high pressures, which makes them expensive and cannot reduce costs in a total way. In order to reduce the supply pressure, it is conceivable to increase the cylinder diameter. However, if the cylinder diameter is increased, there is a limit to the installation space and the cylinder cannot be installed. -It is necessary to prepare a unit, and furthermore, the weight of the power unit and the cylinder increases, and there is a problem that the diameter of the cylinder cannot be easily increased.
[0004]
SUMMARY OF THE INVENTION Accordingly, the present invention provides a vehicle height adjusting device that can reduce the supply pressure of a power unit that supplies hydraulic pressure to a cylinder without increasing the diameter of the cylinder in the suspension device.
[0005]
[Means for Solving the Problems]
In order to achieve the above object, the means of the present invention includes a suspension device having a cylinder and a spring member disposed between a vehicle body and an axle, and a control valve for supplying and discharging hydraulic oil in communication with the cylinder. And a control unit for controlling the power unit and the control valve based on a sensor to adjust the vehicle height, wherein the suspension device is a cylinder, A piston that is slidably inserted into the cylinder, a flange formed on each of the upper end of the cylinder and the outer end of the piston, a spring seat provided on the axle side, and a flange between the piston and the spring seat. The first spring member interposed between the first spring member and the second spring member interposed between the flange portion of the cylinder and the spring seat while being double disposed inside the first spring member. It is characterized by that.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
As shown in FIGS. 1, 2, and 3, a vehicle height adjusting device according to an embodiment of the present invention is a suspension having a cylinder 30 and a spring member disposed between a vehicle body 1 and an axle 2. A power unit 3 provided with a control valve that communicates with the cylinder 4 and supplies and discharges hydraulic oil; and a controller 6 that is a control means for controlling the power unit 3 and the control valve based on a vehicle height sensor 5. In order to adjust the vehicle height. Then, with the suspension device 4 of the cylinder 30, a piston 33 fitted slidably into the cylinder 30, and the flange portion 30 A, 33 A formed on the respective outer ends of the upper portion and the piston of the cylinder 33 A first spring member comprising a spring seat 37 provided on the axle 2 side, a coil spring 31 interposed between the flange 33A of the piston 33 and the spring seat 37, and an inner side of the first spring member It is constituted by a second spring member made of a coil spring 32 interposed between the flange portion 30 a and the spring seat 37 of the cylinder 30 while disposed in duplicate.
This will be described in more detail below.
As shown in FIG. 1, the hydraulic circuit of the system according to this embodiment includes a left and right suspension device 4 interposed between a vehicle body 1 and an axle 2, a power unit 3, a solenoid valve 7, a vehicle height sensor 5, and a control. It is comprised with the controller 6 which is a means.
[0009]
The power unit 3 includes a pump 12 driven by a motor 11, a check valve 13, a relief valve 14, pressure switches 15 and 16, a filter 17, and a tank 18. The vehicle is driven by a signal from the controller 5 based on the vehicle height sensor 5 and the pressure switches 15 and 16.
[0010]
The pump 12 is connected to the main circuit 20 through the filter 17 and the check valve in the branch circuit 21 from the discharge side.
[0011]
The relief valve 14 is provided in the branch circuit 23 between the main circuit 20 and the tank 18 so as to keep the pressure of the main circuit 20 constant.
[0012]
In the main circuit 20, pressure switches 15 and 16 for detecting the pressure in the circuit are provided and connected to the controller 5.
[0013]
The solenoid valve 7 is a two-port two-position valve with a built-in check valve, and is provided in the branch circuit 22 between the main circuit 20 and the tank 18 in the power unit 3, and the main circuit 20 and the tank 18 are controlled. -The ports a and b are switched by the signal from the line 5 to communicate and block.
[0014]
As shown in FIG. 2, the suspension device 4 is disposed between the vehicle body 1 and the axle 2 and suspends the vehicle body 1. The suspension device 4 includes a cylinder 30 and first and second coil springs 31 and 32. A piston 33 is slidably inserted into the cylinder 30 through a seal member 36, and a cylinder chamber 34 is defined. The suspension device 4 is disposed not only between the vehicle body 1 and the axle 2 but also between the axle 1 and a suspension arm or link (not shown).
[0015]
The cylinder chamber 34 communicates with the main circuit 20 of the power unit 3 through a passage 35 formed in the piston 33.
[0016]
The first coil spring 31 is provided between the flange portion 33A of the piston 33 and the spring seat 37 provided on the axle 2 side, and the first coil spring 31 is provided between the flange portion 30A of the cylinder 30 and the spring seat 37 provided on the axle 2 side . A second coil spring 32 is interposed inside the coil spring 31 while being double-arranged concentrically (in parallel) with the coil spring 31 .
[0017]
When the vehicle height is increased, when the motor 12 is driven by the controller 6 based on the vehicle height sensor 5 and the pump 12 is rotated, the pressure set by the relief valve 14 is applied from the main circuit 20. Pressure oil is supplied to the cylinder chamber 34 via the passage 35, and the piston 33 extends to raise the vehicle height.
[0018]
When the vehicle height is to be lowered, the solenoid valve 7 is operated from the a port to the b port side by the controller 6 based on the vehicle height sensor 5, so that the main circuit 20 communicates with the tank 18. Then, the pressure in the cylinder chamber 34 is released to the tank 18 through the main circuit 20 and the piston 33 is contracted to lower the vehicle height.
[0019]
The pressure of the main circuit 20 when the vehicle height is increased is detected by the pressure switch 15, and the pressure of the main circuit when the vehicle height is lowered is detected by the pressure switch 16. After the pump 12 is stopped and the vehicle height is adjusted to a certain height, the main circuit 20 is closed by the check valve 13, the relief valve 14, and the solenoid valve 7 (switching to a port), and the vehicle The height is kept constant.
[0020]
By the way, in the conventional suspension apparatus shown in FIG. 3 and the suspension apparatus of the present embodiment shown in FIG. 2, when the load W applied to the vehicle body increases to W + Δw and the vehicle height is displaced by Δx, Let's look at the hydraulic pressure supplied to the cylinder to return it to the position.
[0021]
In the conventional suspension system, as shown in FIG. 5A, the applied load W + Δw, the spring constant K of the spring 41, the spring deflection δ when the load W is applied, the vehicle height displacement Δx, Then, the following relationship is established between the load and the spring:
W + Δw = K (δ + Δx)
The increase in load is
Δw = KΔx.
[0022]
In order to restore the vehicle height, as shown in FIG. 5B, if a pressure P is applied to a cylinder having a pressure receiving area A, the following relationship is established between the load and the cylinder. ,
Figure 0003682940
The pressure P that returns the vehicle height is
P = (W + Δw) / A
[0023]
Next, in the suspension device of the present embodiment, as shown in FIG. 3A, the acting load W + Δw, the spring constants K1, K2 of the springs 31, 32, the spring 31 when the load W is applied, 32 spring deflections δ1 and δ2 and vehicle height displacement Δx, the following relationship holds between the load and the spring:
Figure 0003682940
The increase Δw in load is
Δw = (K1 + K2) Δx
[0024]
In order to return the vehicle height to the original value, as shown in FIG. 3 (b), when a pressure P1 is applied to the cylinder having the pressure receiving area A1, the load and the force acting on the cylinder 33 are not increased. The following relationship holds:
W + Δw = K1 (δ1 + Δx−Δx) + P1 A pressure P1 for returning the vehicle height from A1 is:
P1 = (W + .DELTA.w-K1.delta.1) / A1.
[0025]
Therefore, taking the difference between P and P1,
P−P1 = (W + Δw) / A− (W + Δw−K1 δ1) / A1
Here, if A = A1,
P−P1 = K1 δ1 / A
Since K1, δ1, A,> 0,
P−P1> 0,
When the load W applied to the vehicle body increases to W + Δw and the vehicle height is displaced by Δx, the hydraulic pressure supplied to the cylinder chamber 34 to return the vehicle height to the original position is the pressure P1 in the suspension device of this embodiment. However, the pressure is lower than the pressure P in the conventional suspension device by K1 δ1 / A.
[0026]
Figure 0003682940
If the sum of the two spring constants K1 and K2 of the coil spring is made the same as the conventional spring constant K, it becomes the same as the conventional riding comfort, and the adverse effect of the riding comfort by the spring is eliminated.
[0027]
Thus, in the suspension device, the first coil spring 31 and the spring seat 37 provided on the axle 2 side between the spring seat 37 provided on the axle 2 side between the vehicle body 1 and the axle 2 and the flange portion 33A of the piston 33 are provided. Since the second coil spring 32 is interposed between the cylinder 30 and the flange portion 30A of the cylinder 30, the load applied to the vehicle body 1 even if the vehicle body 1 has a load change and the vehicle height is displaced. Therefore, the pressure of the oil supplied to the cylinder chamber 34 can be lowered by K1 δ1 / A as compared with the prior art because only the amount of change becomes the adjustment load for returning the vehicle height to the original position. Thus, there is no need to generate high-pressure oil in the power unit, which is very advantageous in terms of energy saving.
[0028]
Furthermore, since the pressure can be lowered, pipes, seals, solenoid valves, pumps, etc. that can withstand low pressure can be used, machining accuracy is not required, high cost is reduced, and total costs are reduced. Can be planned.
[0029]
In addition, since the first and second coil springs 31 and 32 are arranged in parallel and double, the external shape of the suspension device does not increase, and it becomes compact.
[0030]
Further, since the sum of the two spring constants K1 and K2 of the coil spring is made the same as the conventional spring constant K, it is possible to achieve a riding comfort similar to the conventional one.
[0031]
【The invention's effect】
According to the first invention, in the suspension device, the first spring member , the spring seat provided on the axle side and the flange portion of the cylinder between the spring seat provided on the axle side between the axle and the vehicle body and the flange portion of the piston. Since the second spring member is interposed between the vehicle body and the vehicle body, if there is a change in the load and the vehicle height is displaced, only the amount of change in the load applied to the vehicle body Since the adjustment load is returned to the position, the oil pressure supplied to the cylinder is K1 δ1 / A (same as the first spring member's spring constant K1, as compared to the conventional one using a single coil spring) The pressure can be lowered by δ 1 when the load is applied and the pressure area of the piston is A ), which eliminates the need to generate high-pressure oil in the power unit as in the past, which is very advantageous in terms of energy saving. Become. Further, pipes, seals, switching valves, pumps, and the like that can withstand low pressure can be used, the machining accuracy does not require high accuracy, the cost is reduced, and the total cost can be reduced.
Furthermore, since the first and second spring members are arranged in a double manner, the external shape of the suspension device is not increased, and it can be made compact.
[Brief description of the drawings]
FIG. 1 is a configuration diagram of a vehicle height adjusting device showing an embodiment of the present invention;
FIG. 2 is an enlarged cross-sectional view of a cylinder used in the vehicle height adjusting device of FIG. 1;
FIG. 3 is an explanatory view for explaining the operation of the cylinder.
FIG. 4 is an enlarged sectional view of a conventional cylinder.
FIG. 5 is an explanatory view for explaining the operation of the cylinder.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Car body 2 Axle 3 Power unit 4 Suspension device 5 Vehicle height sensor 6 Controller 7 Solenoid valve 11 Motor 12 Pump 13 Check valve 14 Relief valve 15, 16 Pressure switch 17 Filter 18 Tank 20 Main circuit 21, 22, 23 Branch circuit 30 Cylinder 30A Flange portion 31 First coil spring 32 Second coil spring 33 Piston 33A Flange portion 34 Cylinder chamber 35 Passage 36 Seal 37 Spring seat 40 Cylinder 40A Flange 41 Coil spring 43 Piston 44 Cylinder Chamber 45 Passage 46 Seal 47 Spring seat W Load Δw Load increase Δx Vehicle height displacement K, K1, K2 Spring constants δ, δ1, δ2 Spring deflection P, P1 Pressure A, A1 Pressure receiving area

Claims (1)

車体と車軸との間に配設されるシリンダとばね部材とを有する懸架装置と、上記シリンダに連通して作動油を給排する制御弁を設けたパワ−ユニットと、パワ−ユニットと制御弁をセンサに基づいて制御する制御手段とを備えて車高を調整するようにした車高調整装置において、前記懸架装置をシリンダと、シリンダ内に摺動自在に嵌挿したピストンと、シリンダの上端部とピストンの外端部にそれぞれに形成したフランジ部と、車軸側に設けたばね座と、上記ピストンのフランジ部と上記ばね座との間に介在した第１のばね部材と、上記第１のばね部材の内側に二重に配設しながら上記シリンダのフランジ部と上記ばね座との間に介在した第２のばね部材とで構成したことを特徴とする車高調整装置。 A suspension device having a cylinder and a spring member disposed between a vehicle body and an axle, a power unit provided with a control valve that communicates with the cylinder and supplies and discharges hydraulic oil, a power unit, and a control valve A vehicle height adjusting device including a control means for controlling the vehicle height based on a sensor, wherein the suspension device includes a cylinder, a piston slidably fitted in the cylinder, and an upper end of the cylinder. A flange portion formed on each of the outer end portion and the outer end portion of the piston, a spring seat provided on the axle side, a first spring member interposed between the flange portion of the piston and the spring seat, and the first A vehicle height adjusting device comprising a second spring member interposed between the flange portion of the cylinder and the spring seat while being double disposed inside the spring member .
JP17059896A 1996-06-10 1996-06-10 Vehicle height adjustment device Expired - Fee Related JP3682940B2 (en)

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Application Number Priority Date Filing Date Title
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Application Number Priority Date Filing Date Title
JP17059896A JP3682940B2 (en) 1996-06-10 1996-06-10 Vehicle height adjustment device

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JP3682940B2 true JP3682940B2 (en) 2005-08-17

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Publication number Priority date Publication date Assignee Title
JP4025082B2 (en) * 2002-01-31 2007-12-19 ヤンマー農機株式会社 Suspension mechanism of riding rice transplanter
JP2004199728A (en) * 2002-12-16 2004-07-15 Mitsumi Electric Co Ltd Disk device
DE102007015888A1 (en) * 2007-04-02 2008-10-09 Bayerische Motoren Werke Aktiengesellschaft Spring arrangement with adjustable spring rate and strut
FR3061087B1 (en) * 2016-12-28 2019-08-09 Renault S.A.S HYDRAULIC FLOAT CONTROL DEVICE FOR MOTOR VEHICLE AND SUSPENSION AND DAMPING SYSTEM COMPRISING SUCH A DEVICE
CN108656887B (en) * 2018-07-18 2020-10-16 河南职业技术学院 Automobile chassis with suspension system

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