JPH0313420Y2 - - Google Patents
Info
- Publication number
- JPH0313420Y2 JPH0313420Y2 JP1984150110U JP15011084U JPH0313420Y2 JP H0313420 Y2 JPH0313420 Y2 JP H0313420Y2 JP 1984150110 U JP1984150110 U JP 1984150110U JP 15011084 U JP15011084 U JP 15011084U JP H0313420 Y2 JPH0313420 Y2 JP H0313420Y2
- Authority
- JP
- Japan
- Prior art keywords
- wheel steering
- steering
- oil
- rear wheel
- pressure
- 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
- 238000006243 chemical reaction Methods 0.000 claims description 12
- 230000007935 neutral effect Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 5
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
Landscapes
- Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
Description
【考案の詳細な説明】
（産業上の利用分野）
本考案は、４輪操舵車両の後輪操舵制御装置に
関するもので、特に、低速走行時におけるハンド
ルによる大蛇角での操舵に際して後輪が前輪とは
逆向きに転蛇される４輪操舵車両の後輪操舵制御
装置に関するものである。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a rear wheel steering control device for a four-wheel steering vehicle, and in particular, when steering at a large angle with the steering wheel during low-speed driving, the rear wheels are replaced by the front wheels. This invention relates to a rear wheel steering control device for a four-wheel steering vehicle that is turned in the opposite direction.
（従来の技術）
上記の形式の後輪操舵御装置として先願の特願
昭59−15335号にり第３図に示すようなものが提
案されている。(Prior Art) As a rear wheel steering control device of the above type, a device as shown in FIG. 3 has been proposed in the earlier Japanese Patent Application No. 15335/1983.
図中１は後輪操舵用油圧シリンダーを示し、こ
の後輪操舵用油圧シリンダー１の操舵ロツド２
は、その両端部を、ナツクルアーム３ａ，３ｂを
介して後輪４ａ，４ｂにそれぞれ連結されてい
る。 In the figure, 1 indicates a hydraulic cylinder for rear wheel steering, and a steering rod 2 of this hydraulic cylinder 1 for steering rear wheels.
are connected at both ends to rear wheels 4a, 4b via knuckle arms 3a, 3b, respectively.
ここにおけるこの後輪操舵用油圧シリンダー１
は、筒形ハウジング５と、このハウジング５の中
心に貫通する操舵ロツド２とを具える他、ハウジ
ング５の中央部に設けた反力室６およびハウジン
グ５の両端部で、反力室６の両側に隣接させて設
けた油室７，８を具えており、その反力室６は、
ハウジング５の大径穴９内に二枚のばね受プレー
ト１０，１１を摺動可能に嵌め合せ、そしてそれ
らの両プレート１０，１１間に予め圧縮変形させ
たリターンスプリング１２を介装することによ
り、また、油室７，８は、大径穴９に連通する各
小径穴１３，１４内の大径穴側端部分で、操舵ロ
ツド２に、通常はばね受プレート１０，１１とそ
れぞれ接触するピストン１５，１６を設けること
によりそれぞれ構成される。これがため、油室
７，８のいずれか一方へ供給される油圧は、その
油圧によつていずれかのピストンに及ぼされる力
がコイルスプリング１２の圧縮反力に打ち勝つた
場合にのみ操舵ロツド２を作動させ、操舵ロツド
２が図に矢印で示すように右側へ作動された場合
には、後輪４ａ，４ｂの左方向への転蛇が、また
それが図に矢印Ｂで示すように左側へ作動された
場合には、後輪４ａ，４ｂの右方向への転舵がそ
れぞれもたらされる。 This rear wheel steering hydraulic cylinder 1 here
In addition to comprising a cylindrical housing 5 and a steering rod 2 penetrating through the center of the housing 5, a reaction force chamber 6 is provided in the center of the housing 5 and a reaction force chamber 6 is provided at both ends of the housing 5. It has oil chambers 7 and 8 adjacent to each other on both sides, and the reaction force chamber 6 is
By slidably fitting two spring bearing plates 10 and 11 into the large diameter hole 9 of the housing 5, and interposing a return spring 12 which has been compressed and deformed in advance between both plates 10 and 11. Also, the oil chambers 7 and 8 are in contact with the steering rod 2, and usually with the spring bearing plates 10 and 11, respectively, at the large diameter hole side end portions of the small diameter holes 13 and 14 communicating with the large diameter hole 9. They are each configured by providing pistons 15 and 16. Therefore, the hydraulic pressure supplied to either one of the oil chambers 7, 8 will cause the steering rod 2 to move only when the force exerted on one of the pistons by the hydraulic pressure overcomes the compression reaction force of the coil spring 12. When the steering rod 2 is actuated to the right as shown by the arrow in the figure, the rear wheels 4a and 4b roll to the left, which also causes the steering rod 2 to move to the left as shown by the arrow B in the figure. When actuated, each of the rear wheels 4a, 4b is steered to the right.
このような後輪操舵用油圧シリンダー１の油室
７，８はれぞれ油路１７，１８を介して前輪操舵
用のパワーシリンダー１９に接続され、このパワ
ーシリンダー１９は、油路２０，２１およびコン
トロールバルブ２２を介してポンプ２３および油
槽２４に並列に接続される。 The oil chambers 7 and 8 of the rear wheel steering hydraulic cylinder 1 are connected to the front wheel steering power cylinder 19 via oil passages 17 and 18, respectively, and this power cylinder 19 is connected to the front wheel steering power cylinder 19 through oil passages 20 and 21. and is connected in parallel to a pump 23 and an oil tank 24 via a control valve 22.
またここで、２５はハンドルを、２６はハンド
ル２５に連結された機械的な前輪操舵系をそれぞ
れ示す。 Further, here, 25 indicates a handle, and 26 indicates a mechanical front wheel steering system connected to the handle 25.
このように構成してなる後輪操舵装置におい
て、ハンドル２５を左方向に操舵した場合には、
油路２０がポンプ２３に、また油路２１が油槽２
４にそれぞれ連通されるので、パワーシリンダー
１９の図の左側の油室１９ａが高圧になる一方、
図の右側の油室１９ｂが低圧となる。この結果、
パワーシリンダー１９は図示しない前輪の左方向
への転舵をアシストする。 In the rear wheel steering device configured in this way, when the handle 25 is steered to the left,
The oil passage 20 is connected to the pump 23, and the oil passage 21 is connected to the oil tank 2.
4, so while the oil chamber 19a on the left side of the power cylinder 19 in the figure becomes high pressure,
The oil chamber 19b on the right side of the figure has a low pressure. As a result,
The power cylinder 19 assists in steering the front wheels (not shown) to the left.
またハンドル２５を右方向へ操舵した場合に
は、油室１９ｂが高圧になる一方、油室１９ａが
低圧になるので、パワーシリンダー１９は前輪の
右方向への転舵をアシストする。 Furthermore, when the steering wheel 25 is steered to the right, the pressure in the oil chamber 19b becomes high while the pressure in the oil chamber 19a becomes low, so that the power cylinder 19 assists in steering the front wheels to the right.
パワーシリンダー１９のこのような作用に際
し、ハンドル２５を回すための操舵トルクが小さ
い場合には、油室１９ａおよび１９ｂのそれぞれ
に作用する油圧の圧力差が小さいので、油室１９
ａ，１９ｂ内の圧力がそれぞれ油路１８，１７を
介して後輪操舵用油圧シリンダー１の油室８，７
へ導びかれても、その油圧は、ピストン１６，１
５のいずれか一方を、コイルスプリング１２の圧
縮反力に抗して反力室６側へ移動させることはで
きない。 When the power cylinder 19 operates in this way, if the steering torque for turning the handle 25 is small, the pressure difference between the oil pressures acting on each of the oil chambers 19a and 19b is small, so the oil chamber 19
The pressure in a and 19b is transmitted to the oil chambers 8 and 7 of the rear wheel steering hydraulic cylinder 1 via oil passages 18 and 17, respectively.
Even if the hydraulic pressure is guided to the piston 16,1
5 cannot be moved toward the reaction force chamber 6 against the compression reaction force of the coil spring 12.
すなわち、油室７，８のそれぞれに供給される
油圧の圧力差が所定値P0以上となるまで、ここ
かえれば、ピストン１５，１６の有効受圧面にそ
れぞれ作用する力の差が、コイルスプリング１２
のセツト荷重より大きくなるまではピストン１
５，１６は全く変位せず、この結果、後輪操舵用
油圧シリンダー１による後輪の転舵は行われな
い。 In other words, until the pressure difference between the hydraulic pressures supplied to each of the oil chambers 7 and 8 reaches a predetermined value P0 or more, the difference in force acting on the effective pressure receiving surfaces of the pistons 15 and 16 is applied to the coil spring. 12
piston 1 until it becomes larger than the set load of
5 and 16 are not displaced at all, and as a result, the rear wheels are not steered by the rear wheel steering hydraulic cylinder 1.
ところが、操舵トルクが所定値以上となつてパ
ワーシリンダー１９の油室１０ａ，１９ｂの内圧
差が所定値P0以上となつた場合には、後輪操舵
用油圧シリンダー１のピストン１５，１６に作用
する力の差がコイルスプリング１２のセツト荷重
より大きくなり、ピストン１５，１６、ひいては
操舵ロツド２が、油室７，８の内圧差に応じた量
だけいずれかの方向へ変位するので、後輪４ａ，
４ｂは、その変位量に応じた量だけ右もしくは左
へ転舵される。このことを車両の左旋回について
みると、所定の操舵トルク以上でハンドル２５を
左方向へ操舵することにより、パワーシリンダー
１９の油室１９ａおよび後輪操舵用油圧シリンダ
ー１の油室８がそれぞれポンプ２３に連通される
一方、油室１９ｂおよび油室７が油槽２４に連通
され、しかも、油室８の内圧と油室７の内圧との
差圧が所定値P0以上になるため、前輪の左方向
への転舵が、パワーシリンダー１９によつて前述
したと同様にアシストされる他、後輪操舵用油圧
シリンダー１の操舵ロツド２の左方向への変位が
もたらされ、これにより後輪４ａ，４ｂは右方向
へ転舵される。この結果、車両の左方向への旋回
半径は十分小さくなる。 However, when the steering torque exceeds a predetermined value and the internal pressure difference between the oil chambers 10a and 19b of the power cylinder 19 exceeds the predetermined value P0 , the pistons 15 and 16 of the rear wheel steering hydraulic cylinder 1 are affected. The difference in the force exerted by the engine becomes larger than the set load of the coil spring 12, and the pistons 15 and 16, and eventually the steering rod 2, are displaced in either direction by an amount corresponding to the internal pressure difference between the oil chambers 7 and 8. 4a,
4b is steered to the right or left by an amount corresponding to the amount of displacement. Considering this when turning the vehicle to the left, by steering the steering wheel 25 to the left with a predetermined steering torque or more, the oil chamber 19a of the power cylinder 19 and the oil chamber 8 of the rear wheel steering hydraulic cylinder 1 are pumped. 23, while the oil chamber 19b and the oil chamber 7 are connected to the oil tank 24, and the differential pressure between the internal pressure of the oil chamber 8 and the internal pressure of the oil chamber 7 exceeds a predetermined value P0 , so that the front wheel In addition to assisting the steering to the left by the power cylinder 19 in the same manner as described above, the steering rod 2 of the rear wheel steering hydraulic cylinder 1 is also displaced to the left, thereby steering the rear wheels. 4a and 4b are steered to the right. As a result, the leftward turning radius of the vehicle becomes sufficiently small.
なおここで、ハンドルの操舵トルクが所定値以
下もしくは零となつた場合には、後輪操舵用油圧
シリンダー１の操舵ロツド２が、反力室６の作用
下で第６図に示す中立位置へ復帰されるので、後
輪４ａ，４ｂもまたその中立位置へ復元されるこ
とになる。 Here, if the steering torque of the steering wheel becomes less than a predetermined value or becomes zero, the steering rod 2 of the rear wheel steering hydraulic cylinder 1 is moved to the neutral position shown in FIG. 6 under the action of the reaction force chamber 6. Since the rear wheels 4a and 4b are returned to their neutral positions, the rear wheels 4a and 4b are also restored to their neutral positions.
（考案が解決しようとする問題点）
上述したような４輪操舵車両においては、車両
Ｃを道路の縁石Ｄに沿つて縦列駐車した際、前輪
操舵だけであれば脱出可能の状態であつても、４
輪操舵では、第４図に示すように後輪４ａが縁石
Ｄと干渉して脱出できないという問題が生じる。(Problem to be solved by the invention) In the above-mentioned four-wheel steering vehicle, when vehicle C is parallel parked along the curb D of the road, even if it is possible to escape if only the front wheels are steered. , 4
In wheel steering, a problem arises in that the rear wheels 4a interfere with the curb D and cannot escape, as shown in FIG.
（問題点を解決するための手段）
本考案の目的は、４輪操舵車両を縁石に沿つて
の縦列駐車から脱出させる場合に、一方の後輪４
ａが縁石等と干渉した際に、後輪操舵系が機能し
ないように構成した後輪操舵制御装置を提供しよ
うとするものである。(Means for Solving the Problems) The purpose of the present invention is to provide a vehicle with one rear wheel when escaping a four-wheel steering vehicle from parallel parking along a curb.
It is an object of the present invention to provide a rear wheel steering control device configured so that the rear wheel steering system does not function when the rear wheel steering system A interferes with a curb or the like.
車両の一方の後輪４ａ第４図に示すように縁石
Ｄと干渉して脱出困難になる状態は、縁石に沿つ
て縦列駐車している車両Ｃを矢印Ｅの方向に脱出
させるためハンドル２５を右方向に所定値以上の
大きな操舵トルクによつて操舵する結果として生
じる。すなわち、ハンドル２５を右方向に所定値
以上の大きな操舵トルクで操舵する場合、第３図
において前輪操舵系２６のパワーシリンダー１９
の油室１９ａが低圧となり、油室１９ｂが高圧と
なり、これらの油室に油路１７，１８を介してそ
れぞれ接続されている後輪操舵系の油圧シリンダ
ー１の油室７が高圧に、油室８が低圧となり、そ
の油圧の圧力差が大きく生じ、油圧シリンダー１
のピストン１５，１６に作用する力の差がコイル
スプリング１２のセツト荷重より大きくなること
により操舵ロツド２が油室７，８の内圧差に応じ
た量だけ矢印Ａで示すように右側に作動され、後
輪の４ａ，４ｂが左方向に転舵され、一方の後輪
４ａが縁石に干渉する状態が生ずる。そして、か
かる干渉が生じた場合、後輪４によつて矢印Ｂ方
向の力がピストン１５，１６に作用し、この結果
として油室７，８の差圧が常用の一定値以上とな
る。 When one rear wheel 4a of the vehicle interferes with the curb D and becomes difficult to escape as shown in FIG. This occurs as a result of steering to the right with a large steering torque greater than a predetermined value. That is, when steering the steering wheel 25 to the right with a large steering torque greater than a predetermined value, the power cylinder 19 of the front wheel steering system 26 in FIG.
The oil chamber 19a of the rear wheel steering system has a low pressure, the oil chamber 19b has a high pressure, and the oil chamber 7 of the hydraulic cylinder 1 of the rear wheel steering system, which is connected to these oil chambers via oil passages 17 and 18, has a high pressure. The pressure in the chamber 8 becomes low, and a large pressure difference occurs in the hydraulic pressure, causing the hydraulic cylinder 1 to
When the difference in force acting on the pistons 15 and 16 becomes larger than the set load of the coil spring 12, the steering rod 2 is moved to the right as shown by arrow A by an amount corresponding to the internal pressure difference between the oil chambers 7 and 8. , the rear wheels 4a and 4b are steered to the left, resulting in a situation where one of the rear wheels 4a interferes with the curb. When such interference occurs, a force in the direction of arrow B is applied by the rear wheel 4 to the pistons 15 and 16, and as a result, the differential pressure between the oil chambers 7 and 8 becomes equal to or higher than a constant constant value.
したがつて、本考案によれば、上述した目的を
達成するため、第１図に示すように、後輪操舵用
油圧シリンダ１の左右油室７，８の差圧が常用の
一定値P1以上であることを検出して両油室７，
８を連通させる手段を設けたことを特徴とする。 Therefore, according to the present invention, in order to achieve the above-mentioned object, as shown in FIG . After detecting the above, both oil chambers 7,
8 is characterized by providing means for communicating with each other.
（作用）
本考案によれば、上述したように、例えば、ハ
ンドル２５を右方向に操舵することによつて、左
側の後輪４ａが縁石Ｄに干渉した場合、左右油室
７，８の圧力差が常用の一定値P1以上になるか
ら、これを検出して両油室７，８を連通させ、こ
れにより両油室７，８の差圧を所定値P0以下に
減少させる。かようにして両油室７，８の差圧が
所定値P0以下もしくは零となる結果、後輪操舵
用油圧シリンダー１の操舵ロツド２が反力室６の
リターンスプリング１２の作用下で第１図に示す
中立位置に復帰するので、後輪４ａ，４ｂもまた
その中立位置へ復元されることになり、前輪だけ
が操舵されるから容易に脱出することができるよ
うになる。(Function) According to the present invention, as described above, when the left rear wheel 4a interferes with the curb D by, for example, steering the handle 25 to the right, the pressure in the left and right oil chambers 7 and 8 increases. Since the difference becomes more than a commonly used constant value P 1 , this is detected and both oil chambers 7 and 8 are brought into communication, thereby reducing the differential pressure between both oil chambers 7 and 8 to a predetermined value P 0 or less. As a result, the differential pressure between the two oil chambers 7 and 8 becomes less than the predetermined value P0 or zero, and the steering rod 2 of the rear wheel steering hydraulic cylinder 1 is rotated under the action of the return spring 12 of the reaction force chamber 6. Since the vehicle returns to the neutral position shown in FIG. 1, the rear wheels 4a and 4b are also restored to their neutral positions, and since only the front wheels are steered, it becomes possible to escape easily.
（実施例）
第１図は、本考案の第１実施例を示し、この実
施例では、前輪操舵用パワーシリンダー１９の油
室１９ａ，１９ｂを後輪操舵用油圧シリンダー１
の油室７，８に油路２７，２８を介してそれぞれ
接続し、これらの油路２７，２８間に第１および
第２連通路２９，３０をそれぞれ接続し、連通路
２９，３０の連通を油路２７，２８のそれぞれか
らのパイロツト油圧によつて制御する調整ばね型
パイロツト制御弁３１，３２を各連通路２９，３
０にそれぞれ設けている。(Embodiment) FIG. 1 shows a first embodiment of the present invention. In this embodiment, the oil chambers 19a and 19b of the power cylinder 19 for steering the front wheels are connected to the hydraulic cylinder 1 for steering the rear wheels.
are connected to the oil chambers 7 and 8 via oil passages 27 and 28, respectively, and between these oil passages 27 and 28, first and second communication passages 29 and 30 are respectively connected, and the communication passages 29 and 30 are connected to Adjustment spring type pilot control valves 31, 32, which are controlled by pilot oil pressure from oil passages 27, 28, respectively, are connected to communication passages 29, 3, respectively.
0 respectively.
かように構成することによつて、制御弁３１，
３２の調整ばねによつて設定された一定値より両
油室７，８の差圧が高くなつた際、各制御弁３
１，３２は連通路２９，３０のそれぞれを連通さ
せ、これにより両油室７，８の差圧を一定値P1
以下に低下させ、または所定値P0以下に低下さ
せて後輪操舵用油圧シリンダー１の反力室６内の
リターンスプリング１２の作用によつて後輪４
ａ，４ｂを中立位置に復元させる。 With this configuration, the control valve 31,
When the differential pressure between the oil chambers 7 and 8 becomes higher than the constant value set by the adjustment spring 32, each control valve 3
1 and 32 connect the communication passages 29 and 30, respectively, so that the differential pressure between the oil chambers 7 and 8 is maintained at a constant value P 1
or lowering it to a predetermined value P 0 or less, and by the action of the return spring 12 in the reaction force chamber 6 of the rear wheel steering hydraulic cylinder 1, the rear wheel 4
a and 4b are restored to their neutral positions.
第２図は、本考案の第２実施例を示し、本例で
は、前輪操舵用パワーシリンダー１９の油室１９
ａ，１９ｂを後輪操舵用油圧シリンダー１の油室
７，８に接続する接続位置３３Ａに常時位置する
電磁４ポート２位置切換制御弁３３を油路２７，
２８に設け、ソレノイド３３ａの附勢時に、上記
接続位置３３Ａから連通位置３３Ｂに電磁的に切
換えられて後輪操舵用油圧シリンダー１の油室
７，８を連通させるようにし、後輪操舵用油圧シ
リンダーの油室７，８内の油圧をそれぞれ検出す
るための油圧センサー３４，３５を油路２７，２
８に取付け、これらの油圧センサー３４，３５か
らの油圧信号を入力してその油圧差が一定値P1
以上となるに附勢信号を切換制御弁３３のレノイ
ド３３ａに出力するコントローラ３６を設けてい
る。 FIG. 2 shows a second embodiment of the present invention, in which the oil chamber 19 of the front wheel steering power cylinder 19 is
a, 19b to the oil chambers 7, 8 of the rear wheel steering hydraulic cylinder 1.
28, and when the solenoid 33a is energized, it is electromagnetically switched from the connection position 33A to the communication position 33B to connect the oil chambers 7 and 8 of the rear wheel steering hydraulic cylinder 1, so that the rear wheel steering hydraulic pressure Oil pressure sensors 34 and 35 for detecting the oil pressure in the oil chambers 7 and 8 of the cylinder are connected to oil passages 27 and 2, respectively.
8, input the oil pressure signals from these oil pressure sensors 34 and 35, and set the oil pressure difference to a constant value P 1
As described above, a controller 36 is provided which outputs an energizing signal to the renoid 33a of the switching control valve 33.
上述の構成になる第２実施例によれば、後輪操
舵用油圧シリンダー１の油室７，８の差圧が一定
値P1以上となる際に、切換制御弁３３が接続位
置３３Ａから連通位置３３Ｂに切換えられて前輪
操舵用パワーシリンダーと後輪操舵用油圧シリン
ダー１との接続を遮断するとともに後輪操舵用油
圧シリンダー１の両油室７，８を互に連通させ、
これにより両油室７，８の差圧は所定値P0以下
もしくは零に低下し、後輪操舵用油圧シリンダー
１の反力室６内のリターンスプリング１２の作用
によつて後輪４ａ，４ｂを中立位置に復元し、こ
れによつて車両は前輪操舵系２６だけて操舵され
ることになる。 According to the second embodiment configured as described above, when the differential pressure between the oil chambers 7 and 8 of the rear wheel steering hydraulic cylinder 1 exceeds a certain value P1, the switching control valve 33 is opened from the connection position 33A. Switched to position 33B, the connection between the front wheel steering power cylinder and the rear wheel steering hydraulic cylinder 1 is cut off, and both oil chambers 7 and 8 of the rear wheel steering hydraulic cylinder 1 are communicated with each other,
As a result, the differential pressure between the two oil chambers 7, 8 decreases to below a predetermined value P0 or to zero, and by the action of the return spring 12 in the reaction force chamber 6 of the rear wheel steering hydraulic cylinder 1, the rear wheels 4a, 4b is restored to the neutral position, whereby the vehicle is steered using only the front wheel steering system 26.
（考案の効果）
本考案によれば、後輪操舵時に後輪が縁石等と
干渉する際、この干渉によつて生じる後輪操舵用
油圧シリンダーの両油室の差圧の増大を検出し
て、両油室間の差圧を低下もしくは零にし、後輪
を中立位置に戻すよう制御する構成としたから、
後輪操舵により生ずる後輪と縁石等との干渉の問
題を解消することができるという効果が得られ
る。(Effects of the invention) According to the invention, when the rear wheels interfere with a curb, etc. during rear wheel steering, an increase in the differential pressure between both oil chambers of the hydraulic cylinder for rear wheel steering caused by this interference is detected. , the differential pressure between both oil chambers is reduced or zero, and the rear wheels are controlled to return to the neutral position.
This has the effect of solving the problem of interference between the rear wheels and a curb, etc., caused by rear wheel steering.
第１図は本考案の第１実施例による後輪操舵制
御装置を示す図、第２図は本考案の第２実施例に
よる後輪操舵制御装置を示す図、第３図は従来の
後輪操舵制御装置を示す図、第４図は従来の４輪
操舵車両によつて生じる問題の設明用図である。
１……後輪操舵用油圧シリンダー、２……操舵
ロツド、３ａ，３ｂ……ナツクルアーム、４ａ，
４ｂ……後輪、６……反力室、７，８……油室、
１０，１１……ばね受プレート、１２……リター
ンスプリング、１５，１６……ピストン、１９…
…パワーシリンダー、２２……コントロールバル
ブ、２３……ポンプ、２４……油槽、２５……ハ
ンドル、２７，２８……油路、２９，３０………
連通路、３１，３２……制御弁、３３……切換制
御弁、３４，３５……油圧センサー、３６……コ
ントローラ。
FIG. 1 is a diagram showing a rear wheel steering control device according to a first embodiment of the present invention, FIG. 2 is a diagram showing a rear wheel steering control device according to a second embodiment of the present invention, and FIG. 3 is a diagram showing a rear wheel steering control device according to a second embodiment of the present invention. FIG. 4, a diagram showing a steering control device, is a diagram for explaining the problems caused by conventional four-wheel steering vehicles. 1...Hydraulic cylinder for rear wheel steering, 2...Steering rod, 3a, 3b...Knuckle arm, 4a,
4b... Rear wheel, 6... Reaction force chamber, 7, 8... Oil chamber,
10, 11... Spring bearing plate, 12... Return spring, 15, 16... Piston, 19...
...Power cylinder, 22... Control valve, 23... Pump, 24... Oil tank, 25... Handle, 27, 28... Oil path, 29, 30...
Communication path, 31, 32... control valve, 33... switching control valve, 34, 35... oil pressure sensor, 36... controller.
Claims (1)
油圧シリンダの左右油室のいづれか一方に魅圧が
油路を経て導入されることによりリターンスプリ
ングの反力に抗して操舵ロツドを作動して後輪を
操舵するよう構成した４輪操舵車両の後輪操舵制
御装置において、前記油圧シリンダーの両油室の
差圧が常用する一定値以上になる際に前記差圧を
減じる制御弁を前記油路に設けたことを特徴とす
る４輪操舵車両の後輪操舵制御装置。 In response to steering of the front wheel steering system, attractive pressure is introduced into either the left or right oil chamber of the rear wheel steering hydraulic cylinder via the oil passage, thereby operating the steering rod against the reaction force of the return spring. In a rear wheel steering control device for a four-wheel steering vehicle configured to steer the rear wheels, a control valve that reduces the differential pressure when the differential pressure between both oil chambers of the hydraulic cylinder exceeds a commonly used constant value is provided. A rear wheel steering control device for a four-wheel steering vehicle, characterized in that it is installed on a road.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1984150110U JPH0313420Y2 (en) | 1984-10-05 | 1984-10-05 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1984150110U JPH0313420Y2 (en) | 1984-10-05 | 1984-10-05 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6166064U JPS6166064U (en) | 1986-05-07 |
| JPH0313420Y2 true JPH0313420Y2 (en) | 1991-03-27 |
Family
ID=30708264
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1984150110U Expired JPH0313420Y2 (en) | 1984-10-05 | 1984-10-05 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0313420Y2 (en) |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6091563U (en) * | 1983-11-30 | 1985-06-22 | 三菱自動車工業株式会社 | Rear wheel steering device |
-
1984
- 1984-10-05 JP JP1984150110U patent/JPH0313420Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6166064U (en) | 1986-05-07 |
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