JPH0151362B2 - - Google Patents
Info
- Publication number
- JPH0151362B2 JPH0151362B2 JP10241078A JP10241078A JPH0151362B2 JP H0151362 B2 JPH0151362 B2 JP H0151362B2 JP 10241078 A JP10241078 A JP 10241078A JP 10241078 A JP10241078 A JP 10241078A JP H0151362 B2 JPH0151362 B2 JP H0151362B2
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- hydraulic
- piston
- spring
- vehicle body
- 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
- 239000002131 composite material Substances 0.000 claims description 4
- 230000003068 static effect Effects 0.000 claims description 2
- 238000005192 partition Methods 0.000 claims 1
- 230000000694 effects Effects 0.000 description 6
- 239000004020 conductor Substances 0.000 description 4
- 230000035939 shock Effects 0.000 description 4
- 238000013016 damping Methods 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 239000000725 suspension Substances 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 2
- 230000010354 integration Effects 0.000 description 2
- 210000002445 nipple Anatomy 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 210000005069 ears Anatomy 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 230000000116 mitigating effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
-
- 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
- B60G17/015—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 the regulating means comprising electric or electronic elements
- B60G17/0152—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 the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit
-
- 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
- B60G2202/30—Spring/Damper and/or actuator Units
- B60G2202/32—The spring being in series with the damper and/or actuator
- B60G2202/322—The spring being in series with the damper and/or actuator the damper being controllable
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2600/00—Indexing codes relating to particular elements, systems or processes used on suspension systems or suspension control systems
- B60G2600/18—Automatic control means
- B60G2600/182—Active control means
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Vehicle Body Suspensions (AREA)
- Fluid-Damping Devices (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、静荷重を支持する油圧−空気圧ばね
と、これと無関係に動作する油圧減衰器とが、車
体と車輪との間に並列に設けられ、油圧減衰器が
車体に対する車輪の位置および運動を特徴づける
量に関係して制御可能であり、油圧−空気圧ばね
と油圧減衰器の油圧部分がそれぞれピストン−シ
リンダ装置により形成されている。自動車用複合
ばね−減衰装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention is characterized in that a hydraulic-pneumatic spring supporting a static load and a hydraulic damper operating independently of the spring are arranged in parallel between the vehicle body and the wheels. A hydraulic damper is provided and is controllable in relation to variables characterizing the position and movement of the wheel relative to the vehicle body, the hydraulic-pneumatic spring and the hydraulic part of the hydraulic damper being each formed by a piston-cylinder arrangement. This invention relates to a composite spring-damping device for automobiles.
金属ばねの代りに油圧−空気圧ばねを自動車の
車体懸架に用いることは公知であり（特開昭51−
7612号公報）、空気ばねのばね定数が小さいため
ばね効果を軟らかくでき、したがつて乗り心地を
改善できるという利点がある。その際油圧ポンプ
により油圧部分の油の量を変えて車高調節も合わ
せて行なうことができる。
It is well known that hydraulic-pneumatic springs are used in place of metal springs for suspension of automobile bodies (Japanese Patent Application Laid-open No. 1983-1999).
7612), since the spring constant of the air spring is small, the spring effect can be softened, which has the advantage of improving riding comfort. At that time, the vehicle height can also be adjusted by changing the amount of oil in the hydraulic parts using a hydraulic pump.
油圧シリンダ内のピストンに絞りを設け、この
絞りを通してピストンの一方の側のシリンダ空気
にある油を他方の側へ押しやることにより、振動
を減衰させたり衝撃を緩和させる油圧減衰器も公
知であり、絞りの代りに、車体に対する車輪の位
置または運動に応動する切換え弁を介して両シリ
ンダ空間を油圧ポンプまたは油タンクに選択的に
接続することもできる。この場合車体に対する車
輪の位置および運動を特徴づける量として、車体
と車輪との相互間隔またはこの相互間隔の変化速
度が用いられる。これにより車輪の充分な動荷重
すなわち車輪と地面との間の力の変動に関して充
分な走行安全性が保証される。 Hydraulic dampers are also known in which vibrations are damped or shocks are alleviated by providing a restriction on a piston in a hydraulic cylinder and forcing oil present in the cylinder air on one side of the piston to the other side through this restriction. Instead of a throttle, it is also possible to selectively connect the two cylinder spaces to a hydraulic pump or an oil tank via switching valves that are responsive to the position or movement of the wheels relative to the vehicle body. In this case, the mutual distance between the vehicle body and the wheels or the rate of change of this mutual distance is used as the quantity characterizing the position and movement of the wheels relative to the vehicle body. This ensures sufficient driving safety with respect to sufficient dynamic loads on the wheels, ie force fluctuations between the wheels and the ground.
しかしながら軟らかいばね効果をもつ油圧−空
気圧ばねによる乗り心地の改善は、油圧減衰器に
より得られる走行安定性を悪化し、逆に走行安定
性の改善は乗り心地を悪くする。 However, the improvement in riding comfort achieved by a hydro-pneumatic spring with a soft spring effect deteriorates the running stability achieved by a hydraulic damper, and conversely, the improvement in running stability worsens the riding comfort.
これらの矛盾する２つの要求を満たすため、油
圧−空気圧ばねと、これと無関係に動作する油圧
減衰器とを、車体と車輪との間に並列に設けるこ
とができるが、これらを限られた空間に組込むこ
とは困難である。 To meet these two contradictory requirements, a hydraulic-pneumatic spring and an independently operating hydraulic damper can be installed in parallel between the vehicle body and the wheels, but these can be installed in a limited space. It is difficult to incorporate into
本発明の課題は、１つの構造単位として車体と
車輪との間の限られた空間へ組込むのに適した自
動車用複合ばね−減衰器装置を提供することであ
る。
SUMMARY OF THE INVENTION The object of the invention is to provide a composite spring-dampener arrangement for a motor vehicle which is suitable for integration as a single structural unit into the confined space between the vehicle body and the wheels.
〔課題を解決するための手段〕
この課題を解決するため本発明によれば、油圧
減衰器用ピストン−シリンダ装置のシリンダが車
体および車輪の一方に連結され、このシリンダ内
に軸線方向移動可能にはまつてこのシリンダ内を
２つのシリンダ４空間に区画するピストンが、ピ
ストン棒を介して車体および車輪の他方に連結さ
れ、両シリンダ空間が、車体に対する車輪の位置
および運動を特徴づける電気量に関係して切換え
動作する電磁切換え弁を介して圧油の給排を制御
され、油圧−空気圧ばね用ピストン−シリンダ装
置のシリンダが、車体および車輪の他方に連結さ
れ、かつ油圧減衰器ピストン−シリンダ装置のシ
リンダの一部を同心的に包囲して、油圧減衰器ピ
ストン−シリンダ装置のシリンダに設けられるピ
ストンとしての環状フランジと共に環状シリンダ
空間を区画し、この環状シリンダ空間が油圧−空
気圧蓄圧槽の油圧空間に接続されている。[Means for Solving the Problem] In order to solve this problem, according to the present invention, a cylinder of a piston-cylinder device for a hydraulic damper is connected to one of the vehicle body and a wheel, and a cylinder capable of axial movement in the cylinder is connected to one of the vehicle body and the wheel. A piston that divides the inside of this cylinder into two cylinder spaces is connected via a piston rod to the vehicle body and the other of the wheels, and both cylinder spaces are related to electrical quantities that characterize the position and motion of the wheels relative to the vehicle body. The supply and discharge of pressure oil is controlled through an electromagnetic switching valve that switches and operates, and the cylinder of the hydraulic-pneumatic spring piston-cylinder device is connected to the other of the vehicle body and the wheel, and the hydraulic damper piston-cylinder device Concentrically surrounds a part of the cylinder of the hydraulic damper and defines an annular cylinder space together with an annular flange serving as a piston provided in the cylinder of the hydraulic damper piston-cylinder device, and this annular cylinder space is configured to absorb the hydraulic pressure of the hydraulic-pneumatic pressure storage tank. connected to space.
こうして本発明によれば、油圧−空気圧ばねと
油圧減衰器とが１つの構造単位にまとめられ、簡
単に車体と車輪との間に取付けることができる。
しかも油圧減衰器のシリンダとばねシリンダが同
心的に重なつているので、装置全体の全長を従来
のものより短くすることができる。しかも本発明
による複合装置により乗り心地と走行安定性とを
両立させることができる。
According to the invention, the hydraulic-pneumatic spring and the hydraulic damper are thus combined into one structural unit that can be easily installed between the vehicle body and the wheels.
Moreover, since the cylinder of the hydraulic damper and the spring cylinder overlap concentrically, the overall length of the entire device can be made shorter than that of conventional devices. Furthermore, the composite device according to the present invention can provide both ride comfort and running stability.
金属ばねの代りに油圧−空気圧ばねを自動車の
車体懸架に用いることは公知であり、空気ばねの
ばね定数が小さいためばね効果を軟らかくできる
という利点がある。その際油圧ポンプにより油圧
部分の油の量を変えて車高調節も合わせて行なう
ことができる。一方油圧シリンダ内のピストンに
絞りを設け、この絞りを通してピストンの一方の
側のシリンダ空間にある油を他方の側へ押しやる
ことにより、振動を減衰させたり衝撃を緩和させ
る油圧減衰器も公知であり、絞りの代りに、切換
え弁を介して両シリンダ空間を油圧ポンプまたは
油タンクに選択的に接続することもできる。
It is known to use hydraulic-pneumatic springs instead of metal springs for the suspension of automobile bodies, which has the advantage of softening the spring effect due to the small spring constant of air springs. At that time, the vehicle height can also be adjusted by changing the amount of oil in the hydraulic parts using a hydraulic pump. On the other hand, a hydraulic damper is also known in which a piston in a hydraulic cylinder is provided with a restriction, and the oil in the cylinder space on one side of the piston is pushed to the other side through this restriction, thereby damping vibrations and mitigating shocks. Instead of a throttle, it is also possible to selectively connect both cylinder spaces to a hydraulic pump or an oil tank via a switching valve.
このようなばね−減衰器装置は米国特許第
3417985号明細書から公知であり、車体に対する
車輪の位置および運動を特徴づける量として、車
体と車輪との相互間隔、この相互間隔の変化速度
または減衰器シリンダの両シリンダ空間の圧力差
が用いられ、これらの量に関係して減衰器ピスト
ン−シリンダ装置のシリンダへの圧油の給排を制
御する。これにより道路の障害物を介して励振さ
せるため生ずる垂直加速度に関して充分な乗り心
地が得られ、また車輪の充分な動荷重すなわち車
輪と地面との間の力の変動に関して充分な走行安
全性が保証される。 Such a spring-attenuator device is described in U.S. Pat.
3417985, in which the mutual spacing between vehicle body and wheels, the rate of change of this mutual spacing, or the pressure difference between the two cylinder spaces of a damper cylinder are used as variables characterizing the position and movement of the wheels relative to the vehicle body. , which control the supply and discharge of pressurized oil to and from the cylinders of the damper piston-cylinder arrangement in relation to these quantities. This provides sufficient ride comfort with respect to the vertical accelerations that occur due to the excitation through road obstacles, and also ensures sufficient driving safety with regard to sufficient dynamic loads on the wheels, i.e. the fluctuations of the forces between the wheels and the ground. be done.
しかしながらこの構成では、ばねシリンダは長
手方向において減衰器シリンダ−ピストン装置に
続いているので、ばね−減衰器装置の全長が比較
的大きくなり、また減衰器シリンダが一部ばねシ
リンダへ入り込んでいるので、ばねシリンダの容
積が小さくなるという欠点がある。 However, in this configuration, the spring cylinder follows the damper cylinder-piston arrangement in the longitudinal direction, so that the overall length of the spring-damper arrangement is relatively large, and also because the damper cylinder partially extends into the spring cylinder. , the disadvantage is that the volume of the spring cylinder is reduced.
本発明の課題は、車体と車輪との間へ組込むの
に適した小さい全長をもち、しかも減衰器シリン
ダの容積も充分確保される、最初にあげた種類の
自動車用ばね−減衰器装置を提供することであ
る。
It is an object of the invention to provide a spring-dampener device for a motor vehicle of the first type, which has a small overall length suitable for integration between the vehicle body and the wheels, and which also has a sufficient volume for the damper cylinder. It is to be.
この課題を解決するため本発明によれば、減衰
器シリンダとばねシリンダとが互いに同心的に重
なり合い、この互いに重なり合う範囲により環状
空間が区画され、減衰器シリンダに設けられる環
状フランジが、環状空間の開放端部を閉鎖して、
ばねピストン−シリンダ装置のピストンを形成し
ている。
In order to solve this problem, according to the present invention, a damper cylinder and a spring cylinder concentrically overlap each other, an annular space is defined by the mutually overlapping range, and an annular flange provided on the damper cylinder is arranged in the annular space. Close the open end and
The spring forms the piston of the piston-cylinder arrangement.
こうして本発明によれば、減衰器シリンダとば
ねシリンダが同心的に重なり合うように配置され
ているので、ばね−減衰器装置の全長を従来のも
のより短くすることができる。またこの重なり範
囲が環状空間すなわちばねシリンダ空間として用
いられ、減衰器シリンダに環状フランジが設けら
れて、ばねピストン−シリンダ装置のピストンと
して、環状空間の開放端部を閉鎖するようになつ
ているので、減衰器シリンダの容積がばねシリン
ダにより小さくされることもなく、さらに環状フ
ランジの位置を減衰器シリンダの所望の長手方向
位置に選んで、装置の全長に影響を及ぼすことな
く、ばねシリンダの容積を所望の大きさに設定す
ることもできる。
Thus, according to the invention, since the damper cylinder and the spring cylinder are arranged concentrically and overlapping, the overall length of the spring-damper arrangement can be made shorter than in the prior art. This overlapping area is also used as an annular space, that is, a spring cylinder space, and the damper cylinder is provided with an annular flange in order to close off the open end of the annular space as a piston of a spring piston-cylinder arrangement. , the volume of the damper cylinder is not reduced by the spring cylinder, and by choosing the position of the annular flange at the desired longitudinal position of the damper cylinder, the volume of the spring cylinder is reduced without affecting the overall length of the device. can also be set to a desired size.
第１図には、本発明による自動車用ばね−減衰
器装置１が、緩衝支柱のような形で示されてい
る。減衰器シリンダ４内には、減衰器ピストン５
が長手方向に称動可能に設けられて、減衰器ピス
トン−シリンダ装置を構成している。減衰器ピス
トン５は減衰器シリンダ４の内部を、２つの空間
すなわち減衰器ピストン５より上にあるシリンダ
空間６と減衰器ピストン５より下にあるシリンダ
空間７とに分割している。減衰器シリンダ４の外
周には、環状フランジ８が設けられ、減衰器シリ
ンダ４の一部を同心的に包囲するばねシリンダ９
内に移動可能にはまつて、ばねピストンとして、
両シリンダ４，９の間に形成される環状空間１１
の開放端部を閉鎖し、ばねシリンダ９と共にばね
ピストン−シリンダ装置を構成している。減衰器
ピストン５のピストン棒１２は、減衰器シリンダ
４の底１３を油密に貫通して、ばねシリンダ９の
底１４に取付られている。底１４の下にある耳片
１５は、ばね−減衰器装置１を自動車用の横置き
懸架腕に取付けるのに役立つ。また減衰器シリン
ダ４の上端１６に溶接されるボルト１７は、ゴム
−金属結合体からなる付加的なばね減衰器素子１
８を貫通して、自動車の車体の部分２１ヘナツト
１９によりねじ止めされている。
In FIG. 1, a spring-dampener device 1 for a motor vehicle according to the invention is shown in the form of a shock strut. Inside the damper cylinder 4 is a damper piston 5.
are longitudinally movable and form a damper piston-cylinder arrangement. The damper piston 5 divides the interior of the damper cylinder 4 into two spaces: a cylinder space 6 above the damper piston 5 and a cylinder space 7 below the damper piston 5 . An annular flange 8 is provided on the outer periphery of the damper cylinder 4, and a spring cylinder 9 concentrically surrounds a part of the damper cylinder 4.
As a spring piston, it is movable within the
An annular space 11 formed between both cylinders 4 and 9
is closed at its open end and together with the spring cylinder 9 forms a spring piston-cylinder arrangement. The piston rod 12 of the damper piston 5 passes through the bottom 13 of the damper cylinder 4 in an oil-tight manner and is attached to the bottom 14 of the spring cylinder 9. The ears 15 under the bottom 14 serve to attach the spring-dampener device 1 to a transverse suspension arm for a motor vehicle. The bolt 17 welded to the upper end 16 of the damper cylinder 4 also includes an additional spring damper element 1 made of a rubber-metal combination.
8 and is screwed to the vehicle body part 21 by a nut 19.
減衰器シリンダ４の両シリンダ空間６および７
は、接続ニツプル２２および２３と導管２４およ
び２５とを介して、第２図に示すように、４ポー
ト３位置電磁切換え弁２を介して、油圧ポンプ３
４または油タンク３５へ選択的に接続可能で、油
圧減衰器を構成している。この切換え弁２を介し
て、両シリンダ空間６，７への圧油の給排を制御
することにより、振動を減衰させたり、衝撃を緩
和することができる。 Both cylinder spaces 6 and 7 of the damper cylinder 4
is connected to the hydraulic pump 3 via the connecting nipples 22 and 23 and the conduits 24 and 25, as shown in FIG.
4 or an oil tank 35, forming a hydraulic damper. By controlling the supply and discharge of pressure oil to both cylinder spaces 6 and 7 via this switching valve 2, vibrations can be damped and shocks can be alleviated.
ばねシリンダ９のシリンダ空間としての環状空
間１１は、接続ニツプル２６と導管２７とを介し
て油圧−空気圧蓄圧槽２８へ通じて、油圧−空気
圧ばねを構成している。この蓄圧槽２８の空気の
弾性により、油圧を介して空気ばね効果が得られ
る。なおこの油圧−空気圧ばねは、環状空間１１
内の油量の変化により、車高調節に利用すること
もできる。このため蓄圧槽２８は３ポート３位置
切換え弁３１を介して油圧ポンプ２９または油タ
ンク３３に接続可能である。切換え弁３１は任意
に動かすことのできるハンドル３２をもつてい
る。適当な設定により、ポンプ２９で油圧−空気
圧蓄圧槽２８を加圧するか、または切換え弁３１
を介して油タンク３３へ徐々に排圧して、ばね−
減衰器装置１の全長したがつて車高の調節を行な
うことができる。 The annular space 11 as cylinder space of the spring cylinder 9 opens via a connecting nipple 26 and a conduit 27 to a pneumatic-hydraulic pressure reservoir 28 and forms a pneumatic-hydraulic spring. The elasticity of the air in the pressure storage tank 28 provides an air spring effect via hydraulic pressure. Note that this hydraulic-pneumatic spring has an annular space 11
It can also be used to adjust the vehicle height by changing the amount of oil inside. Therefore, the pressure accumulation tank 28 can be connected to the hydraulic pump 29 or the oil tank 33 via the 3-port 3-position switching valve 31. The switching valve 31 has a handle 32 that can be moved arbitrarily. Depending on the appropriate setting, the hydraulic-pneumatic pressure reservoir 28 can be pressurized with the pump 29 or the switching valve 31 can be pressurized with the pump 29.
The pressure is gradually discharged to the oil tank 33 through the spring-
The overall length of the damper device 1 makes it possible to adjust the vehicle height.
切換え弁２の電磁石３９および４０は、導線３
７および３８を介して制御器３６により制御され
る。制御器３６には監視器４１が接続され、導線
４２を介して車体と車輪との相互間隔、この相互
間隔の変化速度または減衰器シリンダのピストン
により区画される両シリンダ空間６，７の圧力差
等の測定情報を受け、適当な処理後制御器３６へ
送る。制御器３６はさらに導線４３を介して必要
な外乱情報を直接受け、導線４４を介して外乱観
測器４１へ帰還結合されている。 The electromagnets 39 and 40 of the switching valve 2 are connected to the conductor 3
7 and 38 by controller 36. A monitor 41 is connected to the controller 36 and monitors the distance between the vehicle body and the wheels through a conductor 42, the rate of change of this distance, or the pressure difference between the two cylinder spaces 6 and 7 defined by the piston of the damper cylinder. etc., and sends it to the controller 36 after appropriate processing. The controller 36 further directly receives necessary disturbance information via a conductor 43 and is coupled back to the disturbance observation device 41 via a conductor 44 .
こうして車体と車輪の相互間隔またはこの相互
間隔の変化速度から、所定の初期位置例えば構造
位置に関して、任意の時点に車体と車輪との間の
運動状態が、そのつどの運動傾向と共に求められ
る。一方減衰器シリンダ４の両シリンダ空間の圧
力差の制御を介して、異なる運動傾向に対抗する
ことができ、したがつてこの圧力差から、前記の
相互間隔およびその変化速度を介して求められる
初期位置において例えば強い減衰を得るためにど
んな手段が必要であるかの情報を得ることができ
る。 In this way, from the mutual spacing between vehicle body and wheels or the rate of change of this mutual spacing, the state of motion between vehicle body and wheels is determined at any given time, as well as the respective movement tendency, with respect to a given initial position, for example a structural position. On the one hand, by controlling the pressure difference between the two cylinder spaces of the damper cylinder 4, different movement trends can be counteracted, and from this pressure difference the initial Information can be obtained as to what measures are required to obtain strong damping at a location, for example.
第１図は本発明によるばね−減衰器装置の縦断
面図、第２図はその制御系の接属図である。
１……ばね−減衰器装置、４……減衰器シリン
ダ、５……減衰器ピストン、８……ばねピストン
（環状フランジ）、９……ばねシリンダ、１１……
環状空間。
FIG. 1 is a longitudinal sectional view of a spring-attenuator device according to the invention, and FIG. 2 is a sectional view of its control system. DESCRIPTION OF SYMBOLS 1... Spring-dampener device, 4... Dampener cylinder, 5... Dampener piston, 8... Spring piston (annular flange), 9... Spring cylinder, 11...
annular space.
Claims (1)
と無関係に動作する油圧減衰器とが、車体と車輪
との間に並列に設けられ、油圧減衰器が車体に対
する車輪の位置および運動を特徴づける量に関係
して制御可能であり、油圧−空気圧ばねと油圧減
衰器の油圧部分がそれぞれピストン−シリンダ装
置により形成されているものにおいて、油圧減衰
器用ピストン−シリンダ装置のシリンダ４が車体
および車輪の一方に連結され、このシリンダ４内
に軸線方向移動可能にはまつてこのシリンダ内を
２つのシリンダ空間６，７に区画するピストン５
が、ピストン棒１２を介して車体および車輪の他
方に連結され、両シリンダ空間４，７が、車体に
対する車輪の位置および運動を特徴づける電気量
に関係して切換え動作する電磁切換え弁２を介し
て圧油の給排を制御され、油圧−空気圧ばね用ピ
ストン−シリンダ装置のシリンダ９が、車体およ
び車輪の他方に連結され、かつ油圧減衰器用ピス
トン−シリンダ装置のシリンダ４の一部を同心的
に包囲して、油圧減衰器用ピストン−シリンダ装
置のシリンダ４に設けられるピストンとしての環
状フランジ８と共に環状シリンダ空間１１を区画
し、この環状シリンダ空間１１が油圧−空気圧蓄
圧槽２８の油圧空間に接続されていることを特徴
とする、自動車用複合ばね−減衰器装置。 ２ 油圧減衰器用ピストン−シリンダ装置のシリ
ンダ４が車体に連結され、油圧−空気圧ばね用ピ
ストン−シリンダ装置のシリンダ９が車輪に連結
されていることを特徴とする、特許請求の範囲第
１項に記載の装置。 ３ 油圧減衰器用ピストン−シリンダ装置のピス
トン５がそのピストン棒１２を介して油圧−空気
圧ばね用ピストン−シリンダ装置のシリンダ９の
端部に結合されていることを特徴とする、特許請
求の範囲第１項に記載の装置。[Claims] 1. A hydraulic-pneumatic spring that supports a static load and a hydraulic damper that operates independently of the spring are provided in parallel between the vehicle body and the wheels, and the hydraulic dampers control the movement of the wheels relative to the vehicle body. Cylinder of a piston-cylinder arrangement for a hydraulic damper, which is controllable in relation to the quantities characterizing its position and movement, and in which the hydraulic-pneumatic spring and the hydraulic part of the hydraulic damper are each formed by a piston-cylinder arrangement. 4 is connected to one of the vehicle body and the wheels, and a piston 5 is movable in the axial direction within the cylinder 4 and partitions the inside of the cylinder into two cylinder spaces 6 and 7.
is connected via a piston rod 12 to the vehicle body and to the other of the wheels, and both cylinder spaces 4, 7 are connected via an electromagnetic switching valve 2 which is switched in dependence on the electrical quantities characterizing the position and movement of the wheel relative to the vehicle body. The cylinder 9 of the piston-cylinder device for the hydraulic-pneumatic spring is connected to the other of the vehicle body and the wheel, and a part of the cylinder 4 of the piston-cylinder device for the hydraulic damper is concentrically connected to the cylinder 9 of the piston-cylinder device for the hydraulic-pneumatic spring. and defines an annular cylinder space 11 together with an annular flange 8 as a piston provided on the cylinder 4 of the piston-cylinder device for a hydraulic damper, and this annular cylinder space 11 is connected to the hydraulic space of the hydraulic-pneumatic pressure storage tank 28. A composite spring-dampener device for an automobile, characterized in that: 2. According to claim 1, the cylinder 4 of the piston-cylinder device for a hydraulic damper is connected to the vehicle body, and the cylinder 9 of the piston-cylinder device for a hydraulic-pneumatic spring is connected to a wheel. The device described. 3. Claim 3, characterized in that the piston 5 of the piston-cylinder arrangement for a hydraulic damper is connected via its piston rod 12 to the end of the cylinder 9 of the piston-cylinder arrangement for a hydraulic-pneumatic spring. The device according to item 1.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19772738455 DE2738455A1 (en) | 1977-08-26 | 1977-08-26 | ACTIVE VIBRATION DAMPERS |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5455913A JPS5455913A (en) | 1979-05-04 |
| JPH0151362B2 true JPH0151362B2 (en) | 1989-11-02 |
Family
ID=6017334
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP10241078A Granted JPS5455913A (en) | 1977-08-26 | 1978-08-24 | Active vibration damping method and its device |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JPS5455913A (en) |
| DE (1) | DE2738455A1 (en) |
| FR (1) | FR2401037A1 (en) |
| GB (1) | GB2003255B (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2948215A1 (en) * | 1979-11-30 | 1981-06-04 | Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart | HYDROPNEUMATIC CUSHIONED SEAT FOR VEHICLES, IN PARTICULAR MOTOR VEHICLES |
| JPS5863440U (en) * | 1981-10-23 | 1983-04-28 | カヤバ工業株式会社 | hydraulic shock absorber |
| WO1984002886A1 (en) * | 1983-01-21 | 1984-08-02 | Lotus Car | Vehicle suspension system |
| JPS6078806A (en) * | 1983-10-04 | 1985-05-04 | Showa Mfg Co Ltd | Damping force adjuster of hydraulic shock absorber for car height adjustment |
| GB8328373D0 (en) | 1983-10-24 | 1983-11-23 | Lotus Car | Vehicle suspension device |
| DE3434757A1 (en) * | 1984-09-21 | 1986-04-03 | Siemens AG, 1000 Berlin und 8000 München | Chassis for wheeled vehicles |
| DE3434877A1 (en) * | 1984-09-22 | 1986-04-17 | Boge Gmbh, 5208 Eitorf | HYDRAULIC, ADJUSTABLE SHOCK ABSORBER |
| EP0190944B2 (en) * | 1985-02-08 | 1993-07-21 | Group Lotus Plc | Vehicle suspension arrangements |
| DE3670893D1 (en) * | 1985-07-31 | 1990-06-07 | Wright Barry Corp | PARAMETER CONTROLLED ACTIVE VIBRATION DAMPING SYSTEM. |
| US4809176A (en) * | 1985-10-22 | 1989-02-28 | Toyota Jidosha Kabushiki Kaisha | System for vehicle body roll control with overshoot prevention |
| JPH075009B2 (en) * | 1985-10-22 | 1995-01-25 | トヨタ自動車株式会社 | Vehicle height adjustment device |
| DE3543156C2 (en) * | 1985-12-06 | 1998-04-09 | Bosch Gmbh Robert | Hydropneumatic shock absorber |
| JPH06104450B2 (en) * | 1986-01-29 | 1994-12-21 | 財団法人鉄道総合技術研究所 | Vehicle vibration control device |
| JPH0780411B2 (en) * | 1986-07-31 | 1995-08-30 | トヨタ自動車株式会社 | Active suspension for vehicles |
| EP0255720B2 (en) * | 1986-08-05 | 1992-10-14 | Mazda Motor Corporation | Vehicle suspension system |
| DE3631876A1 (en) * | 1986-09-19 | 1988-03-31 | Bosch Gmbh Robert | VEHICLE SUSPENSION |
| DE3637984A1 (en) * | 1986-11-07 | 1988-05-19 | Bayerische Motoren Werke Ag | METHOD FOR INFLUENCING A VEHICLE SUSPENSION DEPENDING ON THE ROAD DESIGN AND VEHICLE SUSPENSION |
| JPH0694252B2 (en) * | 1986-11-12 | 1994-11-24 | いすゞ自動車株式会社 | Suspension Kneeling Device |
| JPS63125423A (en) * | 1986-11-12 | 1988-05-28 | Isuzu Motors Ltd | Kneeling device for suspension |
| DE3638574A1 (en) * | 1986-11-12 | 1988-05-26 | Rexroth Mannesmann Gmbh | Arrangement for controlling the pressure of a damping cylinder for the suspension of vehicles |
| JPS63125421A (en) * | 1986-11-12 | 1988-05-28 | Isuzu Motors Ltd | Hydro-pneumatic suspension device |
| DE3724271A1 (en) * | 1987-07-22 | 1989-02-02 | Bosch Gmbh Robert | DAMPING DEVICE |
| JPH069926B2 (en) * | 1988-01-29 | 1994-02-09 | 日産自動車株式会社 | Active suspension |
| DE3842338A1 (en) * | 1988-12-16 | 1990-06-21 | Porsche Ag | ACTUATOR FOR AN ACTIVE SPRING-DAMPER SYSTEM |
| DE3931857A1 (en) * | 1989-09-23 | 1991-04-04 | Bosch Gmbh Robert | DAMPING SYSTEM |
| JPH03118105U (en) * | 1990-03-19 | 1991-12-05 | ||
| JP2512556Y2 (en) * | 1990-03-20 | 1996-10-02 | 日産ディーゼル工業株式会社 | Vehicle suspension system |
| DE4029490A1 (en) * | 1990-09-18 | 1992-03-19 | Boge Ag | Vehicle hydraulic piston-cylinder vibration damper - has secondary piston fitted in guide tube inside main piston rod |
| DE4112005A1 (en) * | 1991-04-12 | 1992-10-15 | Bosch Gmbh Robert | SYSTEM FOR FORMING A SIGNAL IN A VEHICLE |
| DE4112007A1 (en) * | 1991-04-12 | 1992-10-15 | Bosch Gmbh Robert | SYSTEM FOR FORMING A SIGNAL IN A VEHICLE |
| DE4231641C2 (en) * | 1992-09-22 | 1996-12-12 | Daimler Benz Ag | Suspension strut for automotive suspension systems |
| DE4327358C2 (en) * | 1993-04-08 | 1995-04-13 | Fichtel & Sachs Ag | Frequency-selective vibration damper |
| FR2729616A1 (en) * | 1995-01-25 | 1996-07-26 | Peugeot | DEVICE FORMING A HYDRAULIC CYLINDER FOR USE IN A HYDROPNEUMATIC SUSPENSION FOR A MOTOR VEHICLE |
| US5603387A (en) * | 1995-09-06 | 1997-02-18 | Applied Power, Inc. | Active vehicle suspension system |
| US20070045067A1 (en) * | 2005-08-26 | 2007-03-01 | Husco International, Inc. | Hydraulic circuit with a pilot operated check valve for an active vehicle suspension system |
| DE102005044211A1 (en) | 2005-09-12 | 2007-03-22 | Wirtgen Gmbh | Self-propelled construction machine, as well as lifting column for a construction machine |
| NL1030146C2 (en) * | 2005-10-10 | 2007-04-11 | Transp Industry Dev Ct Bv | Vehicle. |
| DE102006010738A1 (en) * | 2006-03-08 | 2007-09-13 | Trw Automotive Gmbh | fluid reservoir |
| DE102006062129B4 (en) | 2006-12-22 | 2010-08-05 | Wirtgen Gmbh | Road construction machine and method for measuring the cutting depth |
| DE202007013300U1 (en) * | 2007-09-21 | 2009-02-12 | Liebherr-Aerospace Lindenberg Gmbh | Active hydraulic damper and hydraulic actuator |
| DE102014207055B4 (en) | 2014-03-04 | 2016-05-12 | Zf Friedrichshafen Ag | Vibration damper with level control |
| DE102015218490A1 (en) | 2015-09-25 | 2017-03-30 | Zf Friedrichshafen Ag | Vibration damper and motor vehicle |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3124368A (en) * | 1964-03-10 | Electronic controlled vehicle suspension system | ||
| US2992837A (en) * | 1958-11-03 | 1961-07-18 | Itt | Vehicle suspension and stabilizing system |
| GB1050064A (en) * | 1964-08-31 | |||
| US3417985A (en) * | 1965-04-16 | 1968-12-24 | Jerry M. Hannan | Automatic antisway machanism for vehicles |
| US3502347A (en) * | 1967-11-06 | 1970-03-24 | Itt | Apparatus for vehicle suspension control |
| US3606233A (en) * | 1968-04-22 | 1971-09-20 | Bolt Beranek & Newman | Vibration isolation system |
| US3606365A (en) * | 1969-11-03 | 1971-09-20 | Budd Co | Active suspension system for a vehicle |
| US3807678A (en) * | 1972-09-19 | 1974-04-30 | Lord Corp | System for controlling the transmission of energy between spaced members |
| US3995883A (en) * | 1973-11-21 | 1976-12-07 | Lucas Aerospace Limited | Land vehicle wheel suspension arrangements |
| JPS5892275A (en) * | 1981-11-28 | 1983-06-01 | Mitsubishi Electric Corp | Manufacture of field effect transistor |
-
1977
- 1977-08-26 DE DE19772738455 patent/DE2738455A1/en active Granted
-
1978
- 1978-08-23 GB GB7834233A patent/GB2003255B/en not_active Expired
- 1978-08-24 JP JP10241078A patent/JPS5455913A/en active Granted
- 1978-08-24 FR FR7824565A patent/FR2401037A1/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| GB2003255B (en) | 1982-06-23 |
| FR2401037A1 (en) | 1979-03-23 |
| JPS5455913A (en) | 1979-05-04 |
| FR2401037B1 (en) | 1983-08-19 |
| DE2738455A1 (en) | 1979-03-01 |
| GB2003255A (en) | 1979-03-07 |
| DE2738455C2 (en) | 1989-10-26 |
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