JPS63215463A - Power steering device - Google Patents

Power steering device

Info

Publication number
JPS63215463A
JPS63215463A JP4582087A JP4582087A JPS63215463A JP S63215463 A JPS63215463 A JP S63215463A JP 4582087 A JP4582087 A JP 4582087A JP 4582087 A JP4582087 A JP 4582087A JP S63215463 A JPS63215463 A JP S63215463A
Authority
JP
Japan
Prior art keywords
hydraulic pressure
hydraulic
pressure chamber
reaction
valve
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.)
Pending
Application number
JP4582087A
Other languages
Japanese (ja)
Inventor
Hiroshi Hachisuga
蜂須賀 寛
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Priority to JP4582087A priority Critical patent/JPS63215463A/en
Publication of JPS63215463A publication Critical patent/JPS63215463A/en
Pending legal-status Critical Current

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  • Power Steering Mechanism (AREA)

Abstract

PURPOSE:To properly suppress the increase of reaction force by interposing a unidirectional valve for cutting off the circulation of liquid to a reaction force hydraulic pressure chamber from a working liquid hydraulic pressure chamber into a bypass passage leading from the reaction hydraulic pressure chamber to the working hydraulic pressure chamber on each noncorrespondence side. CONSTITUTION:A pair of inner holes 21d and 21e are formed in the axial direction at the both edges of a valve spool 21, and reaction hydraulic chamber 28 and 29 are formed between a housing 11 and each inner hole 21d, 21e. The reaction hydraulic chambers 28 and 29 communicate to the respective annular grooves 21b and 21a through the orifices 30 and 31 formed on the valve spool 21, and one reaction hydraulic chamber 28 communicates to one working hydraulic pressure chamber 15 through passage 27. Further, the other reaction hydraulic pressure chamber 28 communicates to the other working hydraulic pressure chamber 16 through a bypass passage 32. In the bypass passages 32 and 33, unidirectional valves 34 and 35 for cutting off the liquid circulation from the working hydraulic pressure chamber to the reaction hydraulic pressure chamber are interposed.

Description

【発明の詳細な説明】 〔発明の目的〕 (産業上の利用分野) 本発明は、車両の動力舵取装置に関し、特に、車両の舵
取リンク機構を動かすための往復動型液圧作動シリンダ
装置、該往復動型液圧作動シリンダ装置にリザーバ内の
作動液を送るための液圧ポンプ及び該液圧ポンプに連通
した通路と前記リザーバに連通した通路を前記往復動型
液圧作動シリンダの再作動液圧室に連通した通路とを有
したバルブシリンダと、該バルブシリンダに摺動可能に
収納されて入力軸の回転により往復摺動させられるバル
ブスプールとを有して前記入力軸の一方向回転に応じて
前記往復動型液圧作動シリンダの両1ヶ勤液圧室の一方
作動液圧室に前記液圧ポンプからの作動液を流入させる
と共にその他方作動液圧室の作動液を前記リザーバに流
出させ且つ前記入力軸の他方向回転に応じて前記他方作
動液圧室に前記液圧ポンプからの作動液を前記リザーバ
に流出させるコントロールバルブ装置を備えた動力舵取
装置における液圧式反力機構に関する。
DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial Field of Application) The present invention relates to a power steering system for a vehicle, and more particularly to a reciprocating hydraulically actuated cylinder for moving a steering linkage mechanism of a vehicle. a hydraulic pump for delivering hydraulic fluid in a reservoir to the reciprocating hydraulic cylinder device, and a passage communicating with the hydraulic pump and a passage communicating with the reservoir of the reciprocating hydraulic cylinder. The input shaft includes a valve cylinder having a passage communicating with a re-operating hydraulic pressure chamber, and a valve spool that is slidably housed in the valve cylinder and slid back and forth by rotation of the input shaft. In response to the directional rotation, the hydraulic fluid from the hydraulic pump flows into one of the two working hydraulic chambers of the reciprocating hydraulic hydraulic cylinder, and the hydraulic fluid in the other hydraulic chamber flows. Hydraulic type in a power steering device comprising a control valve device that causes working fluid from the hydraulic pump to flow out into the reservoir and into the other working hydraulic chamber in response to rotation of the input shaft in the other direction. Regarding reaction force mechanism.

(従来の技術) 従来、この種の装置として特公昭57−44502号公
報に示されるものがあった。
(Prior Art) Conventionally, there has been a device of this type as disclosed in Japanese Patent Publication No. 57-44502.

この装置は、リザーバに連通した通路と液圧作動シリン
ダの再作動液圧室に連通した通路とを有したバルブシリ
ンダと、その外周に一対の環状溝を有し該バルブシリン
ダに摺動可能に収納されて入力軸の回転により往復摺動
させられるバルブスプールと、該バルブスプール内に形
成される一対の軸方向孔内に挿嵌されバルブシリンダに
相対移動不能とされた一対の反作用ピストンと、バルブ
スプール内において反作用ピストンによって制限され絞
り孔を介してバルブスプールの各環状溝に夫々連通され
る反作用室内に配置される過圧弁とを有している。過圧
弁の流入側は常時液圧ポンプに接続されているバルブス
プール両端とケーシングにより形成された流入室に連通
され、その流出側は各反作用室に連通される。また各反
作用室に絞り孔を介して連通するバルブスプールの環状
溝はバルブスプールの移動によって流入室又はリザーバ
に連通した通路に交互に連通され、それにより両件用室
に圧力差が生じ、該圧力差によってバルブスプールに反
力を付与する。
This device includes a valve cylinder having a passage communicating with a reservoir and a passage communicating with a re-operation hydraulic chamber of a hydraulic actuation cylinder, and a pair of annular grooves on the outer periphery of the valve cylinder so as to be slidable on the valve cylinder. a valve spool that is housed and slid back and forth by rotation of an input shaft; a pair of reaction pistons that are inserted into a pair of axial holes formed in the valve spool and are immovable relative to the valve cylinder; and an overpressure valve disposed in a reaction chamber defined by a reaction piston in the valve spool and communicating through a throttle hole with each annular groove of the valve spool. The inlet side of the overpressure valve is communicated with an inlet chamber formed by the casing and both ends of the valve spool, which are constantly connected to a hydraulic pump, and the outlet side thereof is communicated with each reaction chamber. Further, the annular groove of the valve spool, which communicates with each reaction chamber through the throttle hole, is alternately communicated with the passage communicating with the inflow chamber or the reservoir by movement of the valve spool, thereby creating a pressure difference between the chambers for both purposes, and A reaction force is applied to the valve spool due to the pressure difference.

そこで従来の動力舵取装置においては、比較的低い走行
速度、例えば駐車の際等の舵取操作時に生じる大きな舵
取操作抵抗を低減させるために、反力が所定値を超えた
時、過圧弁を開弁し低圧側反作用室に液圧ポンプからの
圧液を注入するかもしくは、高圧側反作用室をリザーバ
に連通させている。
Therefore, in conventional power steering devices, in order to reduce the large steering operation resistance that occurs during steering operations at relatively low travel speeds, for example when parking, an overpressure valve is installed when the reaction force exceeds a predetermined value. The valve is opened to inject pressure liquid from a hydraulic pump into the low-pressure side reaction chamber, or the high-pressure side reaction chamber is communicated with the reservoir.

(発明が解決しようとする問題点) しかしなから、上記した従来の動力舵取装置においては
、その組込みスペースの制約上、バルブスプール内に過
圧弁等を収納した構成であり、構成が複雑になると共に
、過圧弁とバルブスプール間の隙間、もしくはバルブス
プールと反作用ピストンと反作用ピストン間の隙間(組
付上必要とされる隙間)による内部洩れが発生しやすく
、内部洩れが発生した際には、適切な反力が得られない
という問題がある。
(Problems to be Solved by the Invention) However, in the above-mentioned conventional power steering device, due to the limitation of the installation space, the overpressure valve etc. are housed in the valve spool, resulting in a complicated structure. At the same time, internal leakage is likely to occur due to the gap between the overpressure valve and the valve spool, or the gap between the valve spool and the reaction piston (the gap required for assembly), and when internal leakage occurs, , there is a problem that an appropriate reaction force cannot be obtained.

そこで本発明は、構成の複雑化及び液圧式反力機構の損
傷を招くことなく、低速時等における舵取操作反力の増
大を防止することをその技術的課題とする。
Therefore, the technical object of the present invention is to prevent the steering operation reaction force from increasing at low speeds, etc., without complicating the structure or damaging the hydraulic reaction force mechanism.

〔発明の構成〕[Structure of the invention]

(問題点を解決するための手段) 上記した技術的課題を解決するために講じた技術的手段
は、車両の舵取リンク機構を動かすための往復動型液圧
作動シリンダ装置、該往復動型液圧作動シリンダ装置に
リザーバ内の作動液を送るための液圧ポンプ及び該液圧
ポンプに連通した通路と前記リザーバに連通した通路と
、前記往復動型“液圧作動シリンダの再作動液圧室に連
通した通路とを有したバルブシリンダと、該バルブシリ
ンダに摺動可能に収納されて入力軸の回転により往復摺
動させられるバルブスプールとを有して前記入力軸の一
方向回転に応じて前記往復動型液圧作動シリンダの再作
動液圧室の一方作動液圧室に前記液圧ポンプからの作動
液を流入させると共にその他方作動液圧室の作動液を前
記リザーバに流出させ且つ前記入力軸の他方向回転に応
じて前記他方作動液圧室に前記液圧ポンプからの作動液
を流入させると共に前記一方作動液圧室の作動液を前記
リザーバに流出させるコントロールバルブ装置とを備え
た動力舵取装置において、前記バルブスプールの両端に
一対の反力液圧室を形成し、該一対の反力液圧室を夫々
、前記入力軸の回転に応じて夫々の対応した前記作動液
圧室に夫々のオリフイスを介して連通させると共に前記
作動液圧室の非対応側の作動液圧室に前記往復動型液圧
作動シリンダのパワーピストンに設けられ反力液圧室か
ら作動液圧室への液流通を許容し、作動液圧室から反力
液圧室への液流通を遮断する一方向弁を介して連通させ
た、ことである。
(Means for Solving the Problems) The technical measures taken to solve the above-mentioned technical problems include a reciprocating hydraulic cylinder device for moving the steering linkage of a vehicle, A hydraulic pump for sending hydraulic fluid in a reservoir to a hydraulic cylinder device, a passage communicating with the hydraulic pump, a passage communicating with the reservoir, and a re-operating hydraulic pressure of the reciprocating hydraulic cylinder. The valve cylinder has a valve cylinder having a passage communicating with a chamber, and a valve spool that is slidably housed in the valve cylinder and is slid back and forth in response to rotation of the input shaft in one direction. to cause the hydraulic fluid from the hydraulic pump to flow into one of the re-operating hydraulic chambers of the reciprocating hydraulic hydraulic cylinder, and to cause the hydraulic fluid in the other hydraulic chamber to flow out into the reservoir; a control valve device that causes hydraulic fluid from the hydraulic pump to flow into the other hydraulic pressure chamber and hydraulic fluid from the one hydraulic pressure chamber to flow out to the reservoir in response to rotation of the input shaft in the other direction; In the power steering device, a pair of reaction force hydraulic pressure chambers are formed at both ends of the valve spool, and each of the pair of reaction force hydraulic pressure chambers is controlled to operate according to the rotation of the input shaft. The hydraulic pressure chambers are communicated through respective orifices, and the hydraulic pressure chamber on the non-corresponding side of the hydraulic pressure chamber is provided with hydraulic fluid from the reaction hydraulic pressure chamber provided in the power piston of the reciprocating hydraulic pressure cylinder. The communication is made through a one-way valve that allows liquid flow to the pressure chamber and blocks liquid flow from the working hydraulic pressure chamber to the reaction hydraulic pressure chamber.

(作用) これにより、反力液圧室から夫々の非対応側の作動液圧
室へのバイパス通路が一方向弁を介して形成される。そ
れによって入力軸が一方向回転し液圧ポンプからの作動
液が一方の作動液室へ流入すると共にオリフィスを介し
て一方の反力液室に流入され、また他方の作動液圧室が
リザーバに連通ずると共に他方の反力液圧室がオリフィ
スを介してリザーバに連通され、両反力液圧室間に圧力
差が生じて反力が発生した時、一方の反力液圧室内の液
圧が所定値以上になるとバイパス通路の一方向弁が開弁
し、他方の作動液圧室に一方の反力液圧室内の作動液が
バイパス通路を経て流出し、反力の増大を適切に抑制す
ることができる。また、一方向弁は往復動型液圧作動シ
リンダ装置のパワーピストン内に設けられているため、
従来装置のような反作用ピストン及び過圧弁は不要とな
り、それにより内部洩れの発生を防止することができ反
力機構の機能が損なわれることはない。
(Function) As a result, a bypass passage is formed from the reaction force hydraulic pressure chamber to each of the non-corresponding working hydraulic pressure chambers via the one-way valve. As a result, the input shaft rotates in one direction, and the hydraulic fluid from the hydraulic pump flows into one hydraulic fluid chamber and flows into one reaction fluid chamber through the orifice, and the other hydraulic fluid chamber flows into the reservoir. At the same time, the other reaction hydraulic pressure chamber is communicated with the reservoir via the orifice, and when a pressure difference occurs between both reaction force hydraulic pressure chambers and a reaction force is generated, the hydraulic pressure in one reaction force hydraulic pressure chamber decreases. When the value exceeds a predetermined value, the one-way valve in the bypass passage opens, and the hydraulic fluid in one reaction hydraulic pressure chamber flows out through the bypass passage into the other hydraulic pressure chamber, appropriately suppressing the increase in reaction force. can do. In addition, since the one-way valve is installed inside the power piston of the reciprocating hydraulic cylinder device,
There is no need for a reaction piston and an overpressure valve as in the conventional device, thereby preventing the occurrence of internal leakage and preventing the function of the reaction force mechanism from being impaired.

(実施例) 以下、本発明に従った動力舵取装置の一実施例を図面に
基づき説明する。
(Example) Hereinafter, an example of a power steering device according to the present invention will be described based on the drawings.

第1〜3図において、動力舵取装置10は、車両に固定
されるハウジング11と、該ハウジング11内に回転可
能に配置された入力軸12と、ハウジング11内に摺動
可能に且つ液密的に嵌合されたパワーピストン13と、
該パワーピストン13に形成されたうツク13aと噛合
するセクタ14aを有した出力軸14とを有している。
1 to 3, the power steering device 10 includes a housing 11 fixed to a vehicle, an input shaft 12 rotatably disposed within the housing 11, and an input shaft 12 slidably and liquid-tightly disposed within the housing 11. a power piston 13 fitted with a
It has an output shaft 14 having a sector 14a that meshes with a recess 13a formed on the power piston 13.

入力軸12は図示しない舵取ハンドルに連通され、出力
軸14は図示しない舵取リンク機構と連結される。
The input shaft 12 is connected to a steering wheel (not shown), and the output shaft 14 is connected to a steering link mechanism (not shown).

ハウジング11とパワーピストン13はパワーピストン
13の両側に一方作動液圧室15と他方作動液圧室16
を有する往復動型液圧作動シリンダ装置を構成する。
The housing 11 and the power piston 13 have one working hydraulic pressure chamber 15 and the other working hydraulic pressure chamber 16 on both sides of the power piston 13.
A reciprocating hydraulically operated cylinder device is constructed.

パワーピストン13内には、再作動液圧室15゜16の
一方に液圧ポンプP(車両のエンジンにより作動される
)からの作動液を流入させ且つその他方の作動液をリザ
ーバRに流出させるためのコントロールバルブ装置17
と、該コントロールバルブ装置17を入力軸12の回転
に応じて作動させるためのナツト部材18及びバルブピ
ン19が配置されている。ナツト部材18は、入力軸1
2の外周に形成された螺子溝12aとナツト部材18の
内周に形成された螺子溝18aとの間に嵌入されたボー
ル20を介して入力軸12と螺子係合されており、また
パワーピストン13に対しては回転はできるが軸方向へ
は移動不能に組付られている。このため、入力軸12が
回転された時にはナツト部材18が入力軸12と一緒に
回転する。
In the power piston 13, hydraulic fluid from a hydraulic pump P (operated by the vehicle engine) flows into one of the re-operating hydraulic pressure chambers 15 and 16, and the other hydraulic fluid flows out into the reservoir R. Control valve device 17 for
A nut member 18 and a valve pin 19 for operating the control valve device 17 in accordance with the rotation of the input shaft 12 are arranged. The nut member 18 is connected to the input shaft 1
The input shaft 12 is threadedly engaged with the input shaft 12 via a ball 20 fitted between a threaded groove 12a formed on the outer periphery of the nut member 2 and a threaded groove 18a formed on the inner periphery of the nut member 18. 13, it is assembled so that it can rotate but cannot move in the axial direction. Therefore, when the input shaft 12 is rotated, the nut member 18 rotates together with the input shaft 12.

バルブピン19はナツト部材18に固定されており、そ
の自由端をコントロールバルブ装置17のバルブスプー
ル21の径方向孔21fに嵌入されている。
The valve pin 19 is fixed to the nut member 18, and its free end is inserted into the radial hole 21f of the valve spool 21 of the control valve device 17.

第2図、第3図においてコントロールバルブ装置117
は、パワーピストン13の横方向孔に嵌入されたバルブ
シリンダ22内に摺動可能に収納されて入力軸12の回
転によりバルブピン19を介して往復摺動させられるバ
ルブスプール21とを有している。バルブシリンダ22
は液圧ポンプPに連通した通路23と、作動液を貯蔵す
るリザーバRに連通した通路24と、再作動液圧室15
゜16に連通した通路25,26.27を有しており、
通路23.24はバルブシリンダ22の内孔に形成され
た環状溝22a、22bに開口している。またバルブス
プール21はその外周に環状溝21 a、  2 l 
b、  21 cを有し、その径方向に一対の内孔21
d、21eを有している。これにより、各作動液圧室1
5.16に連通した通路25゜26.27は夫々各環状
溝21c、21a、21bに開放されると共に、バルブ
スプール21とバルブシリンダ22間に絞りa、b、c
、dが形成される。
In FIGS. 2 and 3, the control valve device 117
has a valve spool 21 that is slidably housed in a valve cylinder 22 fitted into a lateral hole of the power piston 13 and is slid back and forth via a valve pin 19 by rotation of the input shaft 12. . Valve cylinder 22
A passage 23 that communicates with the hydraulic pump P, a passage 24 that communicates with the reservoir R that stores hydraulic fluid, and a re-operation hydraulic chamber 15.
It has passages 25, 26, and 27 communicating with ゜16,
The passages 23,24 open into annular grooves 22a, 22b formed in the inner bore of the valve cylinder 22. Further, the valve spool 21 has annular grooves 21 a, 2 l on its outer periphery.
b, 21 c, and a pair of inner holes 21 in the radial direction.
d, 21e. As a result, each working hydraulic pressure chamber 1
The passages 25° 26.27 communicating with 5.16 are opened to respective annular grooves 21c, 21a, and 21b, and there are throttles a, b, and c between the valve spool 21 and the valve cylinder 22.
, d are formed.

またバルブスプール21の両端には軸方向の−対の内孔
21d、21eが形成されており、それにより各内孔2
1d、21eとハウジング11間に夫々反力液圧室2B
、29が形成される。各反力液圧室28.29は夫々バ
ルブスプール21に形成されたオリフィス30.31を
介して各環状溝21b、21aに連通しており、これに
より一方の反力液圧室28は一方の作動液圧室15に通
路27を介して連通し、他方の反力液圧室29は他方の
作動液圧室16に通路26を介して連通される。また一
方の反力液圧室28は、第3.4図に示すようにパワー
ピストン13内に形成したバイパス通路32を介して他
方の作動液圧室16に連通され、他方の反力室29も同
様にバイパス通路33を介して一方の作動液圧室15に
連通されている。該バイパス通路32.33内には夫々
、反力液圧室から作動液圧室への液流通を許容し、作動
液圧室から反力液圧室への液流通を遮断する一方向弁3
4.35が介装されている。
Further, a pair of inner holes 21d and 21e in the axial direction are formed at both ends of the valve spool 21, so that each inner hole 2
Reaction force hydraulic pressure chambers 2B are provided between 1d and 21e and the housing 11, respectively.
, 29 are formed. Each reaction pressure chamber 28,29 communicates with each annular groove 21b, 21a via an orifice 30.31 formed in the valve spool 21, so that one reaction force pressure chamber 28 is connected to one of the annular grooves 21b, 21a. It communicates with the working hydraulic pressure chamber 15 through a passage 27, and the other reaction force hydraulic pressure chamber 29 communicates with the other working hydraulic pressure chamber 16 through a passage 26. Further, one reaction force hydraulic pressure chamber 28 is communicated with the other working hydraulic pressure chamber 16 via a bypass passage 32 formed in the power piston 13, as shown in FIG. Similarly, the hydraulic pressure chamber 15 is connected to one of the hydraulic pressure chambers 15 via a bypass passage 33. A one-way valve 3 is provided in each of the bypass passages 32 and 33 to allow fluid flow from the reaction hydraulic pressure chamber to the working hydraulic pressure chamber and to block fluid flow from the working hydraulic pressure chamber to the reaction hydraulic pressure chamber.
4.35 is interposed.

以上の構成から成る本実施例の作用を説明する。The operation of this embodiment having the above configuration will be explained.

中立位置を示す第2図において入力軸12が右回転され
ると、ナツト部材18及びバルブピン19が入力軸12
と一緒に回転して、バルブピン19によりバルブスプー
ル21がバルブシリンダ22内を第2.3図において右
方へ移動される。それにより絞りa、cは更に閉じ、ま
た絞りす、  dは開かれ、液圧ポンプPからの作動液
が通路23−環状溝22b−絞りb−環状溝21b−通
路27の経路を経て一方の作動液圧室15に流入される
と共に、環状溝21bよりオリフィス30を介して一方
の反力液圧室28に流入される。また他方の作動液圧室
16内の作動液は、通路26−環状溝21a−絞りd−
環状溝22a−通路24の経路を経てリザーバRに流出
され、他方の反力液圧室29もまたオリフィス31を介
して環状溝21a−絞りd−環状溝22a−通路24を
経てリザーバに連通される。
When the input shaft 12 is rotated clockwise in FIG. 2 showing the neutral position, the nut member 18 and the valve pin 19 are
The valve pin 19 moves the valve spool 21 inside the valve cylinder 22 to the right in FIG. 2.3. As a result, the restrictors a and c are further closed, and the restrictor d is opened again, and the working fluid from the hydraulic pump P passes through the path of passage 23 - annular groove 22b - restriction b - annular groove 21b - passage 27. It flows into the working hydraulic pressure chamber 15, and also flows into one of the reaction force hydraulic pressure chambers 28 from the annular groove 21b via the orifice 30. The hydraulic fluid in the other hydraulic pressure chamber 16 flows through the passage 26, the annular groove 21a, the throttle d, and the
It flows out to the reservoir R via the annular groove 22a-passage 24 path, and the other reaction force hydraulic pressure chamber 29 also communicates with the reservoir via the annular groove 21a-diaphragm d-annular groove 22a-passage 24 via the orifice 31. Ru.

これにより再作動液圧室15,16内に圧力差が生じ、
該圧力差によってパワーピストン13をナツト部材18
と入力軸12のボール20を介した螺子係合による進行
方向に助勢し移動させる。
This creates a pressure difference within the reactivation hydraulic pressure chambers 15 and 16,
The pressure difference causes the power piston 13 to tighten into the nut member 18.
The input shaft 12 is supported and moved in the advancing direction by screw engagement via the ball 20.

それによってパワーピストン13のラック13aと噛合
するセクタ14aを有した出力軸14を回転させてそれ
に連通される舵取リンク機構が作動させられ、舵取ハン
ドルに印加される操舵力が軽減される。それと同時に、
両反力液圧室28,29間にも圧力差が生じ、バルブス
プール21の外径の断面積にバルブピン19による移動
を妨げる方向に該圧力差が作用し、これが反力として運
転者に伝達され、高速走行時等の車両のフラツキを防止
する。
As a result, the output shaft 14 having the sector 14a meshing with the rack 13a of the power piston 13 is rotated, and the steering link mechanism connected thereto is operated, thereby reducing the steering force applied to the steering wheel. At the same time,
A pressure difference also occurs between the reaction force hydraulic chambers 28 and 29, and this pressure difference acts on the cross-sectional area of the outer diameter of the valve spool 21 in a direction that prevents movement by the valve pin 19, and this is transmitted to the driver as a reaction force. This prevents vehicle fluctuations when driving at high speeds.

ここで、比較的低い走行速度、例えば駐車時等における
舵取操作時においては、路面との摩擦力等による操舵反
力が、上述した両反力液圧室28゜29間の圧力差によ
る反力に加えて舵取ハンドルに付鼻され、大きな操舵反
力が作用する。かかる状態に於いて、一方の反力液圧室
28内の作動液の圧力が一定値を越えると、バイパス通
路32内に介装された一方向弁34の弁部材36がスプ
リング37の付勢力に抗してバイパス通路32の開放す
る方向に移動し、一方の反力液圧室28内の作動液がバ
イパス通路32を介してリザーバRに連通されている他
方の作動液圧室16内に流出される。これにより、両反
力液圧室28.29間の圧力差は低下し、駐車時等にお
ける操舵反力の増大を軽減することができる。
Here, when steering at a relatively low speed, for example when parking, the steering reaction force due to the frictional force with the road surface, etc. In addition to the force, a large steering reaction force acts on the steering wheel. In such a state, when the pressure of the hydraulic fluid in one of the reaction force hydraulic pressure chambers 28 exceeds a certain value, the valve member 36 of the one-way valve 34 interposed in the bypass passage 32 is moved by the biasing force of the spring 37. The hydraulic fluid in one of the reaction force hydraulic pressure chambers 28 moves in the direction in which the bypass passage 32 opens against the flow, and the hydraulic fluid in one of the reaction force hydraulic pressure chambers 28 flows into the other hydraulic pressure chamber 16 that is communicated with the reservoir R via the bypass passage 32. It will be leaked. As a result, the pressure difference between both reaction force hydraulic pressure chambers 28 and 29 is reduced, and an increase in steering reaction force during parking or the like can be reduced.

以上、入力軸12を第2図において右回転させた時の作
動を説明したが、左回転時の作動も同様に液圧ポンプP
からの作動液がバルブスプール21により切替えられ、
他方作動液圧室16に流入されると共にオリフィス31
を介して他方反力液圧室29に流入される。また一方作
動液圧室15はリザ」バRに連通され、一方反力液圧室
28もオリフィス30を介してリザーバRに連通される
The operation when the input shaft 12 is rotated clockwise in FIG.
The hydraulic fluid from is switched by the valve spool 21,
On the other hand, it flows into the working hydraulic pressure chamber 16 and the orifice 31.
The other reaction force flows into the hydraulic pressure chamber 29 via. Further, the working hydraulic pressure chamber 15 is communicated with the reservoir R, and the reaction hydraulic pressure chamber 28 is also communicated with the reservoir R through the orifice 30.

これにより生じる再作動液圧室15,16内の圧力差が
パワーピストン13の断面積に作用し、パワーピストン
13をナツト部材18と入力軸12のボール20を介し
た螺子係合による進行方向に助勢して移動させる。これ
によって舵取ハンドルに印加される操舵力が軽減される
と共に、両反力液圧室28.29間に圧力差が生じ、該
圧力差がバルブスプール21の外径の断面積に作用する
The resulting pressure difference within the re-actuation hydraulic pressure chambers 15 and 16 acts on the cross-sectional area of the power piston 13, causing the power piston 13 to move in the advancing direction through screw engagement via the nut member 18 and the ball 20 of the input shaft 12. Assist and move. As a result, the steering force applied to the steering wheel is reduced, and a pressure difference is created between the reaction pressure chambers 28 and 29, which pressure difference acts on the cross-sectional area of the outer diameter of the valve spool 21.

これによりバルブスプール21はバルブビン19により
移動させられる方向とは逆方向に力が作用し、これが反
力として運転者に伝達される。この反力を与える他方反
力液圧室29内の圧力が所定値を越えると、一方向弁3
5が開弁じバイパス通路33が開かれ、リザーバRに連
通された一方作動液圧室15に他方反力液圧室29内の
作動液がバイパス通路33より流出される。これによっ
て、両反力液圧室28,29間の圧力差が低下し、操舵
反力の増大を適切に抑制することができる。
As a result, a force acts on the valve spool 21 in a direction opposite to the direction in which it is moved by the valve bin 19, and this force is transmitted to the driver as a reaction force. When the pressure in the other reaction force hydraulic pressure chamber 29 that provides this reaction force exceeds a predetermined value, the one-way valve 3
When the valve 5 is opened, the bypass passage 33 is opened, and the hydraulic fluid in the reaction hydraulic pressure chamber 29 flows out from the bypass passage 33 into the hydraulic pressure chamber 15 communicating with the reservoir R. As a result, the pressure difference between the reaction force hydraulic chambers 28 and 29 is reduced, and an increase in the steering reaction force can be appropriately suppressed.

以上、本発明の一実施例について説明したが、本発明の
シリンダ装置、コントロールバルブ装置及び入力軸とコ
ントロールバルブ装置の連結構成等は一実施例の構成に
限定されるものでなく、特許請求の範囲に記載した範囲
内で適宜変更できるものである。
Although one embodiment of the present invention has been described above, the cylinder device, the control valve device, and the connection structure between the input shaft and the control valve device of the present invention are not limited to the structure of the one embodiment. It can be changed as appropriate within the range described in the range.

〔発明の効果〕〔Effect of the invention〕

以上、詳述したように、本発明によれば、コントロール
バルブ装置内、特にバルブスプール内に複雑な加工部品
が不要となり、安価に製作できる。
As described in detail above, according to the present invention, complicated machined parts are not required within the control valve device, particularly within the valve spool, and the control valve device can be manufactured at low cost.

また、バルブスプールの外径の断面積に両反力液圧室の
圧力差が作用するため、大きな反力を得ることができる
と共に、バルブスプールの面積すべてがダンピング容積
として利用されるため、バルブスプールの制振効果が極
めて高く、それによりハンドル操作フィーリングが大巾
に向上できる。
In addition, since the pressure difference between the two reaction force hydraulic pressure chambers acts on the cross-sectional area of the outer diameter of the valve spool, it is possible to obtain a large reaction force, and since the entire area of the valve spool is used as damping volume, the valve The vibration damping effect of the spool is extremely high, which greatly improves the steering feel.

【図面の簡単な説明】[Brief explanation of the drawing]

第1図は本発明に従った動力舵取装置の一実施例を示す
縦断面図、第2図は第1図のA−A断面図、第3図は第
2図に示すコントロールバルブ装置の作動説明図、第4
図は第1図のB−B断面図である。 10・・・動力舵取装置、11・・・ハウジング、12
・・・入力軸、13・・・パワーピストン、14・・・
出力軸、15・・・一方作動液圧室、16・・・他方作
動液圧室、17・・・コントロールバルブ装置、18・
・・ナツト部材、19・・・バルブピストン、21・・
・バルブスプール、22・・・バルブシリンダ、28・
・・一方反力液圧室、29・・・他方反力液圧室、30
゜31・・・オリフィス、34.3’5・・・一方向弁
FIG. 1 is a longitudinal cross-sectional view showing one embodiment of the power steering device according to the present invention, FIG. 2 is a cross-sectional view taken along line A-A in FIG. 1, and FIG. Operation diagram, 4th
The figure is a sectional view taken along line BB in FIG. 10... Power steering device, 11... Housing, 12
...Input shaft, 13...Power piston, 14...
Output shaft, 15... One working hydraulic pressure chamber, 16... Other working hydraulic pressure chamber, 17... Control valve device, 18.
...Nut member, 19...Valve piston, 21...
・Valve spool, 22...Valve cylinder, 28・
...One side reaction force hydraulic pressure chamber, 29...The other side reaction force hydraulic pressure chamber, 30
゜31...Orifice, 34.3'5...One-way valve.

Claims (1)

【特許請求の範囲】[Claims] 車両の舵取リンク機構を動かすための往復動型液圧作動
シリンダ装置、該往復動型液圧作動シリンダ作動にリザ
ーバ内の作動液を送るための液圧ポンプ及び該液圧ポン
プに連通した通路と前記リザーバに連通した通路と前記
往復動型液圧作動シリンダの両作動液圧室に連通した通
路とを有したバルブシリンダと、該バルブシリンダに摺
動可能に収納されて入力軸の回転により往復摺動させら
れるバルブスプールとを有して前記入力軸の一方向回転
に応じて前記往復動型液圧作動シリンダの両作動液圧室
の一方作動液圧室に前記液圧ポンプからの作動液を流入
させると共にその他方作動液圧室の作動液を前記リザー
バに流出させ且つ前記入力軸の他方向回転に応じて前記
他方作動液圧室に前記液圧ポンプからの作動液を流入さ
せると共に前記一方作動液圧室の作動液を前記リザーバ
に流出させるコントロールバルブ装置を備えた動力舵取
装置において、前記バルブスプールの両端に一対の反力
液圧室を形成し、該一対の反力液圧室を夫々、前記入力
軸の回転に応じて夫々の対応した前記作動液圧室に夫々
のオリフィスを介して連通させると共に前記作動液圧室
の非対応側の作動液圧室に前記往復動型液圧作動シリン
ダ装置のパワーピストンに設けられ反力液圧室から作動
液圧室への液流通を許容し、作動液圧室から反力液圧室
への液流通を遮断する一方向弁を介して連通させた動力
舵取装置。
A reciprocating hydraulic cylinder device for moving a steering linkage mechanism of a vehicle, a hydraulic pump for sending hydraulic fluid in a reservoir to actuate the reciprocating hydraulic cylinder, and a passage communicating with the hydraulic pump. a valve cylinder having a passage communicating with the reservoir and a passage communicating with both working hydraulic pressure chambers of the reciprocating hydraulic actuating cylinder; and a valve spool that is slidable in a reciprocating manner, so that in response to unidirectional rotation of the input shaft, one of the two working hydraulic chambers of the reciprocating hydraulic actuating cylinder receives actuation from the hydraulic pump. The hydraulic fluid is caused to flow into the other hydraulic pressure chamber, and the hydraulic fluid from the other hydraulic pressure chamber is caused to flow out into the reservoir, and the hydraulic fluid from the hydraulic pump is caused to flow into the other hydraulic pressure chamber in response to rotation of the input shaft in the other direction. In the power steering device, the power steering device is provided with a control valve device for causing the hydraulic fluid in the one hydraulic pressure chamber to flow out to the reservoir, wherein a pair of reaction hydraulic pressure chambers are formed at both ends of the valve spool, and the pair of reaction force The hydraulic pressure chambers are respectively communicated with the corresponding working hydraulic pressure chambers via respective orifices in accordance with the rotation of the input shaft, and the reciprocating pressure chambers are communicated with the working hydraulic pressure chambers on the non-corresponding side of the working hydraulic pressure chambers. A one-way valve installed in the power piston of a dynamic hydraulic cylinder device that allows liquid flow from the reaction hydraulic pressure chamber to the working hydraulic pressure chamber, and blocks liquid circulation from the working hydraulic pressure chamber to the reaction hydraulic pressure chamber. Power steering device communicated via a valve.
JP4582087A 1987-02-28 1987-02-28 Power steering device Pending JPS63215463A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP4582087A JPS63215463A (en) 1987-02-28 1987-02-28 Power steering device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP4582087A JPS63215463A (en) 1987-02-28 1987-02-28 Power steering device

Publications (1)

Publication Number Publication Date
JPS63215463A true JPS63215463A (en) 1988-09-07

Family

ID=12729885

Family Applications (1)

Application Number Title Priority Date Filing Date
JP4582087A Pending JPS63215463A (en) 1987-02-28 1987-02-28 Power steering device

Country Status (1)

Country Link
JP (1) JPS63215463A (en)

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