JPS6149147B2 - - Google Patents
Info
- Publication number
- JPS6149147B2 JPS6149147B2 JP11455378A JP11455378A JPS6149147B2 JP S6149147 B2 JPS6149147 B2 JP S6149147B2 JP 11455378 A JP11455378 A JP 11455378A JP 11455378 A JP11455378 A JP 11455378A JP S6149147 B2 JPS6149147 B2 JP S6149147B2
- Authority
- JP
- Japan
- Prior art keywords
- ball screw
- shaft
- screw shaft
- liquid
- piston
- 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
- 239000007788 liquid Substances 0.000 claims description 67
- 230000005540 biological transmission Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000007935 neutral effect Effects 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 230000000452 restraining effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000035807 sensation Effects 0.000 description 1
- 239000013585 weight reducing agent Substances 0.000 description 1
Landscapes
- Power Steering Mechanism (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は回転型サーボ制御弁を備えた車両の動
力舵取装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a power steering system for a vehicle equipped with a rotary servo control valve.
従来、この種の動力舵取装置として、実公昭53
−20097号公報に開示されるものがある。これは
第1図に示すように、ボールねじ軸10のつば部
10aの外周にピン孔66を設け、かつその外周
に、一部切欠62を設けた外スリーブ6を嵌合し
てピン孔66と切欠62とを一致させ、径方向に
ピン63を圧入して結合されている。操舵時には
ピストン12の軸方向の動きと同時に液圧が発生
し、前記ボールねじ軸10と外スリーブ6にも軸
方向の荷重がかかる。この荷重による外スリーブ
6とボールねじ軸10との運動を防止するため
に、一方はシリンダ13の端壁32へボールねじ
軸10の端部を軸受43を介して当て、他方は弁
ハウジング17のねじ穴にプラグ64をねじ込
み、これに軸受15を介して外スリーブ6を押し
当て、プラグ64の締付けによりつば部10aと
外スリーブ6との突合せ面に予荷重を与えている
が、これは次のような欠点がある。
Conventionally, as this type of power steering device,
-There is something disclosed in Publication No. 20097. As shown in FIG. 1, a pin hole 66 is provided on the outer periphery of the collar portion 10a of the ball screw shaft 10, and an outer sleeve 6 having a partial notch 62 is fitted to the outer periphery of the pin hole 66. and the notch 62, and the pin 63 is press-fitted in the radial direction to connect them. During steering, hydraulic pressure is generated simultaneously with the axial movement of the piston 12, and an axial load is also applied to the ball screw shaft 10 and the outer sleeve 6. In order to prevent movement of the outer sleeve 6 and the ball screw shaft 10 due to this load, one end of the ball screw shaft 10 is applied to the end wall 32 of the cylinder 13 via a bearing 43, and the other is of the valve housing 17. A plug 64 is screwed into the screw hole, and the outer sleeve 6 is pressed against it through the bearing 15. By tightening the plug 64, a preload is applied to the abutting surface between the collar portion 10a and the outer sleeve 6. There are drawbacks such as.
(a) ボールねじ軸10のつば部10a及び弁部
(外スリーブ)の軸方向の軸受15により弁ハ
ウジング部が外径及び長さとも大型となり軽量
化に問題がある。(a) Due to the collar portion 10a of the ball screw shaft 10 and the axial bearing 15 of the valve portion (outer sleeve), the valve housing portion becomes large in both outer diameter and length, which poses a problem in weight reduction.
(b) 操舵時に軸方向に荷重がかかり、弁作動以外
の不必要な力がかかり、作動が不円滑となり、
操舵感覚が悪くなる。(b) When steering, a load is applied in the axial direction, and unnecessary force other than valve operation is applied, resulting in unsmooth operation.
Steering sensation deteriorates.
(c) ボールねじ軸10の軸方向の動きは先端部を
軸受43により基端部を外スリーブ6を介して
軸受15により支持されるが、車輪からの外力
がピストン12を介してボールねじ軸10に作
用すると、この外力は外スリーブ6に作用し、
これに不円滑な運動をもたらし、これが操舵感
覚に悪影響を及ぼす。(c) The axial movement of the ball screw shaft 10 is supported by the bearing 43 at the distal end and the bearing 15 through the outer sleeve 6 at the base end, but the external force from the wheel moves through the piston 12 to the ball screw shaft. 10, this external force acts on the outer sleeve 6,
This results in an unsmooth movement, which adversely affects the steering feel.
また、特公昭51−2178号公報に開示されるよ
うな動力舵取装置では、1個の4点支持軸受を
もつてシリンダの端壁にボールねじ軸が支持さ
れているが、ボールねじ軸の4点支持軸受に隣
接する部分に弁要素が形成されているので、車
輪の外力はピストンからボールねじ軸の弁要素
を経て4点支持軸受でシリンダの端壁に受け止
められることとなり、弁要素が外力の伝達経路
内に配設されるために外力により弁要素に不円
滑な運動が引き起され、操舵感覚に悪影響を及
ぼす。 Furthermore, in the power steering device disclosed in Japanese Patent Publication No. 51-2178, the ball screw shaft is supported on the end wall of the cylinder with one four-point support bearing. Since the valve element is formed in the area adjacent to the four-point support bearing, the external force from the wheel passes from the piston to the valve element on the ball screw shaft, and is received by the end wall of the cylinder at the four-point support bearing. Since the valve element is disposed in the transmission path of the external force, the external force causes an uneven movement of the valve element, which adversely affects the steering feel.
そこで、本発明の目的は上述の問題に鑑み、車
輪からの外力がボールねじ軸の弁要素に伝達され
ないようにし、弁要素の円滑な動作が常に維持さ
れる、構成が簡単で小型の動力舵取装置を提供す
ることにある。
SUMMARY OF THE INVENTION In view of the above-mentioned problems, an object of the present invention is to provide a small-sized power rudder with a simple configuration, which prevents external force from the wheels from being transmitted to the valve element of the ball screw shaft, and maintains smooth operation of the valve element at all times. The objective is to provide a device for removing
上記目的を達成するために、本発明の構成は一
部外周に設けたラツクが出力歯車軸と噛み合つて
いるピストンと、該ピストンにより区画される1
対の液室を有するシリンダとを有し、操舵軸と前
記ピストンに螺合したボールねじ軸とが可撓軸を
もつて連結され、該ボールねじ軸に結合された円
筒形の第1弁要素と前記操舵軸に一体に形成され
かつ前記第1弁要素に嵌合された第2弁要素と
が、前記可撓軸のねじれにより前記1対の液室の
一方を液圧源に、他方を液槽にそれぞれ連通する
液圧回路を形成する動力舵取装置において、前記
ボールねじ軸の先端部に内輪を形成するフランジ
を一体に形成し、該内輪を含む4点支持軸受によ
り前記ボールねじ軸を前記シリンダの端壁部に軸
方向および径方向不動に支持するとともに、前記
ボールねじ軸と、前記操舵軸との各外経をほぼ同
寸法とし、前記ボールねじ軸の基端部に前記第1
弁要素を外嵌し、かつ径方向のピンにより回転結
合したものである。
In order to achieve the above object, the present invention includes a piston having a rack partially provided on the outer periphery that meshes with the output gear shaft, and a piston partitioned by the piston.
a cylinder having a pair of liquid chambers, a steering shaft and a ball screw shaft screwed onto the piston are connected through a flexible shaft, and a cylindrical first valve element is coupled to the ball screw shaft. and a second valve element integrally formed with the steering shaft and fitted into the first valve element, by twisting the flexible shaft, one of the pair of liquid chambers is used as a hydraulic pressure source and the other is used as a hydraulic pressure source. In a power steering device that forms a hydraulic circuit that communicates with each liquid tank, a flange forming an inner ring is integrally formed at the tip of the ball screw shaft, and a four-point support bearing including the inner ring allows the ball screw shaft to is supported immovably in the axial and radial directions on the end wall of the cylinder, and the outer dimensions of the ball screw shaft and the steering shaft are approximately the same, and the ball screw shaft is provided with a base end of the ball screw shaft. 1
The valve element is fitted onto the outside and rotationally connected with a radial pin.
ボールねじ軸10の先端部が4点支持軸受43
をもつてシリンダの端壁32に支持される一方、
ボールねじ軸10の基端部に弁要素である外スリ
ーブ6が支持されるので、車輪からの外力がピス
トン12を経てボールねじ軸10に伝達される
と、4点支持軸受43により受け止められる。外
スリーブ6は外力の伝達経路外にあるので、非常
に円滑な制御弁の動作が得られる。
The tip of the ball screw shaft 10 is a four-point support bearing 43
while being supported on the end wall 32 of the cylinder with
Since the outer sleeve 6, which is a valve element, is supported at the base end of the ball screw shaft 10, when external force from the wheel is transmitted to the ball screw shaft 10 via the piston 12, it is received by the four-point support bearing 43. Since the outer sleeve 6 is outside the external force transmission path, very smooth operation of the control valve can be achieved.
以下本発明を図に示す実施例について説明す
る。第2図に示すように、まず、動力舵取装置は
端壁32と弁ハウジング17とにより閉鎖される
シリンダ13内に、一部外周にラツク18を備え
るピストン12を嵌装し、該ラツク18に操向車
輪に偏向動力を伝達する歯車軸19を噛合させる
一方、ピストン12の軸心にはボール11を介し
て中空のボールねじ軸10を螺合し、該ボールね
じ軸10の基端中空部に軸受38を介して操舵軸
1の先端を相対回転可能に支持するとともに、前
記ボールねじ軸10の中空部に可撓軸8を挿通
し、この先端をピン44をもつてボールねじ軸1
0の先端と回転結合し、基端をピン3をもつて操
舵軸1と回転結合し、またボールねじ軸10の先
端を4点支持軸受43により端壁32に支持し、
操舵軸1を軸受35をもつて弁ハウジング17の
軸孔に支持され、前記操舵軸1を回転する時、ボ
ールねじ軸10が受ける操向車輪の抗力によつて
生じる可撓軸8のねじれを利用してサーボ制御弁
の2個の弁要素間に回転差動を発生させ、ピスト
ン12によつて2分されるシリンダの液室A,B
の一方に液圧を付与し、ボールねじ軸10の回転
を容易にする方向にピストン12を押動するもの
である。
The present invention will be described below with reference to embodiments shown in the drawings. As shown in FIG. 2, the power steering device is constructed by first fitting a piston 12 with a rack 18 on a part of its outer periphery into a cylinder 13 that is closed by an end wall 32 and a valve housing 17. A gear shaft 19 that transmits deflection power to the steering wheel is engaged with the gear shaft 19, and a hollow ball screw shaft 10 is screwed into the axial center of the piston 12 via a ball 11, and the base end of the ball screw shaft 10 is hollow. The tip of the steering shaft 1 is supported through a bearing 38 in a relatively rotatable manner, and the flexible shaft 8 is inserted into the hollow part of the ball screw shaft 10, and the tip is connected to the ball screw shaft 1 with a pin 44.
0, the base end is rotatably coupled to the steering shaft 1 with a pin 3, and the distal end of the ball screw shaft 10 is supported on the end wall 32 by a four-point support bearing 43,
The steering shaft 1 is supported in the shaft hole of the valve housing 17 with a bearing 35, and when the steering shaft 1 is rotated, the twisting of the flexible shaft 8 caused by the drag force of the steering wheel which the ball screw shaft 10 receives is prevented. A rotational differential is generated between the two valve elements of the servo control valve, and the liquid chambers A and B of the cylinder are divided into two by the piston 12.
The piston 12 is pushed in a direction that facilitates rotation of the ball screw shaft 10 by applying hydraulic pressure to one side of the ball screw shaft 10.
第3図に示すようにボールねじ軸10の先端に
はフランジ10bが一体に構成され、この外周に
ボールを係合する断面ゴシツクアーチの環状溝を
設けてなる内輪と、前記ボールを両側方から挟持
する分割型外輪16とからなる分割型軸受すなわ
ち4点支持軸受43が構成され、前記外輪16は
端壁32とこのねじ穴にねじ込んだ抑え板36と
によつて支持される。 As shown in FIG. 3, a flange 10b is integrally formed at the tip of the ball screw shaft 10, and an inner ring having an annular groove with a gossic arch cross section for engaging the ball on its outer periphery and an inner ring that clamps the ball from both sides. A split type bearing, that is, a four-point support bearing 43 is constituted of a split type outer ring 16, and the outer ring 16 is supported by the end wall 32 and a restraining plate 36 screwed into this screw hole.
サーボ制御弁は第4図に示すように、シリンダ
13と一体に構成される弁ハウジング17の内部
にあつて互いに同心かつ回転可能に支持される外
スリーブ6と内スリーブ2とからなる1対の弁要
素を備えている。外スリーブ6はこの左端部を、
ボールねじ軸10の基端部外周にシールリング3
7を介して嵌合され、かつ外スリーブ6に螺合し
たピン34の先端小径部分をボールねじ軸10の
ピン穴に挿通して回転結合され、前記ピン34の
外端にはロツクナイト39が締付けられる。外ス
リーブ6を嵌合する弁室61の内周面には環状溝
22が構成され、これは給液口20と連通され
る。前記環状溝22の両側に1対の環状溝が削設
されこれらにシールリング50,51が装着され
る。内スリーブ2は操舵軸1と一体に構成され、
この外周側にダンパシール41を介して外スリー
ブ6が外嵌され、弁要素相互の振動を防止するよ
うになつている。 As shown in FIG. 4, the servo control valve has a pair of outer sleeves 6 and inner sleeves 2 that are rotatably supported concentrically within a valve housing 17 that is integrally formed with a cylinder 13. It has a valve element. The outer sleeve 6 has this left end,
A seal ring 3 is attached to the outer periphery of the base end of the ball screw shaft 10.
The small diameter portion of the tip of the pin 34, which is fitted through the pin 7 and screwed into the outer sleeve 6, is inserted into the pin hole of the ball screw shaft 10 and rotationally coupled, and a lockite 39 is tightened on the outer end of the pin 34. It will be done. An annular groove 22 is formed on the inner peripheral surface of the valve chamber 61 into which the outer sleeve 6 is fitted, and this groove communicates with the liquid supply port 20 . A pair of annular grooves are cut on both sides of the annular groove 22, and seal rings 50 and 51 are attached to these. The inner sleeve 2 is constructed integrally with the steering shaft 1,
An outer sleeve 6 is fitted onto this outer peripheral side via a damper seal 41 to prevent mutual vibration of the valve elements.
操舵軸1は内スリーブ2よりも左端側が細くな
つており、ボールねじ軸10との間に、歯と歯の
間に十分間隙を有するスプラインに類似する相対
回転制限部材65が構成され、液圧の失陥などに
よつて舵取動力が得られない場合には、手動によ
つて操舵軸1の回転力をボールねじ軸10へ伝達
し得るようになつている。操舵軸1の内スリーブ
2よりも右端側は軸受35をもつて弁ハウジング
17の軸穴に支持され、この軸受部は止め輪45
によつて支持されるシール部材55によつて外部
から密封されている。外スリーブ6の右端部と軸
受35との間の弁室61には隙間61aが構成さ
れ、この隙間61aは還液口21と連なつてい
る。操舵軸1の先端側は前述したように中空とな
つており、この内部に可撓軸8がシールリング4
7を介して嵌合され、径方向のピン3によつて互
いに回転結合される。 The steering shaft 1 is thinner on the left end side than the inner sleeve 2, and a relative rotation limiting member 65 similar to a spline with a sufficient gap between teeth is configured between the steering shaft 1 and the ball screw shaft 10, and a relative rotation limiting member 65 is formed between the steering shaft 1 and the ball screw shaft 10. When steering power cannot be obtained due to failure of the steering wheel, the rotational force of the steering shaft 1 can be manually transmitted to the ball screw shaft 10. The right end side of the inner sleeve 2 of the steering shaft 1 is supported in the shaft hole of the valve housing 17 with a bearing 35, and this bearing portion is supported by a retaining ring 45.
It is sealed from the outside by a sealing member 55 supported by. A gap 61 a is formed in the valve chamber 61 between the right end portion of the outer sleeve 6 and the bearing 35 , and this gap 61 a is connected to the liquid return port 21 . As mentioned above, the tip side of the steering shaft 1 is hollow, and the flexible shaft 8 is fitted with the seal ring 4 inside.
7 and are rotationally connected to each other by radial pins 3.
外スリーブ6と内スリーブ2とはこれらの摺動
面に弁溝を備えており、外スリーブ6の弁溝の1
つは傾斜した液孔24aを介してシリンダ液室B
と連なり、また内スリーブ2の弁溝の1つは径方
向の液孔33を径て操舵軸1の中空部と連なり、
さらに、第2図に示すようにボールねじ軸10の
中空部によつて構成される液路29を通り、ボー
ルねじ軸10の先端に設けた径方向の液孔28を
経てシリンダ液室Aと連なる。内スリーブ2の他
の弁溝は径方向の液孔26aを経て操舵軸1の軸
穴30の閉鎖端部に連なり、さらに、操舵軸1に
設けた径方向の液路42を経て前述した弁室61
の隙間61a、環液口21へと連なる。 The outer sleeve 6 and the inner sleeve 2 have valve grooves on their sliding surfaces, and one of the valve grooves of the outer sleeve 6
One is the cylinder liquid chamber B via the inclined liquid hole 24a.
and one of the valve grooves of the inner sleeve 2 is connected to the hollow part of the steering shaft 1 through the radial liquid hole 33,
Furthermore, as shown in FIG. 2, the liquid passes through a liquid passage 29 formed by the hollow part of the ball screw shaft 10, and enters the cylinder liquid chamber A through a radial liquid hole 28 provided at the tip of the ball screw shaft 10. Continuing. The other valve groove of the inner sleeve 2 is connected to the closed end of the shaft hole 30 of the steering shaft 1 through the radial liquid hole 26a, and further connected to the closed end of the shaft hole 30 of the steering shaft 1 through the radial liquid passage 42 provided in the steering shaft 1 to the above-mentioned valve. room 61
The gap 61a continues to the reflux port 21.
弁要素である外スリーブ6と内スリーブ2の構
成について詳述すると、第4,5図に示すように
外スリーブ6は周方向に位置を異にして径方向の
液孔22a,24aを穿設される。液孔22aの
外周端は給液口20と連なる前述した環状溝22
に連なり、液孔24aの内端は連絡溝24に、外
端は液室Bに直接連なる。 To explain in detail the structure of the outer sleeve 6 and the inner sleeve 2, which are valve elements, as shown in FIGS. 4 and 5, the outer sleeve 6 has radial liquid holes 22a and 24a formed at different positions in the circumferential direction. be done. The outer peripheral end of the liquid hole 22a is connected to the above-mentioned annular groove 22 connected to the liquid supply port 20.
The inner end of the liquid hole 24a is directly connected to the communication groove 24, and the outer end is directly connected to the liquid chamber B.
内スリーブ2はこの外周に周方向の位置を異に
して、軸方向に延びる制御溝25,26を削設さ
れ、特に制御溝26は径方向の液孔26aによつ
て操舵軸1に可撓軸8を嵌合するための軸穴30
の閉鎖端部に連通する。 The inner sleeve 2 has control grooves 25 and 26 cut in the outer circumference at different positions in the circumferential direction and extending in the axial direction.In particular, the control groove 26 is provided with a radial liquid hole 26a to provide flexibility to the steering shaft 1. Shaft hole 30 for fitting the shaft 8
communicates with the closed end of.
また、制御溝23に対して、内スリーブ2に径
方向の液孔33が設けられる。 Furthermore, a radial liquid hole 33 is provided in the inner sleeve 2 with respect to the control groove 23 .
そうして、内外両スリーブ2,6は中立位置、
すなわち可撓軸8にねじれが生じていない場合、
制御溝25は液孔22aを連絡溝23,24に連
通させ、また制御溝26は連絡溝23,24を液
孔26aに連通させる。 Then, both the inner and outer sleeves 2 and 6 are in the neutral position.
In other words, when the flexible shaft 8 is not twisted,
The control groove 25 allows the liquid hole 22a to communicate with the communication grooves 23 and 24, and the control groove 26 allows the communication groove 23 and 24 to communicate with the liquid hole 26a.
ピストン12により仕切られる液室A,B間の
液密を得るために、シリンダ13と摺接するピス
トン外周部にシールリング48が、ボールねじ軸
10とピストン12との摺動部にシールリング5
6が装着され、また給液口20に連なる環状溝2
2と液室Bとの間の液密を得るためのシールリン
グ50と、環状溝22と還液口21に連なる隙間
61aとの液密を得るためのシールリング51が
それぞれ弁室61の内周壁部に装着される。ま
た、還液口21に連なる軸穴30の閉鎖端部と、
室Aに連なる液路29との間の液密を得るため
に、可撓軸8の端部外周にシールリング47が装
着される。 In order to obtain liquid tightness between the liquid chambers A and B partitioned by the piston 12, a seal ring 48 is provided on the outer periphery of the piston in sliding contact with the cylinder 13, and a seal ring 5 is provided on the sliding portion between the ball screw shaft 10 and the piston 12.
6 is installed, and the annular groove 2 connected to the liquid supply port 20
A seal ring 50 for obtaining liquid tightness between the valve chamber B and the liquid chamber B, and a seal ring 51 for obtaining liquid tightness between the annular groove 22 and the gap 61a connected to the liquid return port 21 are installed inside the valve chamber 61, respectively. Attached to the surrounding wall. In addition, a closed end of the shaft hole 30 connected to the liquid return port 21,
In order to obtain liquid tightness between the flexible shaft 8 and the liquid path 29 connected to the chamber A, a seal ring 47 is attached to the outer periphery of the end of the flexible shaft 8.
次に上記構成の液圧式動力舵取装置の作用につ
いて説明する。第5図は動力舵取装置の中立状態
(車両が直進走行)を示しており、この時圧液は
給液口20から環状溝22、液孔22aを経て制
御溝25に入り、ここから連絡溝24、液孔24
aを経て液室Bに入る一方、連絡溝23、液孔3
3、液路29,28を経て液室Aに入り、ピスト
ン12の両端面に圧力を及ぼすが、各連絡溝2
4,23はまた液孔26aを経て操舵軸1の軸穴
30、液路42、隙間61aに入り、軸受35を
潤滑し、還液口21に戻るようになつているか
ら、ピストン12に作用する液圧は液路抵抗によ
る極く低いものであり、その圧力は左右同じであ
るから、ピストン12には推力が生じない。 Next, the operation of the hydraulic power steering device having the above configuration will be explained. Figure 5 shows the power steering system in its neutral state (vehicle is running straight); at this time, the pressurized fluid enters the control groove 25 from the fluid supply port 20 via the annular groove 22 and fluid hole 22a, and is connected from here. Groove 24, liquid hole 24
It enters the liquid chamber B through a, while the communication groove 23 and the liquid hole 3
3. It enters the liquid chamber A through the liquid passages 29 and 28 and exerts pressure on both end surfaces of the piston 12, but each communication groove 2
4 and 23 also enter the shaft hole 30 of the steering shaft 1, the liquid path 42, and the gap 61a through the liquid hole 26a, lubricate the bearing 35, and return to the liquid return port 21, so that they act on the piston 12. The hydraulic pressure caused by the piston 12 is extremely low due to the fluid path resistance, and the pressure is the same on both sides, so no thrust is generated in the piston 12.
いまハンドルを右に切ると、ボールねじ軸10
は操向車輪からの抗力を受けていため、操舵軸1
だけが可撓軸8のねじれを伴つて回転され、内ス
リーブ2が外スリーブ6に対して時針方向(第5
図)に回転差動を生じる。従つて、溝25,24
間及び溝23,26間が閉じ、溝25,23間及
び溝24,26間が拡がるから、給液口20から
の圧液は環状溝22、液孔22a、液溝25、液
溝23、液孔33、液路29,28を通つてシリ
ンダ液室Aに入つてピストン12の左端に液圧を
及ぼし、一方シリンダ液室Bの液は液孔24a連
絡溝24、制御溝26、液孔26a、操舵軸1の
軸穴30、液路42、隙間61aを通つて軸受3
5を潤滑して還液口21に戻る。ピストン12の
右方移動はボールねじ軸10が右ねじ軸となつて
いるから、可撓軸8にねじれを生じる僅かの回転
力を付与するだけでボールねじ軸10の右回転を
容易にし、ピストン12の受ける液圧動力によつ
て歯車軸19を時計方向に回転し、図示していな
いピツトマンアーム及びリンク機構を介して操向
車輪の右偏向を達成する。 If you turn the handle to the right now, the ball screw shaft 10
is receiving drag from the steering wheel, so the steering axis 1
The inner sleeve 2 is rotated with the twist of the flexible shaft 8, and the inner sleeve 2 is rotated in the hour hand direction (the fifth
(Figure) produces a rotational differential. Therefore, the grooves 25, 24
Since the gap between the grooves 23 and 26 closes, and the gap between the grooves 25 and 23 and the grooves 24 and 26 widen, the pressure liquid from the liquid supply port 20 flows through the annular groove 22, the liquid hole 22a, the liquid groove 25, the liquid groove 23, The liquid in the cylinder liquid chamber A enters the cylinder liquid chamber A through the liquid hole 33 and the liquid passages 29 and 28 and exerts liquid pressure on the left end of the piston 12, while the liquid in the cylinder liquid chamber B flows through the liquid hole 24a, the communication groove 24, the control groove 26, and the liquid hole. 26a, the shaft hole 30 of the steering shaft 1, the liquid passage 42, and the bearing 3 through the gap 61a.
5 and return to the liquid return port 21. Since the ball screw shaft 10 is a right-handed screw shaft, the rightward movement of the piston 12 is facilitated by applying a slight rotational force that causes twisting to the flexible shaft 8, and the piston 12 is easily rotated clockwise. The gear shaft 19 is rotated clockwise by the hydraulic power received by the gear shaft 12, and the steering wheels are deflected to the right via a pitman arm and a link mechanism (not shown).
このような液圧回路は可撓軸8に捩れが生じて
いる期間だけ生じ、その間車輪の偏向角度は増大
する。所要の偏向角度に達した時、操舵軸1の回
転力の付与を停止すれば、ピストン12の移動が
可撓軸8のねじれを解消する位置にまで追随運動
し、そこで、外スリーブ6と内スリーブ2との関
係は第5図の中立状態となり、歯車軸19は停止
し、このようにして操舵軸1にサーボ運動する。 Such a hydraulic circuit only occurs during the period of twisting of the flexible shaft 8, during which the deflection angle of the wheels increases. When the required deflection angle is reached, if the application of rotational force to the steering shaft 1 is stopped, the movement of the piston 12 follows until the position where the twist of the flexible shaft 8 is released, and then the outer sleeve 6 and the inner sleeve The relationship with the sleeve 2 is in the neutral state shown in FIG. 5, and the gear shaft 19 is stopped, thus making a servo movement to the steering shaft 1.
次にハンドルと一緒に操舵軸1を左に回転させ
た場合については、前述の右に回転させた場合と
逆方向の液圧回路が形成されるが、作用は全く同
様であるので説明を省略する。 Next, when the steering shaft 1 is rotated to the left together with the steering wheel, a hydraulic pressure circuit is formed in the opposite direction to the case where the steering shaft 1 is rotated to the right as described above, but the operation is exactly the same, so the explanation will be omitted. do.
本発明は上述のように構成したので、次のよう
な効果が得られる。
Since the present invention is configured as described above, the following effects can be obtained.
(a) ボールねじ軸10の先端部を4点支持軸受4
3をもつてシリンダの端壁32に支持するとと
もに、ボールねじ軸10の基端部に制御弁の弁
要素である外スリーブ6を支持したものである
から、ピストンを経てボールねじ軸10へ伝達
される車輪からの外力は4点支持軸受43によ
り端壁32に受け止められ、外スリーブ6を支
持するボールねじ軸10の基端部への外力の伝
達が抑えられる。すなわち、外力の伝達経路で
あるボールねじ軸10を支持する4点支持軸受
43とボールねじ軸10のピストン12に螺合
する部分との間には弁要素が配設されていない
から、弁要素が直接外力を受けることがなく、
制御弁としての円滑な作動が得られる。(a) Bearing 4 supports the tip of the ball screw shaft 10 at four points.
3 is supported on the end wall 32 of the cylinder, and the outer sleeve 6, which is the valve element of the control valve, is supported on the base end of the ball screw shaft 10, so that the pressure is transmitted to the ball screw shaft 10 through the piston. The external force from the wheels is received by the end wall 32 by the four-point support bearing 43, and the transmission of the external force to the base end of the ball screw shaft 10 that supports the outer sleeve 6 is suppressed. That is, since no valve element is disposed between the four-point support bearing 43 that supports the ball screw shaft 10, which is the external force transmission path, and the portion of the ball screw shaft 10 that is screwed into the piston 12, the valve element is not directly subjected to external force,
Smooth operation as a control valve can be obtained.
(b) ボールねじ軸10と操舵軸1の各外径はほぼ
同寸とされ、ボールねじ軸10に支持した外ス
リーブ6に操舵軸1に一体的に形成した内スリ
ーブ2が嵌合されることとなり、全体としての
制御弁の外径寸法が小さくなり、このことはキ
ヤブオーバ型トラツクなどの場合のように運転
室の床下および前方部分が狭い場合でも、ブレ
ーキペダルやアクセルペダルの配置に影響を及
ぼすことなく、取付けが可能となる。(b) The outer diameters of the ball screw shaft 10 and the steering shaft 1 are approximately the same, and the inner sleeve 2 formed integrally with the steering shaft 1 is fitted into the outer sleeve 6 supported on the ball screw shaft 10. As a result, the outer diameter of the control valve as a whole becomes smaller, which affects the placement of the brake pedal and accelerator pedal even when the underfloor and front part of the driver's cab is narrow, such as in cab-over type trucks. It can be installed without causing any damage.
(c) 内スリーブ2が操舵軸1と一体的に形成され
るのに対して、外スリーブ6はボールねじ軸1
0の基端部にいわばフローテイング支持される
ので、制御弁の一層円滑な作動が得られる。(c) While the inner sleeve 2 is formed integrally with the steering shaft 1, the outer sleeve 6 is formed integrally with the ball screw shaft 1.
Since the control valve is floatingly supported at the base end of the control valve, smoother operation of the control valve can be achieved.
第1図は従来の動力舵取装置の縦断面図、第2
図は本発明に係る動力舵取装置の縦断面図、第3
図は同装置におけるボールねじ軸先端の回転支持
部についての縦断面図、第4図は同装置のサーボ
制御弁部についての縦断面図、第5図はサーボ制
御弁についての作動を説明する横断面図である。
A,B:液室、1:操舵軸、2:内スリーブ、
6:外スリーブ、8:可撓軸、10:ボールねじ
軸、10b:フランジ、12:ピストン、13:
シリンダ、16:外輪、17:弁ハウジング、1
9:出力歯車軸、20:給液口、21:還液口、
28,29:液路、34:ピン、35:軸受、3
6:抑え板、38:軸受、43:軸受、61:弁
室。
Figure 1 is a vertical cross-sectional view of a conventional power steering device;
The figure is a longitudinal sectional view of the power steering device according to the present invention,
The figure is a longitudinal cross-sectional view of the rotation support part at the tip of the ball screw shaft in the device, Figure 4 is a vertical cross-sectional view of the servo control valve part of the device, and Figure 5 is a cross-sectional view explaining the operation of the servo control valve It is a front view. A, B: Liquid chamber, 1: Steering shaft, 2: Inner sleeve,
6: Outer sleeve, 8: Flexible shaft, 10: Ball screw shaft, 10b: Flange, 12: Piston, 13:
Cylinder, 16: Outer ring, 17: Valve housing, 1
9: Output gear shaft, 20: Liquid supply port, 21: Liquid return port,
28, 29: Liquid path, 34: Pin, 35: Bearing, 3
6: Holding plate, 38: Bearing, 43: Bearing, 61: Valve chamber.
Claims (1)
合つているピストンと、該ピストンにより区画さ
れる1対の液室を有するシリンダとを有し、操舵
軸と前記ピストンに螺合したボールねじ軸とが可
撓軸をもつて連結され、該ボールねじ軸に結合さ
れた円筒形の第1弁要素と前記操舵軸に一体に形
成されかつ前記第1弁要素に嵌合された第2弁要
素とが、前記可撓軸のねじれにより前記1対の液
室の一方を液圧源に、他方を液槽にそれぞれ連通
する液圧回路を形成する動力舵取装置において、
前記ボールねじ軸の先端部に内輪を形成するフラ
ンジを一体に形成し、 該内輪を含む4点支持軸受により前記ボールね
じ軸を前記シリンダの端壁部に軸方向および径方
向不動に支持するとともに、 前記ボールねじ軸と前記操舵軸との各外径をほ
ぼ同寸法とし、前記ボールねじ軸の基端部に前記
第1弁要素を外嵌し、かつ径方向のピンにより回
転結合したことを特徴とする動力舵取装置。[Scope of Claims] 1. A piston with a rack provided on a part of its outer periphery meshing with an output gear shaft, and a cylinder having a pair of liquid chambers partitioned by the piston, and the steering shaft and the piston are connected to each other. A cylindrical first valve element coupled to the ball screw shaft is integrally formed with the steering shaft and is fitted into the first valve element. In the power steering device, the combined second valve element forms a hydraulic circuit that communicates one of the pair of liquid chambers with a liquid pressure source and the other with a liquid tank by twisting the flexible shaft. ,
A flange forming an inner ring is integrally formed at the tip of the ball screw shaft, and the ball screw shaft is immovably supported in the axial and radial directions on the end wall of the cylinder by a four-point support bearing including the inner ring. , the outer diameters of the ball screw shaft and the steering shaft are approximately the same, the first valve element is externally fitted onto the base end of the ball screw shaft, and the first valve element is rotatably coupled to the ball screw shaft by a radial pin. Features a power steering device.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP11455378A JPS5544016A (en) | 1978-09-20 | 1978-09-20 | Power steering apparatus |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP11455378A JPS5544016A (en) | 1978-09-20 | 1978-09-20 | Power steering apparatus |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS5544016A JPS5544016A (en) | 1980-03-28 |
JPS6149147B2 true JPS6149147B2 (en) | 1986-10-28 |
Family
ID=14640670
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP11455378A Granted JPS5544016A (en) | 1978-09-20 | 1978-09-20 | Power steering apparatus |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5544016A (en) |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019064538A1 (en) | 2017-09-29 | 2019-04-04 | Attaccato合同会社 | Binder for lithium ion batteries, and electrode and separator using same |
WO2021075440A1 (en) | 2019-10-15 | 2021-04-22 | Attaccato合同会社 | Electrode for non-aqueous electrolyte power storage device, non-aqueous electrolyte power storage device, and method for producing same |
EP3937279A1 (en) | 2020-07-09 | 2022-01-12 | Honda Motor Co., Ltd. | Non-aqueous electrolyte secondary battery negative electrode and non-aqueous electrolyte secondary battery including same |
DE102022101030A1 (en) | 2021-01-21 | 2022-07-21 | Honda Motor Co., Ltd. | NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY |
DE102022100171A1 (en) | 2021-01-19 | 2022-07-21 | Honda Motor Co., Ltd. | NEGATIVE ELECTRODE OF NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY AND NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY, COMPRISING THE SAME |
DE102022101815A1 (en) | 2021-02-01 | 2022-08-04 | Honda Motor Co., Ltd. | NEGATIVE ELECTRODE FOR NON-AQUEOUS ELECTROLYTE SECONDARY BATTERIES AND NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY COMPRISING THESE |
DE102022101767A1 (en) | 2021-02-01 | 2022-08-04 | Honda Motor Co., Ltd. | NEGATIVE ELECTRODE FOR USE IN A NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY AND NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY COMPRISING THESE |
DE102022101901A1 (en) | 2021-02-01 | 2022-08-04 | Honda Motor Co., Ltd. | NEGATIVE ELECTRODE FOR NON-AQUEOUS ELECTROLYTE SECONDARY BATTERIES AND NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY COMPRISING THESE |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS57151409U (en) * | 1981-03-19 | 1982-09-22 | ||
JPS5871U (en) * | 1981-06-26 | 1983-01-05 | 日本精工株式会社 | Power steering device |
-
1978
- 1978-09-20 JP JP11455378A patent/JPS5544016A/en active Granted
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2019064538A1 (en) | 2017-09-29 | 2019-04-04 | Attaccato合同会社 | Binder for lithium ion batteries, and electrode and separator using same |
KR20200046077A (en) | 2017-09-29 | 2020-05-06 | 아탁카토 고도가이샤 | Binder for lithium ion battery and electrode and separator using the same |
KR20210156334A (en) | 2017-09-29 | 2021-12-24 | 아탁카토 고도가이샤 | Binder for lithium ion batteries, and electrode and separator using same |
WO2021075440A1 (en) | 2019-10-15 | 2021-04-22 | Attaccato合同会社 | Electrode for non-aqueous electrolyte power storage device, non-aqueous electrolyte power storage device, and method for producing same |
EP3937279A1 (en) | 2020-07-09 | 2022-01-12 | Honda Motor Co., Ltd. | Non-aqueous electrolyte secondary battery negative electrode and non-aqueous electrolyte secondary battery including same |
DE102022100171A1 (en) | 2021-01-19 | 2022-07-21 | Honda Motor Co., Ltd. | NEGATIVE ELECTRODE OF NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY AND NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY, COMPRISING THE SAME |
DE102022101030A1 (en) | 2021-01-21 | 2022-07-21 | Honda Motor Co., Ltd. | NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY |
DE102022101815A1 (en) | 2021-02-01 | 2022-08-04 | Honda Motor Co., Ltd. | NEGATIVE ELECTRODE FOR NON-AQUEOUS ELECTROLYTE SECONDARY BATTERIES AND NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY COMPRISING THESE |
DE102022101767A1 (en) | 2021-02-01 | 2022-08-04 | Honda Motor Co., Ltd. | NEGATIVE ELECTRODE FOR USE IN A NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY AND NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY COMPRISING THESE |
DE102022101901A1 (en) | 2021-02-01 | 2022-08-04 | Honda Motor Co., Ltd. | NEGATIVE ELECTRODE FOR NON-AQUEOUS ELECTROLYTE SECONDARY BATTERIES AND NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY COMPRISING THESE |
DE102022101815B4 (en) | 2021-02-01 | 2023-08-03 | Honda Motor Co., Ltd. | NEGATIVE ELECTRODE FOR NON-AQUEOUS ELECTROLYTE SECONDARY BATTERIES AND NON-AQUEOUS ELECTROLYTE SECONDARY BATTERY COMPRISING THESE |
Also Published As
Publication number | Publication date |
---|---|
JPS5544016A (en) | 1980-03-28 |
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