JPH02185865A - Four-wheel steering system - Google Patents
Four-wheel steering systemInfo
- Publication number
- JPH02185865A JPH02185865A JP1004299A JP429989A JPH02185865A JP H02185865 A JPH02185865 A JP H02185865A JP 1004299 A JP1004299 A JP 1004299A JP 429989 A JP429989 A JP 429989A JP H02185865 A JPH02185865 A JP H02185865A
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- wheel steering
- steering device
- wheel
- output shaft
- 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.)
- Granted
Links
- 238000010586 diagram Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 238000004804 winding Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Landscapes
- Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
Abstract
Description
【発明の詳細な説明】
〈産業上の利用分野〉
本発明は、前輪の操舵をケーブルを介して後輪に伝える
ようにした４輪操舵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 four-wheel steering device in which steering of front wheels is transmitted to rear wheels via a cable.
〈従来の技術〉
かかる４輪操舵装置は、例えば実開昭６０−１５０５２
号公報で公知であり、このものは前輪の動きをケーブル
を介して後輪操舵装置のギヤに伝え、このギヤの回転を
ラックに伝えることによって後輪を前輪と逆相に操舵し
ている。<Prior art> Such a four-wheel steering device is disclosed in, for example, Utility Model Application No. 60-15052.
This device transmits the movement of the front wheels to the gear of the rear wheel steering device via a cable, and transmits the rotation of this gear to the rack, thereby steering the rear wheels in the opposite phase to the front wheels.
〈発明が解決しようとする課題〉
上述したものは、後輪の操舵角が前輪の操舵角に比例し
て直線的に増加するため、第６図に示すような３次曲線
的なカーブが得られない。従って、前輪の少ない操舵角
でも後輪が操舵されるため、高速走行に向かない問題が
あった。<Problem to be solved by the invention> In the above-mentioned case, the steering angle of the rear wheels increases linearly in proportion to the steering angle of the front wheels, so a cubic curve as shown in FIG. 6 is obtained. I can't do it. Therefore, since the rear wheels are steered even when the front wheels are steered at a small steering angle, there is a problem that the vehicle is not suitable for high-speed driving.
〈課題を解決するための手段〉
本発明は上述した問題点を解決するためになされたもの
で、後輪操舵装置に後輪側の出力軸を回転可能に設け、
この出力軸に出力軸の回転中心から偏心した位置に偏心
ピンを取付け、後輪操舵装置にケーブル側の入力軸を出
力軸に対する偏心ピンの偏心量よりも少ない量で出力軸
に対して偏心した位置に回転可能に設け、この入力軸に
前記偏心ピンが係合する係合溝を半径方向に形成する。<Means for Solving the Problems> The present invention has been made in order to solve the above-mentioned problems, and includes a rear wheel steering device that is rotatably provided with an output shaft on the rear wheel side,
An eccentric pin is attached to this output shaft at a position eccentric from the center of rotation of the output shaft, and the input shaft on the cable side of the rear wheel steering device is eccentrically attached to the output shaft by an amount smaller than the eccentricity of the eccentric pin with respect to the output shaft. The input shaft is rotatably provided at a position, and an engagement groove in which the eccentric pin engages is formed in the radial direction of the input shaft.
また前輪操舵装置に前輪側の入力軸を回転可能に設け、
この入力軸に半径方向に係合溝を形成し、前輪操舵装置
にケーブル側の出力軸を入力軸に対して偏心した位置に
回転可能に設け、この出力軸に前記係合溝に係合する偏
心ピンを入力軸に対する出力軸の偏心量よりも多い量で
出力軸に対して偏心した位置に取付ける。In addition, the front wheel steering device is equipped with a rotatable input shaft on the front wheel side.
An engagement groove is formed in the input shaft in the radial direction, an output shaft on the cable side of the front wheel steering device is rotatably provided at a position eccentric to the input shaft, and the output shaft is engaged with the engagement groove. Install the eccentric pin at a position that is eccentric to the output shaft by an amount greater than the amount of eccentricity of the output shaft to the input shaft.
く作用〉
後輪操舵装置に係合溝と係合ピンを設けたものにおいて
は、前輪操舵装置によって前輪を操舵すると、前輪の操
舵がケーブルを介して後輪操舵装置の入力軸に伝えられ
、この入力軸の回転が係合溝と係合ピンを介して出力軸
に伝えられる。入力軸の回転につれて出力軸は始めは少
なく回転し、最後は大きく回転する。この出力軸の回転
によって後輪は操舵される。また前輪操舵装置に係合溝
と係合ピンを設けたものにおいては、前輪操舵装置によ
って前輪を操舵すると、前輪の操舵が前輪操舵装置の入
力軸に伝えられ、この入力軸の回転が係合溝と保合ピン
を介して出力軸に伝えられる。In a rear wheel steering device in which an engagement groove and an engagement pin are provided, when the front wheels are steered by the front wheel steering device, the steering of the front wheels is transmitted to the input shaft of the rear wheel steering device via a cable. This rotation of the input shaft is transmitted to the output shaft via the engagement groove and the engagement pin. As the input shaft rotates, the output shaft rotates less at first and then more at the end. The rear wheels are steered by this rotation of the output shaft. In addition, in a front wheel steering device in which an engagement groove and an engagement pin are provided, when the front wheels are steered by the front wheel steering device, the steering of the front wheels is transmitted to the input shaft of the front wheel steering device, and the rotation of this input shaft is transmitted to the input shaft of the front wheel steering device. It is transmitted to the output shaft via the groove and retaining pin.
入力軸の回転につれて出力軸は始めは少なく回転し、最
後は大きく回転する。この出力軸の回転はケーブルを介
して後輪操舵装置に伝えられ、後輪を操舵する。As the input shaft rotates, the output shaft rotates less at first and then more at the end. This rotation of the output shaft is transmitted via a cable to the rear wheel steering device, which steers the rear wheels.
〈実施例〉 以下本発明の実施例を図面に基づいて説明する。<Example> Embodiments of the present invention will be described below based on the drawings.
第２図において、１ｏは前輪用ラック軸であり、この前
輪用ラック軸ＩＯの両端にはタイロッド１１とナックル
アーム１２を介して前輪１３が連結されている。前輪用
ラック軸１ｏにはラック１４が形成され、このラック１
４に前輪用ビニオン軸１５のビニオン１６が噛合されて
いる。ピニオン軸１５はロータリーバルブ１７を介して
ハンドル１８に回転連結されている。前記前輪用ラック
軸１０にはシリンダチューブ１９内を摺動するピストン
２０が取付けられている。前述した前輪用ラック軸１０
とピニオン軸１５とロータリーバルブ１７とシリンダチ
ューブ１９とピストン２０とによって前輪操舵装置２１
が構成される。In FIG. 2, 1o is a front wheel rack shaft, and a front wheel 13 is connected to both ends of this front wheel rack shaft IO via a tie rod 11 and a knuckle arm 12. A rack 14 is formed on the front wheel rack shaft 1o, and this rack 1
4 is engaged with a binion 16 of a front wheel binion shaft 15. The pinion shaft 15 is rotatably connected to a handle 18 via a rotary valve 17. A piston 20 that slides within a cylinder tube 19 is attached to the front wheel rack shaft 10. The aforementioned front wheel rack shaft 10
A front wheel steering device 21 is formed by the pinion shaft 15, rotary valve 17, cylinder tube 19, and piston 20.
is configured.
２５は後輪用ラック軸であり、この後輪用ラック軸２５
の両端にはタイロッド２６とナックルアーム２７を介し
て後輪２８が連結されている。後輪用ラック軸２５には
うツク２９が形成され、このラック２９に後輪用ピニオ
ン軸３０のビニオン３１が噛合されている。ピニオン軸
３０はロータリーバルブ３２とアシスト遅れ時の回避装
置３３と操舵特性装置３４を介してプーリ３５に回転連
結されている。前記後輪用ラック軸２５にはシリンダチ
ューブ３６内を摺動するピストン３７が取付けられてい
る。前述した後輪用ラック軸２５とピニオン軸３０とロ
ータリーバルブ３２とアシスト遅れ時の回避装置３３と
操舵特性装置３４とプーリ３５とによって後輪操舵装置
３８が構成される。25 is a rear wheel rack shaft;
A rear wheel 28 is connected to both ends of the rear wheel 28 via a tie rod 26 and a knuckle arm 27. A rack 29 is formed on the rear wheel rack shaft 25, and a pinion 31 of a rear wheel pinion shaft 30 is meshed with this rack 29. The pinion shaft 30 is rotationally connected to a pulley 35 via a rotary valve 32, an assist delay avoidance device 33, and a steering characteristic device 34. A piston 37 that slides within a cylinder tube 36 is attached to the rear wheel rack shaft 25. A rear wheel steering device 38 is constituted by the rear wheel rack shaft 25, pinion shaft 30, rotary valve 32, assist delay avoidance device 33, steering characteristic device 34, and pulley 35 described above.
前輪用ラック軸１０の両端には２本のケーブル巻きつけ
られている。２本のケーブル４０．４１の途中には回路
の中間ローラが設けられ、この中間ローラによってケー
ブル４０．４１が通過する場所が制限されるようになっ
ている。２本のケーブル４０．４１の途中にはケーブル
４０．４１の伸びによる撓みを吸収するため、ケーブル
長さ調整装置４２が設けられている。Two cables are wound around both ends of the front wheel rack shaft 10. An intermediate roller of the circuit is provided in the middle of the two cables 40.41, and the intermediate roller limits the location through which the cables 40.41 pass. A cable length adjustment device 42 is provided in the middle of the two cables 40.41 in order to absorb the bending caused by the extension of the cables 40.41.
４５は自動車のエンジンであり、このエンジン４５のよ
ってＰＳポンプ４６が駆動されるようになっている。Ｐ
Ｓポンプ４６によってリザーバ４７から汲み上げられた
油は分流制御弁４８によって分流され、分流された一方
の油は前輪側のロータリーサーボ弁１７に導かれ、分流
された他方の油は後輪側のロータリーサーボ弁３２に導
かれるようになっている。各ロータリーサーボ弁１７゜
３２はシリンダチューブ１９．３６の左右室に接続され
、またリザーバ４７に接続されている。Reference numeral 45 denotes an automobile engine, and the PS pump 46 is driven by this engine 45. P
The oil pumped up from the reservoir 47 by the S pump 46 is divided by the flow control valve 48, one of the divided oil is guided to the rotary servo valve 17 on the front wheel side, and the other divided oil is guided to the rotary servo valve 17 on the rear wheel side. It is designed to be guided to a servo valve 32. Each rotary servo valve 17.32 is connected to the left and right chambers of the cylinder tube 19.36, and is also connected to the reservoir 47.
第１図において、５０は後輪操舵装置３８の後輪用ハウ
ジングを示すものであり、この後輪用ハウジング５０に
後輪用ラック軸２５が挿通されている。また後輪用ハウ
ジング５０にはピニオン軸３０が後輪用ラック軸２５と
略直交する軸線回りに回転可能に軸承され、ピニオン軸
３０にトーションバー５１の一端が連結されている。ト
ーションバー５１の他端は作動軸５２に連結され、この
作動軸５２は後輪用ハウジング５０とピニオン軸３０に
回転可能に軸承されている。作動軸５２にはロータリー
バルブ３８のインナーバルブ５３が一体形成され、ピニ
オン軸３０にはロータリーパルプ３８のアウターパルプ
５４がピン５５を介して連結されている。後輪用ハウジ
ング５０には第１回転部材５６と第２回転部材５７と第
３回転部材（出力軸）５８がピニオン軸３０と同軸回り
に回転可能に軸承され、作動軸５２と第１回転部材５６
とはピン５９を介して回転連結されている。In FIG. 1, 50 indicates a rear wheel housing of the rear wheel steering device 38, and the rear wheel rack shaft 25 is inserted through this rear wheel housing 50. Further, a pinion shaft 30 is supported on the rear wheel housing 50 so as to be rotatable about an axis substantially perpendicular to the rear wheel rack shaft 25, and one end of a torsion bar 51 is connected to the pinion shaft 30. The other end of the torsion bar 51 is connected to an operating shaft 52, which is rotatably supported by the rear wheel housing 50 and the pinion shaft 30. An inner valve 53 of the rotary valve 38 is integrally formed on the operating shaft 52, and an outer pulp 54 of the rotary pulp 38 is connected to the pinion shaft 30 via a pin 55. A first rotating member 56, a second rotating member 57, and a third rotating member (output shaft) 58 are rotatably supported on the rear wheel housing 50 about the same axis as the pinion shaft 30, and the operating shaft 52 and the first rotating member are rotatably supported on the rear wheel housing 50. 56
and are rotationally connected via a pin 59.
第１回転部材５６には第１保合部材６０が回転可能に軸
承され、この第１保合部材６０は第４図において半径内
方へ突出した第１回転部材５６の突起部５６ａに時計回
りに係合し、また半径内方へ突出した第２回転部材５７
の突起部５７ａに時計方向に係合している。第３回転部
材５８には第２保合部材６１が回転可能に軸承され、こ
の第２保合部材６１は第３図において半径内方へ突出し
た第２回転部材５７の突起部５７ｂに時計回りに係合し
、また第３回転部材５８の端面より突設されたピン５８
ａに時計方向に係合している。第１回転部材５６と第２
回転部材５７間には第１うす巻きバネ６２が配置され、
この第１うす巻きバネ６２の外端は第１回転部材５６と
第２回転部材５７に第４図の反時計回りに係合し、第１
うず巻きバネ６２の内端は第１係合部材６０に時計回り
に係合している。第２回転部材５７と第３回転部材５８
間には第２うす巻きバネ６３が配置され、この第２うず
巻きバネ６３の外端は第２回転部材５７と第３回転部材
５８に第３図の反時計回りに係合し、第２うず巻きバネ
６３の内端は第２保合部材６１に時計回りに係合してい
る。第１回転部材５６と第２回転部材５７と第３回転部
材５８と第１係合部材６０と第２係合部材６１と第１う
す巻きバネ６２と第２うす巻きバネ６３とによって脱輪
によって後輪２８が操舵されないとき、ケーブル４０．
４１を引っ張る力を逃がすアシスト遅れ時の回避装置３
３が構成される。A first retaining member 60 is rotatably supported on the first rotary member 56, and the first retaining member 60 is rotated clockwise by a protrusion 56a of the first rotary member 56 that protrudes radially inward in FIG. a second rotary member 57 that engages with and projects radially inward;
It is engaged clockwise with the protrusion 57a of. A second retaining member 61 is rotatably supported on the third rotating member 58, and the second retaining member 61 is rotated clockwise by the projection 57b of the second rotating member 57 that protrudes radially inward in FIG. A pin 58 is engaged with the pin 58 and protrudes from the end surface of the third rotating member 58.
a clockwise. The first rotating member 56 and the second
A first thinly wound spring 62 is arranged between the rotating members 57,
The outer end of the first thinly wound spring 62 engages with the first rotating member 56 and the second rotating member 57 in the counterclockwise direction in FIG.
The inner end of the spiral spring 62 is engaged with the first engagement member 60 in a clockwise direction. Second rotating member 57 and third rotating member 58
A second thin spiral spring 63 is disposed therebetween, and the outer end of the second spiral spring 63 engages with the second rotating member 57 and the third rotating member 58 counterclockwise in FIG. The inner end of the spring 63 is engaged with the second retaining member 61 in a clockwise direction. The first rotating member 56, the second rotating member 57, the third rotating member 58, the first engaging member 60, the second engaging member 61, the first thinly wound spring 62, and the second thinly wound spring 63 cause the wheel to come off. When rear wheel 28 is not steered, cable 40.
Avoidance device 3 when assist is delayed to release the force that pulls 41
3 is composed.
第３回転部材５８にはこの第３回転部材５８の回転中心
からＡだけ偏心した位置に偏心ピン６５が第３回転部材
５８の回転軸線と平行に取付けられ、この偏心ピン６５
は回転可能なローラ６５ａを備えている。後輪用ハウジ
ング５０にプーリ（入力軸）３５が第３回転部材５８の
回転中心からＢだけ偏心した位置に第３回転部材５８の
回転軸線と平行に回転可能に軸承されている。プーリ３
５には前記偏心ビン６５が係合する係合溝６６が第５図
に示すように半径方向に形成され、この係合溝６６は、
プーリ（入力軸）３５と第３回転部材（出力軸）５８の
中立状態においてブーＩ７３５の回転中心と第３回転部
材５８の回転中心を結ぶ線上に形成される。前記偏心量
Ａは偏心量Ｂより大きめに設定されている。プーリ３５
にはケーブル４０とケーブル４１がそれぞれ巻き付けら
れている。前記第３回転部材（出力軸）５８と偏心ピン
６５と係合溝６６とプーリ（入力軸）３５とによって操
舵特性装置３４が構成され、入力軸３５の回転角に対す
る出力軸５８の回転角の特性が第６図に示すように変え
られる。即ち、入力軸３５の回転角が少ない時は、出力
軸５８がほとんど回転しない。入力軸３５の回転角が多
くなると、出力軸５日の回転角が急激に上昇するような
操舵特性が得られる。An eccentric pin 65 is attached to the third rotating member 58 at a position offset by A from the rotation center of the third rotating member 58 and parallel to the rotational axis of the third rotating member 58.
is equipped with a rotatable roller 65a. A pulley (input shaft) 35 is rotatably supported on the rear wheel housing 50 at a position offset by B from the rotation center of the third rotation member 58 in parallel to the rotation axis of the third rotation member 58. Pulley 3
As shown in FIG. 5, an engagement groove 66 with which the eccentric pin 65 engages is formed in the radial direction.
It is formed on a line connecting the rotation center of the boot I 735 and the rotation center of the third rotation member 58 when the pulley (input shaft) 35 and the third rotation member (output shaft) 58 are in a neutral state. The eccentricity A is set to be larger than the eccentricity B. Pulley 35
A cable 40 and a cable 41 are wound around the cable 40 and the cable 41, respectively. The third rotating member (output shaft) 58, the eccentric pin 65, the engagement groove 66, and the pulley (input shaft) 35 constitute a steering characteristic device 34, which determines the rotation angle of the output shaft 58 with respect to the rotation angle of the input shaft 35. The characteristics are changed as shown in FIG. That is, when the rotation angle of the input shaft 35 is small, the output shaft 58 hardly rotates. When the rotation angle of the input shaft 35 increases, a steering characteristic is obtained in which the rotation angle of the output shaft 5 rapidly increases.
次に上述した構成に基づいて作用について説明する、ハ
ンドル１８を操舵するとこのハンドル１８の操舵がロー
タリーバルブ１７０入方側に伝えられ、ロークリバルブ
１７の入力側とピニオン軸１５との間で相対回転が生ず
ると分流制御弁４８によって分流された油はシリンダチ
ューブ１９の一方の室に供給される。この結果、前輪用
ラック軸１０は例えば矢印Ｈ方向に軸移動し、前輪１３
が第２図において時計回りに操向され、シリンダチュー
ブ１９の他方の室から出た油はロータリバルブ１７を介
してリザーバ；；に回収される。前輪用ラック軸１０の
軸方向の移動によってケーブル４０．４１の一方が引っ
張られ、他方が緩められる。ケーブル４０．４１の一方
が引っ張られることによってプーリ３５が一方向に回転
し、プーリ３５の回転によって前記ケーブル４０．４１
の他方が引っ張られる。またプーリ３５の回転によって
保合溝６６と偏心ピン６５を介して第３回転部材５８が
回転し、この第３回転部材５８の回転は第２うず巻きバ
ネ６３と第２回転部材５７と第１うす巻きバネ６２と第
１回転部材５６とピン５９を介して作動軸５２に伝えら
れる。作動軸５２０回転はトーションバー５１とピニオ
ン軸３０に伝えられ、作動軸５３とピニオン軸３０との
間で相対回転が生ずるとロークリバルブ３８が作動し、
分流制御弁４ｔによって分流された油はシリンダチュー
ブ３６の一方に供給される。この結果、後輪用ラック軸
２５を矢印Ｊ方向に軸移動させ、後輪２８を前輪１３と
逆方向、即ち第１図において反時計回りに操向する。高
速走行時は、ハンドル１８の操舵角が少ないため、操舵
特性装置３４によって第３回転部材５８が殆ど回転せず
、後輪２８は操向されない。逆に低速走行時は、ハンド
ル１８の操舵角が多いため、操舵特性装置３４によって
第３回転部材５８が多く回転され、後輪２８が前輪１３
と逆方向に大きく操向される。Next, the operation will be explained based on the above-mentioned configuration. When the handle 18 is steered, the steering of the handle 18 is transmitted to the input side of the rotary valve 170, and relative rotation is caused between the input side of the rotary valve 17 and the pinion shaft 15. When this occurs, the oil diverted by the diversion control valve 48 is supplied to one chamber of the cylinder tube 19. As a result, the front wheel rack shaft 10 is moved, for example, in the direction of arrow H, and the front wheel 13
is steered clockwise in FIG. 2, and the oil coming out of the other chamber of the cylinder tube 19 is collected into the reservoir via the rotary valve 17. The axial movement of the front wheel rack axle 10 tensions one cable 40, 41 and loosens the other. When one of the cables 40.41 is pulled, the pulley 35 rotates in one direction, and the rotation of the pulley 35 causes the cable 40.41 to rotate in one direction.
The other side is pulled. Further, the rotation of the pulley 35 rotates the third rotating member 58 via the retaining groove 66 and the eccentric pin 65, and the rotation of the third rotating member 58 is caused by the rotation of the second spiral spring 63, the second rotating member 57, and the first thin member. It is transmitted to the operating shaft 52 via the coiled spring 62, the first rotating member 56, and the pin 59. The rotation of the operating shaft 520 is transmitted to the torsion bar 51 and the pinion shaft 30, and when relative rotation occurs between the operating shaft 53 and the pinion shaft 30, the rotary valve 38 is activated.
The oil separated by the separation control valve 4t is supplied to one side of the cylinder tube 36. As a result, the rear wheel rack shaft 25 is moved in the direction of arrow J, and the rear wheels 28 are steered in the opposite direction to the front wheels 13, that is, counterclockwise in FIG. When the vehicle is running at high speed, the steering angle of the steering wheel 18 is small, so the third rotating member 58 is hardly rotated by the steering characteristic device 34, and the rear wheels 28 are not steered. On the contrary, when driving at low speed, the steering angle of the steering wheel 18 is large, so the third rotating member 58 is rotated more by the steering characteristic device 34, and the rear wheel 28 is rotated more than the front wheel 13.
is steered significantly in the opposite direction.
後輪２８の脱輪等によって作動軸５２の回転が阻止され
た状態で、ハンドル１８の操舵により第３回転部材５８
とピン５８ａを第３図の時計回りに回転させると第２う
す巻きバネ６３の外端が時計回りに回転する。この結果
、第２うず巻きバネ６３の内端には突起部５７ｂを介し
て第２回転部材５７を時計回りに回転させようとするカ
が作用し、さらに第４図において第１うす巻きバネ６２
を介して突起部５６ａと第１回転部材５６を時計回りに
回転させようとする力が作用する。第１うす巻きバネ６
２と第２うす巻きバネ６３の力が同じであるときは、第
２回転部材５７が第３回転部材５８と同方向に１／２だ
け回転し、第１．第２うす巻きバネ６２．６３の巻き量
が増加する。With the rotation of the operating shaft 52 being prevented due to the rear wheel 28 coming off, etc., the third rotating member 58 is rotated by steering the handle 18.
When the pin 58a is rotated clockwise in FIG. 3, the outer end of the second thinly wound spring 63 is rotated clockwise. As a result, a force that attempts to rotate the second rotating member 57 clockwise acts on the inner end of the second spiral spring 63 via the protrusion 57b, and furthermore, as shown in FIG.
A force that attempts to rotate the protrusion 56a and the first rotating member 56 clockwise acts through the protrusion 56a. First thinly wound spring 6
2 and the second thinly wound spring 63 are the same, the second rotating member 57 rotates by 1/2 in the same direction as the third rotating member 58, and the second rotating member 57 rotates by 1/2 in the same direction as the third rotating member 58. The amount of winding of the second thinly wound springs 62 and 63 increases.
逆に後輪２８の脱輪等によって作動軸５２の回転が阻止
された状態で、ハンドル１８の操舵により第３回転部材
５８とピン５８ａを第３図の反時計回りに回転させると
第２うず巻きバネ６３の内端が反時計回りに回転する。Conversely, when the rotation of the operating shaft 52 is blocked due to the rear wheel 28 coming off, etc., if the third rotating member 58 and the pin 58a are rotated counterclockwise in FIG. 3 by steering the handle 18, the second spiral winding occurs. The inner end of spring 63 rotates counterclockwise.
この結果、第２うす巻きバネ６３の外端には第２回転部
材５７を反時計回りに回転させようとする力が作用し、
さらに第４図において第１うす巻きバネ６２を介して第
１回転部材５６を反時計回りに回転させようとする力が
作用する。よって、第２回転部材５７が第３回転部材５
８と同方向に１／２だけ回転し、第１、第２うず巻きバ
ネ６２．６３の巻き量が増加する。As a result, a force that attempts to rotate the second rotating member 57 counterclockwise acts on the outer end of the second thinly wound spring 63,
Further, in FIG. 4, a force is applied via the first thinly wound spring 62 to rotate the first rotating member 56 counterclockwise. Therefore, the second rotating member 57 is the third rotating member 5.
8, and the amount of winding of the first and second spiral springs 62 and 63 increases.
なお第７図と第８図は他の変形例として前輪縁！
舵装置２１にアシスト遅れ時の回避装置７引と操舵特性
装置７繁を設けた例を示すもので、前輪用ラック軸７２
の軸移動は、中間ピニオン軸７３と操舵特性装置７１と
アシスト遅れ時の回避装置７０と前輪用プーリ７４とケ
ーブル７５．７６と後輪用ブー１Ｊ７７を介して後輪用
のロークリバルブ３８に伝えられる。前輪用ハウジング
８０には前輪用ラック軸７２が挿通され、この前輪用ラ
ック軸７２に噛み合う中間ピニオン軸（入力軸）７３が
前輪用ハウジング８０に回転可能に軸承されている。ま
た前輪用ハウジング８０には中間ピニオン軸７３の回転
中心からしだけ偏心した位置に第１回転部材（出力軸）
８１と第２回転部材８２と第３回転部材８３が中間ピニ
オン軸７３の回転軸線と平行な軸線回りに回転可能に軸
承されている。In addition, Figures 7 and 8 show the front wheel edge as another modification! This shows an example in which the steering device 21 is provided with an assist delay avoidance device 7 and a steering characteristic device 7.
The axis movement is transmitted to the rear wheel low-return valve 38 via the intermediate pinion shaft 73, the steering characteristic device 71, the assist delay avoidance device 70, the front wheel pulley 74, the cable 75, 76, and the rear wheel boolean 1J77. . A front wheel rack shaft 72 is inserted through the front wheel housing 80, and an intermediate pinion shaft (input shaft) 73 that meshes with the front wheel rack shaft 72 is rotatably supported by the front wheel housing 80. Further, in the front wheel housing 80, a first rotating member (output shaft) is located at a position eccentric from the rotation center of the intermediate pinion shaft 73.
81, a second rotating member 82, and a third rotating member 83 are rotatably supported around an axis parallel to the rotational axis of the intermediate pinion shaft 73.
中間ピニオン軸７３には半径方向に係合溝８４が形成さ
れ、この係合溝８４に係合する偏心ピン８５が第１回転
部材８１に第１回転部材８１の回転中心からＭだけ偏心
した位置に取付けられている。An engagement groove 84 is formed in the intermediate pinion shaft 73 in the radial direction, and an eccentric pin 85 that engages with the engagement groove 84 is located at a position eccentric to the first rotating member 81 by M from the center of rotation of the first rotating member 81. installed on.
前記偏心量りは偏心量Ｍより小さい。第１回転部材８１
と第２回転部材８２間には第１うす巻きバネ８６が配置
され、第２回転部材８２と第３回転部材８３間には第２
うず巻きバネ８７が配置されている。第３回転部材８３
には前輪用プーリ７４が一体形成されている。The eccentricity measure is smaller than the eccentricity M. First rotating member 81
A first thin coil spring 86 is disposed between the second rotating member 82 and the second rotating member 82, and a second thin coil spring 86 is disposed between the second rotating member 82 and the third rotating member 83.
A spiral spring 87 is arranged. Third rotating member 83
A front wheel pulley 74 is integrally formed with the front wheel pulley 74.
〈発明の効果〉
以上述べたように本発明は、出力軸と入力軸を互いに偏
心させた状態でハウジングに回転可能に軸承し、入力軸
に半径方向に係合溝を形成し、この係合溝に係合する偏
心ピンを入力軸に対する出力軸の偏心量より多い量で出
力軸に対して偏心した位置に出力軸に取付けた構成であ
るので、前輪の操舵角が少ない時は、後輪はほとんど操
舵されないため、高速走行に適する効果が得られる。<Effects of the Invention> As described above, the present invention has an output shaft and an input shaft that are eccentrically supported in a housing so as to be rotatable, an engagement groove is formed in the input shaft in the radial direction, and an engagement groove is formed in the input shaft. The configuration is such that the eccentric pin that engages with the groove is attached to the output shaft at a position that is eccentric to the output shaft by an amount greater than the amount of eccentricity of the output shaft to the input shaft, so when the steering angle of the front wheels is small, the rear wheels Since the vehicle is hardly steered, it produces an effect suitable for high-speed driving.
図面は本発明の実施例を示すもので、第１図は後輪操舵
装置の断面図、第２図は４輪操舵装置の全体システム図
、第３図は第１図において■−■線で断面した図、第４
図は第１図においてＩＶ−ＩＶ線で断面した図、第５図
は第１図において■−Ｖ線で断面した図、第６図は操舵
特性線図、第７図は他の変形例としての４輪操舵装置の
全体システム図、第８図は他の変形例としての前輪操舵
装置の断面図。
１０．７２・・・前輪用ラック軸、１３・・・前輪、ｌ
７・・・ロータリーバルブ、１９・・・シリンダチュ
ーブ、２０・・・ピストン、２１・・・前輪操舵装置、
２５・・・後輪用ラック軸、２８・・・後輪、３０・・
・後輪用ピニオン軸、３２・・・ロータリーパルプ、３
３．７１・・・アシスト遅れ時の回避装置、３４．７０
・・・操舵特性装置、３５・・・プーリ（入力軸）、３
６・・・シリンダチューブ、３８・・・後輪操舵装置、
４０．４１．７５．７６・・・ケーブル、５０・・・後
輪用ハウジング、５１・・・トーションバー、５２・・
・作動軸、５８・・・第３回転部材（出力軸）、６５．
８５・・・偏心ピン、６６．８４・・・係合溝、７３・
・・中間ピニオン軸、８０・・・前輪用ハウジング、８
１・・・第１回転部材（出力軸）。The drawings show an embodiment of the present invention, and FIG. 1 is a cross-sectional view of a rear wheel steering device, FIG. 2 is an overall system diagram of a four-wheel steering device, and FIG. Sectional view, No. 4
The figure is a cross-sectional view taken along the IV-IV line in Figure 1, Figure 5 is a cross-sectional view taken along the ■-V line in Figure 1, Figure 6 is a steering characteristic diagram, and Figure 7 is a diagram showing another modification. FIG. 8 is a sectional view of a front wheel steering device as another modification. 10.72... Front wheel rack shaft, 13... Front wheel, l
7... Rotary valve, 19... Cylinder tube, 20... Piston, 21... Front wheel steering device,
25... Rack shaft for rear wheels, 28... Rear wheels, 30...
・Pinion shaft for rear wheels, 32...Rotary pulp, 3
3.71...Avoidance device for assist delay, 34.70
... Steering characteristic device, 35 ... Pulley (input shaft), 3
6... Cylinder tube, 38... Rear wheel steering device,
40.41.75.76... Cable, 50... Rear wheel housing, 51... Torsion bar, 52...
- Operating shaft, 58...Third rotating member (output shaft), 65.
85...Eccentric pin, 66.84...Engagement groove, 73...
...Intermediate pinion shaft, 80...Front wheel housing, 8
1... First rotating member (output shaft).
Claims (2)
後輪操舵装置を設け、前輪操舵装置の作動をケーブルを
介して後輪操舵装置に伝えるようにした４輪操舵装置に
おいて、前記後輪操舵装置の後輪用ハウジングに後輪側
の出力軸を回転可能に軸承し、この出力軸に出力軸の回
転中心から偏心した位置に偏心ピンを取付け、後輪用ハ
ウジングにケーブル側の入力軸を出力軸に対する偏心ピ
ンの偏心量よりも少ない量で出力軸に対して偏心した位
置に回転可能に軸承し、この入力軸に前記偏心ピンが係
合する係合溝を半径方向に形成したことを特徴とする４
輪操舵装置。(1) In a four-wheel steering device, the four-wheel steering device is provided with a front wheel steering device that steers the front wheels and a rear wheel steering device that steers the rear wheels, and the operation of the front wheel steering device is transmitted to the rear wheel steering device via a cable. The output shaft on the rear wheel side is rotatably supported on the rear wheel housing of the rear wheel steering device, and an eccentric pin is attached to the output shaft at a position eccentric from the rotation center of the output shaft. The input shaft is rotatably supported at a position eccentric to the output shaft by an amount smaller than the eccentricity of the eccentric pin with respect to the output shaft, and an engagement groove in which the eccentric pin engages is formed in the input shaft in the radial direction. 4 characterized by having done
Wheel steering device.
後輪操舵装置を設け、前輪操舵装置の作動をケーブルを
介して後輪操舵装置に伝えるようにした４輪操舵装置に
おいて、前記前輪操舵装置の前輪用ハウジングに前輪側
の入力軸を回転可能に軸承し、この入力軸に半径方向に
係合溝を形成し、前輪用ハウジングにケーブル側の出力
軸を入力軸に対して偏心した位置に回転可能に軸承し、
この出力軸に前記係合溝に係合する偏心ピンを入力軸に
対する出力軸の偏心量よりも多い量で出力軸に対して偏
心した位置に取付けたことを特徴とする４輪操舵装置。(2) In the four-wheel steering device, the four-wheel steering device is provided with a front wheel steering device that steers the front wheels and a rear wheel steering device that steers the rear wheels, and the operation of the front wheel steering device is transmitted to the rear wheel steering device via a cable. The input shaft on the front wheel side is rotatably supported on the front wheel housing of the front wheel steering device, an engagement groove is formed in the radial direction on this input shaft, and the output shaft on the cable side is eccentrically mounted on the front wheel housing with respect to the input shaft. rotatably supported in the position
A four-wheel steering device characterized in that an eccentric pin that engages with the engagement groove is attached to the output shaft at a position that is eccentric with respect to the output shaft by an amount greater than the eccentricity of the output shaft with respect to the input shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP429989A JP2552348B2 (en) | 1989-01-11 | 1989-01-11 | 4-wheel steering system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP429989A JP2552348B2 (en) | 1989-01-11 | 1989-01-11 | 4-wheel steering system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH02185865A true JPH02185865A (en) | 1990-07-20 |
| JP2552348B2 JP2552348B2 (en) | 1996-11-13 |
Family
ID=11580635
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP429989A Expired - Fee Related JP2552348B2 (en) | 1989-01-11 | 1989-01-11 | 4-wheel steering system |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2552348B2 (en) |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63154469A (en) * | 1986-12-18 | 1988-06-27 | Toyota Motor Corp | Rear wheel steering device for front and rear wheel steering vehicle |
| JPS63258271A (en) * | 1987-04-15 | 1988-10-25 | Hino Motors Ltd | Front/rear wheel steering system for vehicle |
-
1989
- 1989-01-11 JP JP429989A patent/JP2552348B2/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63154469A (en) * | 1986-12-18 | 1988-06-27 | Toyota Motor Corp | Rear wheel steering device for front and rear wheel steering vehicle |
| JPS63258271A (en) * | 1987-04-15 | 1988-10-25 | Hino Motors Ltd | Front/rear wheel steering system for vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2552348B2 (en) | 1996-11-13 |
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