JPH1045010A - Hydraulic power steering device - Google Patents
Hydraulic power steering deviceInfo
- Publication number
- JPH1045010A JPH1045010A JP22058696A JP22058696A JPH1045010A JP H1045010 A JPH1045010 A JP H1045010A JP 22058696 A JP22058696 A JP 22058696A JP 22058696 A JP22058696 A JP 22058696A JP H1045010 A JPH1045010 A JP H1045010A
- Authority
- JP
- Japan
- Prior art keywords
- valve member
- valve
- hydraulic
- steering
- power steering
- 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
- 238000011144 upstream manufacturing Methods 0.000 claims description 12
- 238000006073 displacement reaction Methods 0.000 claims description 10
- 230000002542 deteriorative effect Effects 0.000 abstract 1
- 238000003754 machining Methods 0.000 abstract 1
- 238000000034 method Methods 0.000 abstract 1
- 230000001105 regulatory effect Effects 0.000 description 4
- 230000001276 controlling effect Effects 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 230000005856 abnormality Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Landscapes
- Power Steering Mechanism (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、ロータリー式の油
圧制御弁により操舵補助力発生用油圧アクチュエータに
作用する油圧を制御する油圧パワーステアリング装置に
関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulic power steering apparatus for controlling a hydraulic pressure acting on a hydraulic actuator for generating a steering assist force by a rotary hydraulic control valve.
【０００２】[0002]
【従来の技術】筒状の第１バルブ部材と、この第１バル
ブ部材に操舵抵抗に応じて相対回転可能に挿入される第
２バルブ部材とを備え、その第１バルブ部材の内周と第
２バルブ部材の外周との間に、圧油供給用ポンプ、操舵
補助力発生用油圧アクチュエータ、及びタンクに通じる
と共に、両バルブ部材の相対回転に応じて開度が変化す
る絞り部が形成され、その絞り部の開度変化により操舵
補助力発生用油圧アクチュエータに作用する油圧を制御
可能な油圧パワーステアリング装置が従来から用いられ
ている。2. Description of the Related Art A first valve member having a cylindrical shape and a second valve member inserted into the first valve member so as to be relatively rotatable in accordance with a steering resistance are provided. A throttle portion is formed between the outer periphery of the two valve members and communicates with the pressure oil supply pump, the hydraulic actuator for generating steering assist force, and the tank, and the degree of opening changes according to the relative rotation of the two valve members. Conventionally, a hydraulic power steering device capable of controlling a hydraulic pressure acting on a hydraulic actuator for generating a steering assist force by a change in the opening degree of the throttle portion has been used.
【０００３】そのような油圧パワーステアリング装置に
おいて、ポンプから吐出される圧油の脈動等により第１
バルブ部材と第２バルブ部材とが相対振動し、異常音が
発生するという問題があった。[0003] In such a hydraulic power steering apparatus, the first hydraulic power steering apparatus is caused by pulsation of pressure oil discharged from a pump or the like.
There has been a problem that the valve member and the second valve member relatively vibrate and an abnormal sound is generated.
【０００４】そこで、その第２バルブ部材の外周に形成
した周溝にリング状弾性部材を挿入し、その弾性部材を
介して両バルブ部材を嵌め合わせ、その周溝を上記絞り
部よりもポンプ側に連絡する油溝を第２バルブ部材に形
成することで、そのリング状弾性部材をポンプから供給
される圧油により径方向外方に張って第１バルブ部材の
内周面に押し付け、両バルブ部材の相対振動を規制して
いる（実公平１‐４３９７７公報参照）。Therefore, a ring-shaped elastic member is inserted into a peripheral groove formed on the outer periphery of the second valve member, and the two valve members are fitted through the elastic member. Is formed in the second valve member, so that the ring-shaped elastic member is stretched radially outward by pressure oil supplied from the pump and pressed against the inner peripheral surface of the first valve member. The relative vibration of the member is restricted (see Japanese Utility Model Publication No. 1-4977).
【０００５】[0005]
【発明が解決しようとする課題】上記従来の油圧制御弁
では、リング状弾性部材を挿入する周溝や、その周溝を
ポンプ側に連絡する油溝が必要なため、加工工数が増大
し、さらに、リング状弾性部材が必要なために組み立て
工数や部品点数が増大するという問題がある。In the above-mentioned conventional hydraulic control valve, a circumferential groove for inserting the ring-shaped elastic member and an oil groove for connecting the circumferential groove to the pump side are required. Further, there is a problem that the number of assembly steps and the number of parts increase because the ring-shaped elastic member is required.
【０００６】また、高速走行時や小舵角時等において
は、操舵補助力発生用油圧アクチュエータに作用する油
圧が小さいため、そのリング状弾性部材に作用する油圧
も小さくなる。そのため、運転条件によっては両バルブ
部材の相対振動を充分に低減できないという問題があ
る。Also, when the vehicle is running at high speed or at a small steering angle, the hydraulic pressure acting on the hydraulic actuator for generating the steering assist force is small, so that the hydraulic pressure acting on the ring-shaped elastic member is also small. Therefore, there is a problem that the relative vibration between the two valve members cannot be sufficiently reduced depending on the operating conditions.
【０００７】本発明は上記課題を解決することのできる
油圧パワーステアリング装置を提供することを目的とす
る。An object of the present invention is to provide a hydraulic power steering device that can solve the above-mentioned problems.
【０００８】[0008]
【課題を解決するための手段】本発明は、筒状の第１バ
ルブ部材と、その第１バルブ部材に操舵抵抗に応じて相
対回転可能に挿入される第２バルブ部材とを備え、その
第１バルブ部材の内周と第２バルブ部材の外周との間
に、圧油供給用ポンプ、操舵補助力発生用油圧アクチュ
エータ、及びタンクに通じると共に、両バルブ部材の相
対回転に応じて開度が変化する絞り部が形成され、その
絞り部の開度変化により操舵補助力発生用油圧アクチュ
エータに作用する油圧を制御可能な油圧パワーステアリ
ング装置において、その第１バルブ部材を第２バルブ部
材に油圧によって軸方向から押し付ける手段が設けられ
ていることを特徴とする。According to the present invention, there is provided a cylindrical first valve member, and a second valve member inserted into the first valve member so as to be relatively rotatable according to steering resistance. Between the inner periphery of the first valve member and the outer periphery of the second valve member, the opening communicates with the pressure oil supply pump, the hydraulic actuator for generating steering assist force, and the tank, and the degree of opening increases in accordance with the relative rotation of the two valve members. A variable throttle portion is formed, and in a hydraulic power steering device capable of controlling a hydraulic pressure acting on a steering assist force generating hydraulic actuator by a change in the opening degree of the throttle portion, the first valve member is connected to the second valve member by hydraulic pressure. It is characterized in that a means for pressing from the axial direction is provided.
【０００９】その第１バルブ部材を第２バルブ部材に油
圧によって軸方向から押し付けることで、その軸方向に
直交する面における両バルブ部材の相対変位を規制する
摩擦抵抗が発生するので、両バルブ部材の相対振動を規
制できる。その第１バルブ部材の第２バルブ部材への押
し付け方向は軸方向であるので、第１バルブ部材の内周
と第２バルブ部材の外周とが互いにこじれることはな
く、両バルブ部材の円滑な相対回転が阻害されることは
ない。By pressing the first valve member against the second valve member in the axial direction by hydraulic pressure, a frictional resistance is generated which regulates the relative displacement of the two valve members in a plane perpendicular to the axial direction. Relative vibration can be regulated. Since the direction in which the first valve member is pressed against the second valve member is the axial direction, the inner periphery of the first valve member and the outer periphery of the second valve member are not squeezed from each other, so that the two valve members can smoothly move relative to each other. The rotation is not hindered.
【００１０】その絞り部とタンクとの間の圧油戻り流路
に固定絞り部が、この固定絞り部の上流側と下流側との
圧力差によって第１バルブ部材が第２バルブ部材に軸方
向から押し付けられるように設けられているのが好まし
い。これにより、その第１バルブ部材の第２バルブ部材
への押し付け力を、操舵補助力発生用油圧アクチュエー
タに作用する油圧の大きさに拘らず、その固定絞り部の
上下流側の圧力差に対応する適当な値とすることができ
る。A fixed throttle portion is provided in a pressure oil return flow path between the throttle portion and the tank, and a first valve member is axially moved to a second valve member by a pressure difference between an upstream side and a downstream side of the fixed throttle portion. It is preferably provided so as to be pressed from above. Accordingly, the pressing force of the first valve member against the second valve member corresponds to the pressure difference between the upstream and downstream sides of the fixed throttle portion regardless of the magnitude of the hydraulic pressure acting on the hydraulic actuator for generating the steering assist force. It can be set to an appropriate value.
【００１１】本発明において、その第２バルブ部材に、
その第１バルブ部材の軸方向一方への移動を阻止可能な
受け部が設けられ、その受け部を介して第１バルブ部材
は第２バルブ部材に軸方向から押し付けられ、その受け
部と第１バルブ部材との間に、両バルブ部材の相対変位
を規制する摩擦抵抗を増大させる手段が設けられている
のが好ましい。両バルブ部材の相対変位を規制する摩擦
抵抗を増大させることで、両バルブ部材の相対振動をよ
り確実に規制できる。In the present invention, the second valve member includes:
A receiving portion capable of preventing the first valve member from moving in one axial direction is provided. The first valve member is pressed against the second valve member from the axial direction via the receiving portion. It is preferable that means for increasing the frictional resistance for restricting the relative displacement between the two valve members be provided between the valve member and the valve member. By increasing the frictional resistance that regulates the relative displacement between the two valve members, the relative vibration between the two valve members can be more reliably regulated.
【００１２】[0012]
【発明の実施の形態】以下、図１〜図３を参照して本発
明の第１実施形態を説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described below with reference to FIGS.
【００１３】図１に示すラックピニオン式パワーステア
リング装置１は、ステアリングホイール（図示省略）に
連結される入力軸２と、この入力軸２にトーションバー
３を介し連結される出力軸４とを備えている。そのトー
ションバー３はピン５を介し入力軸２に連結され、ま
た、セレーション６を介し出力軸４に連結されている。
その出力軸４にピニオン７が形成され、このピニオン７
に噛み合うラック８が操舵用車輪（図示省略）に連結さ
れている。その入力軸２はベアリング９を介しバルブハ
ウジング１０ａに支持され、また、ブッシュ１１を介し
出力軸４に支持されている。その出力軸４はベアリング
１２、１３を介しラックハウジング１０ｂに支持されて
いる。これにより、操舵による入力軸２の回転がトーシ
ョンバー３を介しピニオン７に伝達されてラック８が車
両幅方向に移動し、このラック８の移動により車輪が操
舵される。なお、その入出力軸２、４とバルブハウジン
グ１０ａとの間にオイルシール１４、１５が設けられて
いる。また、そのラック８を支持するサポートヨーク１
６が設けられ、このサポートヨーク１６はバネ１７の弾
性力によりラック８に押し付けられている。A rack and pinion type power steering device 1 shown in FIG. 1 includes an input shaft 2 connected to a steering wheel (not shown), and an output shaft 4 connected to the input shaft 2 via a torsion bar 3. ing. The torsion bar 3 is connected to the input shaft 2 via a pin 5 and to the output shaft 4 via a serration 6.
A pinion 7 is formed on the output shaft 4.
Is connected to steering wheels (not shown). The input shaft 2 is supported by a valve housing 10 a via a bearing 9, and is supported by an output shaft 4 via a bush 11. The output shaft 4 is supported by the rack housing 10b via bearings 12 and 13. As a result, the rotation of the input shaft 2 due to the steering is transmitted to the pinion 7 via the torsion bar 3, and the rack 8 moves in the vehicle width direction, and the wheels are steered by the movement of the rack 8. Note that oil seals 14, 15 are provided between the input / output shafts 2, 4 and the valve housing 10a. Further, the support yoke 1 for supporting the rack 8
The support yoke 16 is pressed against the rack 8 by the elastic force of a spring 17.
【００１４】操舵補助力を付与する油圧アクチュエータ
として油圧シリンダ１８が設けられている。その油圧シ
リンダ１８はラックハウジング１０ｂにより構成される
シリンダチューブと、ラック８に一体に形成されたピス
トン２０とを備え、そのピストン２０により仕切られる
一対の油室２１、２２が形成されている。各油室２１、
２２にロータリー式油圧制御弁２３が接続されている。
その制御弁２３は、筒状の第１バルブ部材２４と、この
第１バルブ部材２４に相対回転可能に挿入される第２バ
ルブ部材２５とを備えている。その第１バルブ部材２４
は出力軸４にピン２６を介し同行回転可能に取り付けら
れている。その第２バルブ部材２５は入力軸２の外周に
一体に形成されている。これにより、操舵抵抗に応じて
上記トーションバー３が弾性的に捩じれることで、両バ
ルブ部材２４、２５は操舵抵抗に応じて弾性的に相対回
転する。A hydraulic cylinder 18 is provided as a hydraulic actuator for applying a steering assist force. The hydraulic cylinder 18 includes a cylinder tube constituted by a rack housing 10b and a piston 20 formed integrally with the rack 8, and a pair of oil chambers 21 and 22 partitioned by the piston 20 are formed. Each oil chamber 21,
A rotary hydraulic control valve 23 is connected to 22.
The control valve 23 includes a cylindrical first valve member 24 and a second valve member 25 inserted into the first valve member 24 so as to be relatively rotatable. The first valve member 24
Is attached to the output shaft 4 via a pin 26 so as to be rotatable with the output shaft 4. The second valve member 25 is formed integrally with the outer periphery of the input shaft 2. As a result, the torsion bar 3 is elastically twisted according to the steering resistance, so that the two valve members 24 and 25 elastically rotate relative to each other according to the steering resistance.
【００１５】図２、図３に示すように、第１バルブ部材
２４の内周と第２バルブ部材２５の外周とに軸方向に沿
う複数の凹部が周方向等間隔に形成されている。その第
１バルブ部材側凹部は、互いに周方向等間隔に位置する
４つの右操舵用凹部２７と、互いに周方向等間隔に位置
する４つの左操舵用凹部２８とで構成される。その第２
バルブ部材側凹部は、互いに周方向等間隔に位置する４
つの圧油供給用凹部２９と、互いに周方向等間隔に位置
する４つの圧油排出用凹部３０とで構成される。各右操
舵用凹部２７と各左操舵用凹部２８とは周方向に交互に
配置され、各圧油供給用凹部２９と各圧油排出用凹部３
０とは周方向に交互に配置される。各右操舵用凹部２７
は、第１バルブ部材２４に形成された第１流路３１およ
びバルブハウジング１０ａに形成された第１ポート３２
を介し、図１に示すように油圧シリンダ１８の一方の油
室２１に通じ、各左操舵用凹部２８は、第１バルブ部材
２４に形成された第２流路３３およびバルブハウジング
１０ａに形成された第２ポート３４を介し油圧シリンダ
１８の他方の油室２２に通じる。各圧油供給用凹部２９
は、第１バルブ部材２４に形成された第３流路３５およ
びバルブハウジング１０ａに形成された入口ポート３６
を介し、図１に示すようにポンプ３７に通じる。各圧油
排出用凹部３０は第２バルブ部材２５に形成された第１
排出路３８、入力軸２とトーションバー３の内外周間の
通路４７、入力軸２に形成された第２排出路３９、及び
バルブハウジング１０ａに形成された排出ポート４０に
より構成される圧油戻り流路を介しタンク４１に通じ
る。これにより、そのポンプ３７、タンク４１、及び油
圧シリンダ１８の各油室２１、２２が第１バルブ部材２
４と第２バルブ部材２５の内外周間の弁間流路４２を介
して通じる。その第１バルブ部材２４の内周と第２バル
ブ部材２５の外周との間の弁間流路４２において、第１
バルブ部材側凹部と第２バルブ部材側凹部の間は、両バ
ルブ部材２４、２５の相対回転により開度が変化する絞
り部Ａ、Ｂ、Ｃ、Ｄとされている。各絞り部Ａ、Ｂ、
Ｃ、Ｄは、そのポンプ３７、タンク４１、及び油圧シリ
ンダ１８の各油室２１、２２に通じ、各絞り部Ａ、Ｂ、
Ｃ、Ｄの開度変化により油圧シリンダ１８に作用する油
圧が制御される。As shown in FIGS. 2 and 3, a plurality of concave portions along the axial direction are formed on the inner periphery of the first valve member 24 and the outer periphery of the second valve member 25 at equal intervals in the circumferential direction. The first valve member-side recess is composed of four right steering recesses 27 located at equal intervals in the circumferential direction and four left steering recesses 28 located at equal intervals in the circumferential direction. The second
The recesses on the valve member side are located at equal intervals in the circumferential direction.
It is composed of two pressure oil supply recesses 29 and four pressure oil discharge recesses 30 located at equal intervals in the circumferential direction. Each right steering recess 27 and each left steering recess 28 are arranged alternately in the circumferential direction, and each pressure oil supply recess 29 and each pressure oil discharge recess 3
0 is alternately arranged in the circumferential direction. Each right steering recess 27
A first flow path 31 formed in the first valve member 24 and a first port 32 formed in the valve housing 10a.
As shown in FIG. 1, each of the left steering recesses 28 communicates with one of the oil chambers 21 of the hydraulic cylinder 18 through the second passage 33 formed in the first valve member 24 and the valve housing 10 a. Through the second port 34 to the other oil chamber 22 of the hydraulic cylinder 18. Each pressure oil supply recess 29
Is a third flow path 35 formed in the first valve member 24 and an inlet port 36 formed in the valve housing 10a.
Through the pump 37 as shown in FIG. Each pressurized oil discharge recess 30 is formed by a first valve member 25 formed in the second valve member 25.
A pressure oil return constituted by a discharge passage 38, a passage 47 between the input shaft 2 and the inner and outer peripheries of the torsion bar 3, a second discharge passage 39 formed in the input shaft 2, and a discharge port 40 formed in the valve housing 10a. It communicates with the tank 41 via the flow path. Thereby, the pump 37, the tank 41, and the oil chambers 21 and 22 of the hydraulic cylinder 18 are connected to the first valve member 2 respectively.
4 and the second valve member 25 through an inter-valve flow path 42 between the inner and outer circumferences. In the inter-valve flow path 42 between the inner periphery of the first valve member 24 and the outer periphery of the second valve member 25, the first
Between the valve member-side concave portion and the second valve member-side concave portion, there are formed throttle portions A, B, C, and D whose opening degree changes by relative rotation of the two valve members 24 and 25. Each of the apertures A, B,
C and D communicate with the pump 37, the tank 41, and the respective oil chambers 21 and 22 of the hydraulic cylinder 18, and each of the throttle portions A, B,
The hydraulic pressure acting on the hydraulic cylinder 18 is controlled by the change in the opening degree of C and D.
【００１６】図２は、直進状態での両バルブ部材２４、
２５の相対位置を示しており、この状態においては各圧
油供給用凹部２９と各圧油排出用凹部３０とが全絞り部
Ａ、Ｂ、Ｃ、Ｄを介して通じるため、ポンプ３７から供
給された圧油は直接タンク４１へ還流し操舵補助力は発
生しない。直進状態から右方へ操舵すると、操舵トルク
に応じトーションバー３は捩じれ、両バルブ部材２４、
２５は相対回転する。その結果、各右操舵用凹部２７と
各圧油供給用凹部２９との間の絞り部Ａの開度および各
左操舵用凹部２８と各圧油排出用凹部３０との間の絞り
部Ｂの開度が大きくなり、各左操舵用凹部２８と各圧油
供給用凹部２９との間の絞り部Ｃの開度および各右操舵
用凹部２７と各圧油排出用凹部３０との間の絞り部Ｄの
開度が小さくなる。これにより、ポンプ３７から油圧シ
リンダ１８の一方の油室２１へ圧油が供給され、油圧シ
リンダ１８の他方の油室２２よりタンク４１へ圧油が還
流され、車両の右方への操舵補助力がラック８に作用す
る。直進状態から左方へ操舵すると、各絞り部Ａ、Ｂ、
Ｃ、Ｄの開度は右方へ操舵した場合と逆に変化するの
で、車両の左方への操舵補助力がラック８に作用する。FIG. 2 shows both valve members 24 in a straight running state.
25. In this state, the pressure oil supply recess 29 and the pressure oil discharge recess 30 communicate with each other through all the throttle portions A, B, C, and D. The supplied pressure oil is directly returned to the tank 41 and no steering assist force is generated. When the vehicle is steered to the right from the straight traveling state, the torsion bar 3 is twisted in accordance with the steering torque, and the two valve members 24,
25 relatively rotates. As a result, the opening degree of the throttle portion A between each right steering recess 27 and each pressure oil supply recess 29 and the throttle portion B between each left steering recess 28 and each pressure oil discharge recess 30 are formed. The opening degree increases, and the opening degree of the throttle portion C between each left steering recess 28 and each pressure oil supply recess 29 and the throttle between each right steering recess 27 and each pressure oil discharge recess 30. The opening degree of the portion D is reduced. As a result, pressure oil is supplied from the pump 37 to one oil chamber 21 of the hydraulic cylinder 18, and the pressure oil is recirculated from the other oil chamber 22 of the hydraulic cylinder 18 to the tank 41, and the steering assist force to the right of the vehicle is provided. Acts on the rack 8. When steered to the left from the straight running state, each of the throttle portions A, B,
Since the opening degrees of C and D change oppositely to the case of steering to the right, the steering assisting force of the vehicle to the left acts on the rack 8.
【００１７】その第１バルブ部材２４を第２バルブ部材
２５に油圧によって軸方向から押し付ける手段が設けら
れている。すなわち、図３に示すように、第２バルブ部
材２５の外周に止め輪６１が嵌め合わされ、この止め輪
６１の一端面は、第１バルブ部材２４の一端面に接する
ことで、その第１バルブ部材２４の軸方向一方（図３に
おいて上方）への移動を阻止可能な受け部６１ａとされ
ている。上記圧油戻り流路における第２排出路３９の下
流側は、小径の筒状部材が挿入されることで固定絞り部
３９ａとされている。その固定絞り部３９ａによりタン
ク４１に還流する圧油が絞られることで、その固定絞り
部３９ａの上流側圧力は下流側圧力よりも高くなる。そ
の固定絞り部３９ａの上流側は、入力軸２とトーション
バー３の内外周間の通路４７、および上記ブッシュ１１
と入力軸２または出力軸４との間の隙間を介して、第１
バルブ部材２４の他端側（図３において下方側）の上流
側空間５２に通じる。その固定絞り部３９ａの下流側
は、第１バルブ部材２４の一端側（図３において上方
側）の下流側空間５１に通じる。これにより、その固定
絞り部３９ａの上流側と下流側との圧力差によって、第
１バルブ部材２４は第２バルブ部材２５に上記受け部６
１ａを介して軸方向から押し付けられ、その軸方向に直
交する面における両バルブ部材２４、２５の相対変位を
規制する摩擦抵抗を発生させることができる。例えば、
その固定絞り部３９ａの上下流での圧力差をオイルのシ
ール機能に支障がないように２ｋｇｆ／ｃｍ2 とし、そ
の上流側空間５２における第１バルブ部材２４の受圧面
積を６．２ｃｍ2 、その受け部６１ａと第１バルブ部材
２４との間の摩擦係数を０．２、その受け部６１ａの外
径と内径とを平均した直径を２．６ｃｍとした場合、２
×６．２×０．２×１．３＝３．２２４ｋｇｆ．ｃｍの
トルクを、両バルブ部材２４、２５の相対変位を規制す
る負荷トルクとして発生させることができる。A means is provided for pressing the first valve member 24 against the second valve member 25 from the axial direction by hydraulic pressure. That is, as shown in FIG. 3, a retaining ring 61 is fitted around the outer periphery of the second valve member 25, and one end surface of the retaining ring 61 contacts one end surface of the first valve member 24, so that the first valve The receiving portion 61a can prevent the member 24 from moving in one axial direction (upward in FIG. 3). The fixed throttle portion 39a is formed by inserting a small-diameter tubular member downstream of the second discharge passage 39 in the pressure oil return flow passage. The pressure oil flowing back to the tank 41 is throttled by the fixed throttle portion 39a, so that the upstream pressure of the fixed throttle portion 39a becomes higher than the downstream pressure. On the upstream side of the fixed throttle portion 39a, the passage 47 between the input shaft 2 and the inner and outer circumferences of the torsion bar 3 and the bush 11
Through a gap between the input shaft 2 and the output shaft 4
It communicates with the upstream space 52 on the other end side (the lower side in FIG. 3) of the valve member 24. The downstream side of the fixed throttle portion 39a communicates with the downstream space 51 on one end side (upper side in FIG. 3) of the first valve member 24. Thereby, the first valve member 24 causes the second valve member 25 to receive the receiving portion 6 by the pressure difference between the upstream side and the downstream side of the fixed throttle section 39a.
It is possible to generate frictional resistance that is pressed from the axial direction via 1a and restricts the relative displacement between the two valve members 24 and 25 on a plane perpendicular to the axial direction. For example,
The pressure difference between the upstream and downstream of the fixed throttle portion 39a is set to 2 kgf / cm 2 so as not to interfere with the oil sealing function, and the pressure receiving area of the first valve member 24 in the upstream space 52 is 6.2 cm 2 . When the friction coefficient between the receiving portion 61a and the first valve member 24 is 0.2 and the average diameter of the outer and inner diameters of the receiving portion 61a is 2.6 cm, 2
× 6.2 × 0.2 × 1.3 = 3.224 kgf. cm of torque can be generated as a load torque that regulates the relative displacement between the two valve members 24 and 25.
【００１８】本実施形態では、両バルブ部材２４、２５
の相対変位を規制する摩擦抵抗を増大させることができ
るように、その受け部６１ａと第１バルブ部材２４との
間において、その受け部６１ａにローレットが形成され
ている。In this embodiment, both valve members 24, 25
A knurl is formed in the receiving portion 61a between the receiving portion 61a and the first valve member 24 so as to increase the frictional resistance that restricts the relative displacement of the first and second valve members.
【００１９】上記構成によれば、第１バルブ部材２４を
第２バルブ部材２５に油圧によって軸方向から押し付け
ることで、両バルブ部材２４、２５の相対変位を規制す
る摩擦抵抗を発生することができるので、両バルブ部材
２４、２５の相対振動を規制して異常音の発生を防止で
きる。また、その第１バルブ部材２４の第２バルブ部材
２５への押し付け方向は軸方向であるので、第１バルブ
部材２４の内周と第２バルブ部材２５の外周とが互いに
こじれることはなく、両バルブ部材２４、２５の円滑な
相対回転が阻害されることはないので、操舵フィーリン
グが低下することはない。また、その第１バルブ部材２
４の第２バルブ部材２５への押し付け力を、操舵補助力
発生用油圧シリンダ１８に作用する油圧の大きさに拘ら
ず、固定絞り部３９ａの上下流側の圧力差に対応する適
当な値とすることができる。さらに、その第１バルブ部
材２４と受け部６１ａとの間にローレットを設けて両バ
ルブ部材２４、２５の相対変位を規制する摩擦抵抗を増
大させることで、両バルブ部材２４、２５の相対振動を
より確実に規制できる。According to the above configuration, by pressing the first valve member 24 against the second valve member 25 in the axial direction by hydraulic pressure, it is possible to generate frictional resistance for regulating the relative displacement between the two valve members 24, 25. Therefore, the relative vibration between the two valve members 24 and 25 can be restricted to prevent the generation of abnormal noise. Further, since the direction in which the first valve member 24 is pressed against the second valve member 25 is the axial direction, the inner periphery of the first valve member 24 and the outer periphery of the second valve member 25 are not squeezed from each other. Since the smooth relative rotation of the valve members 24 and 25 is not hindered, the steering feeling does not deteriorate. Also, the first valve member 2
The pressing force on the second valve member 25 of No. 4 is set to an appropriate value corresponding to the pressure difference between the upstream and downstream sides of the fixed throttle portion 39a regardless of the magnitude of the hydraulic pressure acting on the hydraulic cylinder 18 for generating the steering assist force. can do. Furthermore, a knurl is provided between the first valve member 24 and the receiving portion 61a to increase the frictional resistance that regulates the relative displacement between the two valve members 24 and 25, thereby reducing the relative vibration between the two valve members 24 and 25. It can be regulated more reliably.
【００２０】図４は本発明の第２実施形態を示す。上記
実施形態との相違は、第２排出路３９の下流側を固定絞
り部３９ａとするのに代えて、その第２排出路３９の上
流においてトーションバー３の一部を大径部３ａとする
ことで、入力軸２とトーションバー３の内外周間の通路
４７の一部を固定絞り部３９ａ′とした点にある。他は
第１実施形態と同様の構成で、同一の作用効果を奏する
ことができる。FIG. 4 shows a second embodiment of the present invention. The difference from the above embodiment is that, instead of using the fixed throttle portion 39a on the downstream side of the second discharge passage 39, a part of the torsion bar 3 is formed on the large diameter portion 3a upstream of the second discharge passage 39. Thus, a part of the passage 47 between the input shaft 2 and the inner and outer peripheries of the torsion bar 3 is a fixed throttle portion 39a '. Otherwise, the configuration is the same as that of the first embodiment, and the same operation and effect can be obtained.
【００２１】なお、本発明は上記実施形態に限定されな
い。例えば、受け部と第１バルブ部材との間にゴムリン
グ等の摩擦係数の大きな部材を介在させることで、両バ
ルブ部材の相対変位を規制する摩擦抵抗を増大させても
よい。また、上記のような圧油戻り流路に代えて、各圧
油排出用凹部３０を下流側空間５１と上流側空間５２と
に連絡する延長凹部を第２バルブ部材２５に設け、その
延長凹部を圧油戻り流路の一部とし、その下流側空間５
１との連絡用の延長凹部に固定絞り部を設けてもよい。
また、本発明をボールスクリュー式油圧パワーステアリ
ング装置に適用してもよい。The present invention is not limited to the above embodiment. For example, by interposing a member having a large friction coefficient, such as a rubber ring, between the receiving portion and the first valve member, the frictional resistance that regulates the relative displacement between the two valve members may be increased. Further, instead of the above-described pressure oil return flow path, an extension recess connecting each pressure oil discharge recess 30 to the downstream space 51 and the upstream space 52 is provided in the second valve member 25, and the extension recess is provided. Is a part of the pressure oil return flow path, and its downstream space 5
A fixed throttle portion may be provided in the extension concave portion for communication with the device 1.
Further, the present invention may be applied to a ball screw type hydraulic power steering device.
【００２２】[0022]
【発明の効果】本発明の油圧パワーステアリング装置に
よれば、部品の加工工数、組み立て工数、部品点数を増
大させることなく、操舵フィーリングを低下させること
なく、さらに、運転条件に拘らず、異常音の発生を防止
できる。According to the hydraulic power steering apparatus of the present invention, abnormalities can be obtained without increasing the number of processing steps, assembling steps, and the number of parts, reducing the steering feeling, and irrespective of the driving conditions. Generation of sound can be prevented.
【図１】本発明の第１実施形態の油圧パワーステアリン
グ装置の断面図FIG. 1 is a sectional view of a hydraulic power steering device according to a first embodiment of the present invention.
【図２】図１のＩＩ‐ＩＩ線断面図FIG. 2 is a sectional view taken along line II-II of FIG.
【図３】本発明の第１実施形態の油圧パワーステアリン
グ装置の要部の断面図FIG. 3 is a sectional view of a main part of the hydraulic power steering device according to the first embodiment of the present invention.
【図４】本発明の第２実施形態の油圧パワーステアリン
グ装置の要部の断面図FIG. 4 is a sectional view of a main part of a hydraulic power steering device according to a second embodiment of the present invention.
１８ 油圧シリンダ ２４ 第１バルブ部材 ２５ 第２バルブ部材 ３７ ポンプ ３９ａ 固定絞り部 ４１ タンク ６１ａ 受け部 Ａ、Ｂ、Ｃ、Ｄ 絞り部 18 Hydraulic cylinder 24 First valve member 25 Second valve member 37 Pump 39a Fixed throttle unit 41 Tank 61a Receiving unit A, B, C, D Throttle unit
Claims (3)
ブ部材に操舵抵抗に応じて相対回転可能に挿入される第
２バルブ部材とを備え、 その第１バルブ部材の内周と第２バルブ部材の外周との
間に、圧油供給用ポンプ、操舵補助力発生用油圧アクチ
ュエータ、及びタンクに通じると共に、両バルブ部材の
相対回転に応じて開度が変化する絞り部が形成され、 その絞り部の開度変化により操舵補助力発生用油圧アク
チュエータに作用する油圧を制御可能な油圧パワーステ
アリング装置において、 その第１バルブ部材を第２バルブ部材に油圧によって軸
方向から押し付ける手段が設けられていることを特徴と
する油圧パワーステアリング装置。A first valve member having a cylindrical shape, and a second valve member inserted into the first valve member so as to be relatively rotatable in accordance with a steering resistance; and an inner periphery of the first valve member and a second valve member. A throttle portion is formed between the outer periphery of the two valve members and communicates with the pressure oil supply pump, the hydraulic actuator for generating steering assist force, and the tank, and the degree of opening changes according to the relative rotation of the two valve members. In a hydraulic power steering device capable of controlling a hydraulic pressure acting on a steering assist force generating hydraulic actuator by a change in the opening degree of the throttle, a means is provided for pressing the first valve member against the second valve member in the axial direction by hydraulic pressure. A hydraulic power steering device comprising:
路に固定絞り部が、この固定絞り部の上流側と下流側と
の圧力差によって第１バルブ部材が第２バルブ部材に軸
方向から押し付けられるように設けられている請求項１
に記載の油圧パワーステアリング装置。2. A fixed throttle portion is provided in a pressure oil return flow path between the throttle portion and the tank, and a first valve member is connected to a second valve member by a pressure difference between an upstream side and a downstream side of the fixed throttle portion. 2. The device according to claim 1, wherein the pressing member is provided so as to be pressed from an axial direction.
2. The hydraulic power steering device according to claim 1.
部材の軸方向一方への移動を阻止可能な受け部が設けら
れ、 その受け部を介して第１バルブ部材は第２バルブ部材に
押し付けられ、 その受け部と第１バルブ部材との間に、両バルブ部材の
相対変位を規制する摩擦抵抗を増大させる手段が設けら
れている請求項１または２に記載の油圧パワーステアリ
ング装置。3. The second valve member is provided with a receiving portion capable of preventing the first valve member from moving in one axial direction, and the first valve member is connected to the second valve member through the receiving portion. 3. The hydraulic power steering apparatus according to claim 1, wherein a means for increasing frictional resistance is provided between the receiving portion and the first valve member so as to restrict relative displacement between the two valve members.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22058696A JP3681829B2 (en) | 1996-08-01 | 1996-08-01 | Hydraulic power steering device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22058696A JP3681829B2 (en) | 1996-08-01 | 1996-08-01 | Hydraulic power steering device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH1045010A true JPH1045010A (en) | 1998-02-17 |
| JP3681829B2 JP3681829B2 (en) | 2005-08-10 |
Family
ID=16753302
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22058696A Expired - Fee Related JP3681829B2 (en) | 1996-08-01 | 1996-08-01 | Hydraulic power steering device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3681829B2 (en) |
-
1996
- 1996-08-01 JP JP22058696A patent/JP3681829B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP3681829B2 (en) | 2005-08-10 |
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