JP2005247290A - Hydraulic power steering device - Google Patents

Hydraulic power steering device Download PDF

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JP2005247290A
JP2005247290A JP2004266366A JP2004266366A JP2005247290A JP 2005247290 A JP2005247290 A JP 2005247290A JP 2004266366 A JP2004266366 A JP 2004266366A JP 2004266366 A JP2004266366 A JP 2004266366A JP 2005247290 A JP2005247290 A JP 2005247290A
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input
moving body
output shaft
elastic member
axial direction
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Hiroji Ueda
博二 植田
Masafumi Uota
雅史 魚田
Kazuhiro Watanabe
和宏 渡邉
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Koyo Seiko Co Ltd
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Koyo Seiko Co Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To vary the steering auxiliary characteristic according to a driving state of a vehicle without requiring a complex structure or reducing steering feeling. <P>SOLUTION: A hydraulic control valve 30 controls the oil pressure of pressure oil supplied to a hydraulic actuator 20 for generating a steering auxiliary force according to an elastic relative rotation amount of input/outputs 2 and 3 according to the steering torque. A moving mechanism 50 has a moving body 51 moving by an amount according to the driving state of the vehicle. An elastic member 70 generates an elastic force for regulating a relative rotation of the input/outputs 2 and 3 according to the relative rotation amount. A rigidity adjusting mechanism 80 adjusts the rigidity of the elastic member 70 so that the generated elastic force of the elastic member 70 changes according to the moving amount of the moving body 51. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、車速等の運転状態に応じて操舵補助特性を変更可能な油圧パワーステアリング装置に関する。   The present invention relates to a hydraulic power steering apparatus capable of changing a steering assist characteristic in accordance with a driving state such as a vehicle speed.

操舵補助力発生用油圧アクチュエータに供給される圧油の油圧を、操舵トルクに応じた入力シャフトと出力シャフトの弾性的な相対回転量に応じて制御する油圧制御バルブを備える油圧パワーステアリング装置においては、操舵トルクに応じて操舵補助特性を変化させることができる。そのような油圧パワーステアリング装置において、車速等の運転状態に応じて操舵補助力を変化させることで、高車速での走行安定性や低車速での操舵に対する応答性を向上することが図られている。   In a hydraulic power steering apparatus including a hydraulic control valve that controls the hydraulic pressure of pressure oil supplied to a hydraulic actuator for generating steering assist force according to the elastic relative rotational amount of an input shaft and an output shaft according to a steering torque. The steering assist characteristic can be changed according to the steering torque. In such a hydraulic power steering device, by changing the steering assist force according to the driving state such as the vehicle speed, it is possible to improve the running stability at a high vehicle speed and the responsiveness to the steering at a low vehicle speed. Yes.

例えば、トーションバーの捩れによるアウタ側のバルブ構成要素とインナ側のバルブ構成要素の相対回転量に応じて油圧を制御するロータリー型油圧制御バルブを備える油圧パワーステアリング装置において、そのトーションバーの捩れ角度を両バルブ構成要素の相対回転角度に変換する際に、その変換率を車速に応じて変化させる変換機構を設けることや（特許文献１参照）、アウタ側のバルブ構成要素の回転を車速に応じて規制する負荷をシャフト軸方向から転がり軸受を介して付与する負荷付与装置を設けること（特許文献２参照）が提案されている。
特開平７−１１７６９４号公報 特開平１０−１６８０５号公報 For example, in a hydraulic power steering apparatus including a rotary hydraulic control valve that controls oil pressure according to the relative rotation amount of an outer side valve component and an inner side valve component due to torsion bar twisting, the twist angle of the torsion bar Is converted to the relative rotation angle of both valve components, a conversion mechanism is provided for changing the conversion rate according to the vehicle speed (see Patent Document 1), and the rotation of the valve component on the outer side is determined according to the vehicle speed. It has been proposed to provide a load applying device that applies a load to be regulated from the shaft axial direction via a rolling bearing (see Patent Document 2).
JP-A-7-117694 Japanese Patent Laid-Open No. 10-16805

トーションバーの捩れ角度と両バルブ構成要素の相対回転角度との間の変換率を変化させる変換機構は、その相対回転を伝達するピンを支持する複数の球面軸受けと、その支持位置を変化させる機構を備え、その支持位置の変化により変換率を変化させるものであるため構造が極めて複雑になり、重量、コストが増大する。バルブ構成要素の回転を規制する負荷を転がり軸受を介して付与する場合、軸受構成部材間の摩擦やがたにより操舵フィーリングが低下する。本発明は、そのような従来技術の問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。   The conversion mechanism that changes the conversion rate between the torsion angle of the torsion bar and the relative rotation angle of both valve components includes a plurality of spherical bearings that support pins that transmit the relative rotation, and a mechanism that changes the support position. Since the conversion rate is changed by changing the support position, the structure becomes extremely complicated, and the weight and cost increase. When a load that restricts the rotation of the valve component is applied via the rolling bearing, the steering feeling is reduced due to friction and play between the bearing components. It is an object of the present invention to provide a hydraulic power steering apparatus that can solve such problems of the prior art.

本発明の油圧パワーステアリング装置は、入力シャフトと、前記入力シャフトに操舵トルクに応じて弾性的に相対回転可能に連結される出力シャフトと、操舵補助力発生用油圧アクチュエータと、前記油圧アクチュエータに供給される圧油の油圧を、前記入出力シャフトの相対回転量に応じて制御する油圧制御バルブと、車両の運転状態に応じた量だけ移動する移動体を有する移動機構と、前記入出力シャフトの相対回転を規制する弾力を、その相対回転量に応じて発生する弾性部材と、前記移動体の移動量に応じて前記弾力が変化するように前記弾性部材の剛性を調節する剛性調節機構とを備える。
本発明によれば、操舵トルクの作用により入出力シャフトは相対回転し、その入出力シャフトの相対回転は弾性部材の発生弾力により規制され、その弾性部材の剛性は車両の運転状態に応じた量の移動体の移動により調節される。よって、車両の運転状態に応じて入出力シャフトの相対回転量が変化し、油圧制御バルブにより制御される操舵補助力発生用の油圧が変化する。その移動機構は車両の運転状態に応じて油圧の大きさを調節する油圧調節機構を有し、油圧調節機構による調節油圧の大きさに応じて移動体を移動させるのが好ましい。 The hydraulic power steering device according to the present invention supplies an input shaft, an output shaft connected to the input shaft so as to be elastically rotatable relative to the input shaft, a steering assist force generating hydraulic actuator, and the hydraulic actuator A hydraulic control valve that controls the hydraulic pressure of the pressurized oil according to the relative rotation amount of the input / output shaft, a moving mechanism that has a moving body that moves by an amount according to the driving state of the vehicle, An elastic member that generates an elastic force that restricts relative rotation according to the amount of relative rotation, and a rigidity adjustment mechanism that adjusts the rigidity of the elastic member so that the elastic force changes according to the amount of movement of the moving body. Prepare.
According to the present invention, the input / output shaft is relatively rotated by the action of the steering torque, the relative rotation of the input / output shaft is regulated by the elastic force generated by the elastic member, and the rigidity of the elastic member is an amount corresponding to the driving state of the vehicle. It is adjusted by the movement of the moving body. Therefore, the relative rotation amount of the input / output shaft changes according to the driving state of the vehicle, and the hydraulic pressure for generating the steering assist force controlled by the hydraulic control valve changes. It is preferable that the moving mechanism has a hydraulic pressure adjusting mechanism that adjusts the hydraulic pressure according to the driving state of the vehicle, and the moving body is moved according to the hydraulic pressure adjusted by the hydraulic adjusting mechanism.

前記移動体は、前記入出力シャフトに対して軸方向移動すると共に前記入出力シャフトの中の一方に同行回転するように連結され、前記弾性部材は、前記入出力シャフトの軸心から偏心した位置で前記入出力シャフトの中の他方と同行回転する固定端と、固定端から入出力シャフトの軸方向に離れた自由端を有し、前記剛性調節機構は、前記移動体と同行回転すると共に軸方向に同行移動する押し付け部を有し、前記押し付け部は、前記入出力シャフトの相対回転により前記弾性部材を押し付ける位置に配置され、前記押し付け部の押し付けによる前記弾性部材の弾性的な曲げ変形により前記弾力が発生され、前記入出力シャフトの軸方向における前記押し付け部による押し付け位置の変化に応じて、前記弾性部材の曲げ剛性が変化するのが好ましい。これにより、弾性部材として入出力シャフトの相対回転方向の曲げ変形により弾力を発生するものを用いることができる。   The moving body is axially moved with respect to the input / output shaft and connected to one of the input / output shafts so as to rotate together. The elastic member is a position eccentric from the axis of the input / output shaft. A fixed end that rotates together with the other of the input / output shafts, and a free end that is separated from the fixed end in the axial direction of the input / output shaft, and the rigidity adjusting mechanism rotates together with the movable body and has a shaft. A pressing portion that moves in the same direction, and the pressing portion is disposed at a position where the elastic member is pressed by relative rotation of the input / output shaft, and the elastic member is elastically deformed by the pressing of the pressing portion. The elastic force is generated, and the bending rigidity of the elastic member changes according to the change of the pressing position by the pressing portion in the axial direction of the input / output shaft. Masui. Accordingly, an elastic member that generates elasticity by bending deformation in the relative rotation direction of the input / output shaft can be used.

前記移動体は、前記入出力シャフトに対して軸方向移動すると共に前記入出力シャフトの軸方向の間隔をおいて相対配置される第１移動体片と第２移動体片とを有し、前記第１移動体片と前記第２移動体片は、車両の運転状態に応じた量だけ互いに逆方向に移動し、前記剛性調節機構は、前記両移動体片の間において、前記入力シャフトと出力シャフトの中の一方にねじ合わされると共に、他方に同行回転かつ軸方向相対移動可能に連結される変位部材を有し、前記弾性部材は、前記第１移動体片と前記変位部材との間に配置される第１バネ片と、前記第２移動体片と前記変位部材との間に配置される第２バネ片とを有し、前記変位部材は、前記入出力シャフトの相対回転により前記入出力シャフトに対して軸方向変位され、前記変位部材の変位による前記各バネ片の前記入出力シャフトの軸方向に沿った弾性変形により前記弾力が発生され、前記各バネ片は、前記入出力シャフトの軸方向に沿った弾性変形量に応じて縦弾性係数が変化する非線形バネとされているのが好ましい。これにより、弾性部材として入出力シャフトの軸方向の変形により弾力を発生するものを用いることができる。また、移動体を油圧調節機構による調節油圧の大きさに応じて移動させる場合、移動体を変位させる油圧と弾性部材の弾力とがバランスする位置に移動体を変位させることができる。   The moving body includes a first moving body piece and a second moving body piece that move in the axial direction with respect to the input / output shaft and are disposed relative to each other at an interval in the axial direction of the input / output shaft, The first moving body piece and the second moving body piece move in directions opposite to each other by an amount corresponding to a driving state of the vehicle, and the rigidity adjusting mechanism is arranged between the input shaft and the output between the two moving body pieces. The elastic member is disposed between the first movable body piece and the displacement member. A first spring piece disposed, and a second spring piece disposed between the second moving body piece and the displacement member, and the displacement member is moved by the relative rotation of the input / output shaft. Axially displaced with respect to the output shaft, The elastic force is generated by elastic deformation along the axial direction of the input / output shaft of each spring piece due to the position, and each spring piece is longitudinally elastic according to the amount of elastic deformation along the axial direction of the input / output shaft. It is preferably a non-linear spring whose coefficient changes. Accordingly, an elastic member that generates elasticity by the axial deformation of the input / output shaft can be used. Further, when the moving body is moved according to the magnitude of the adjustment hydraulic pressure by the hydraulic pressure adjusting mechanism, the moving body can be displaced to a position where the hydraulic pressure for displacing the moving body and the elasticity of the elastic member are balanced.

前記移動体は、前記入出力シャフトに対して軸方向移動すると共に前記入出力シャフトの中の一方に同行回転するように連結され、前記剛性調節機構は、前記入出力シャフトの中の他方と同行回転すると共に、前記移動体から前記入出力シャフトの軸方向の間隔をおいて配置される受け部を有し、前記弾性部材は、前記移動体に同行回転するように連結される一端部と前記受け部に同行回転するように連結される他端部とを有し、且つ、前記移動体と前記受け部との間で圧縮され、前記入出力シャフトの相対回転による前記弾性部材の弾性的な捩れ変形により前記弾力が発生され、前記移動体と前記受け部との間での前記入出力シャフトの軸方向における圧縮量の変化に応じて、前記弾性部材の捩れ剛性が変化するのが好ましい。これにより、弾性部材として入出力シャフトの相対回転方向の捩れ変形により弾力を発生するものを用いることができる。しかも、入出力シャフトの相対回転を直接に弾性部材の捩れ変形に変換できるので、構造を簡単化できる。この場合、前記入出力シャフトの径方向における前記弾性部材の変形を阻止する阻止部を備えるのが好ましい。これにより、弾性部材の軸方向圧縮量の変化に応じた捩れ剛性の変化が径方向変形により抑制されるのを防止でき、弾性部材の材料選択範囲を拡げて設計の自由度を増し、また、高速直進走行時における剛性を大きくして走行安定性を向上できる。また、移動体を油圧調節機構による調節油圧の大きさに応じて移動させる場合、移動体を変位させる油圧と弾性部材の弾力とがバランスする位置に移動体を変位させることができる。   The movable body is axially moved with respect to the input / output shaft and connected to one of the input / output shafts so as to rotate together. The rigidity adjusting mechanism is accompanied with the other of the input / output shafts. The elastic member has a receiving portion that is rotated and spaced apart from the moving body in the axial direction of the input / output shaft, and the elastic member is connected to the moving body to rotate together with the one end portion and the The other end connected to the receiving portion so as to rotate together with the receiving portion, and is compressed between the moving body and the receiving portion, and the elastic member is elastically moved by relative rotation of the input / output shaft. It is preferable that the elastic force is generated by torsional deformation, and the torsional rigidity of the elastic member changes according to a change in the compression amount in the axial direction of the input / output shaft between the moving body and the receiving portion. Accordingly, an elastic member that generates elasticity by torsional deformation in the relative rotational direction of the input / output shaft can be used. In addition, since the relative rotation of the input / output shaft can be directly converted into the torsional deformation of the elastic member, the structure can be simplified. In this case, it is preferable to provide a blocking portion for blocking deformation of the elastic member in the radial direction of the input / output shaft. Thereby, it is possible to prevent the change in torsional rigidity according to the change in the axial compression amount of the elastic member from being suppressed by the radial deformation, increase the material selection range of the elastic member and increase the degree of freedom of design, The running stability can be improved by increasing the rigidity during high-speed straight running. Further, when the moving body is moved according to the magnitude of the adjustment hydraulic pressure by the hydraulic pressure adjusting mechanism, the moving body can be displaced to a position where the hydraulic pressure for displacing the moving body and the elasticity of the elastic member are balanced.

本発明の油圧パワーステアリング装置によれば、複雑な構造を要することなく、また、操舵フィーリングを低下させることなく、車両の運転状態に応じて操舵補助特性を変化させることで、重量、コストを低減し、さらに走行安定性を向上できる。   According to the hydraulic power steering device of the present invention, the weight and cost can be reduced by changing the steering assist characteristic according to the driving state of the vehicle without requiring a complicated structure and without lowering the steering feeling. It can be reduced and the running stability can be improved.

図１に示す本発明の第１実施形態のラックピニオン式油圧パワーステアリング装置１は、車両のステアリングホイール（図示省略）に連結される入力シャフト２と、入力シャフト２に操舵トルクに応じて弾性的に相対回転するようトーションバー６を介して同軸心に連結される出力シャフト３を備えている。トーションバー６は入力シャフト２を貫通し、ピン４により入力シャフト２に連結され、セレーション５を介して出力シャフト３に連結される。入力シャフト２の一端側はベアリング８を介してハウジング７により支持される。入力シャフト２の他端側は、出力シャフト３の一端側の端部に形成された凹部に挿入されると共に、その凹部の内周によりブッシュ１２を介して支持される。出力シャフト３は、ベアリング１０、１１を介してハウジング７により回転可能に支持されている。出力シャフト３の他端側外周にピニオン１５が一体的に形成され、ピニオン１５に噛み合うラック１６に車輪（図示省略）が連結される。これにより、操舵による入力シャフト２の回転は、トーションバー６を介してピニオン１５に伝達され、ピニオン１５の回転によりラック１６は車両幅方向に移動し、ラック１６の移動により車両の舵角が変化する。入力シャフト２とハウジング７との間および出力シャフト３とハウジング７との間にオイルシール１７、１８が設けられている。なお、ラック１６を支持するサポートヨーク４０がバネ４１の弾力によりラック１６に押し付けられている。   A rack and pinion type hydraulic power steering apparatus 1 according to the first embodiment of the present invention shown in FIG. 1 includes an input shaft 2 connected to a steering wheel (not shown) of a vehicle, and the input shaft 2 is elastic according to a steering torque. And an output shaft 3 connected coaxially via a torsion bar 6 so as to rotate relative to each other. The torsion bar 6 passes through the input shaft 2, is connected to the input shaft 2 by a pin 4, and is connected to the output shaft 3 through a serration 5. One end side of the input shaft 2 is supported by the housing 7 via a bearing 8. The other end side of the input shaft 2 is inserted into a recess formed at the end portion on the one end side of the output shaft 3 and supported by the inner periphery of the recess via the bush 12. The output shaft 3 is rotatably supported by the housing 7 via bearings 10 and 11. A pinion 15 is integrally formed on the outer periphery of the other end of the output shaft 3, and wheels (not shown) are connected to a rack 16 that meshes with the pinion 15. Thereby, the rotation of the input shaft 2 by steering is transmitted to the pinion 15 through the torsion bar 6, the rack 16 moves in the vehicle width direction by the rotation of the pinion 15, and the steering angle of the vehicle changes by the movement of the rack 16. To do. Oil seals 17 and 18 are provided between the input shaft 2 and the housing 7 and between the output shaft 3 and the housing 7. The support yoke 40 that supports the rack 16 is pressed against the rack 16 by the elasticity of the spring 41.

操舵補助力発生用油圧アクチュエータとして油圧シリンダ２０が設けられている。油圧シリンダ２０は、ハウジング７と一体のシリンダチューブと、ラック１６に一体化されるピストン２１を備え、シリンダチューブ内にピストン２１により仕切られる油室２２、２３が形成されている。   A hydraulic cylinder 20 is provided as a steering assist force generating hydraulic actuator. The hydraulic cylinder 20 includes a cylinder tube integrated with the housing 7 and a piston 21 integrated with the rack 16. Oil chambers 22 and 23 partitioned by the piston 21 are formed in the cylinder tube.

油圧シリンダ２０に供給される圧油の油圧を、入力シャフト２と出力シャフト３の相対回転量に応じて制御するロータリー式油圧制御バルブ３０が設けられている。制御バルブ３０は、ハウジング７に回転可能に挿入されている筒状の第１バルブ部材３１と、第１バルブ部材３１に同軸中心に相対回転可能に挿入されている第２バルブ部材３２を備えている。第１バルブ部材３１は出力シャフト３にピン３３を介して同軸中心に同行回転するよう連結されている。第２バルブ部材３２は入力シャフト２の外周に一体的に成形され、これにより第２バルブ部材３２は入力シャフト２と同軸中心に同行回転する。ハウジング７に、圧油吐出用ポンプ４２に接続されるポート４２ａと、タンク４３に接続されるポート４３ａと、油圧シリンダ２０の一方の油室２２に接続されるポート２２ａと、他方の油室２３に接続されるポート２２ｂが設けられ、各ポートは第１バルブ部材３１と第２バルブ部材３２の間における弁間流路２７を介して互いに連通する。弁間流路２７における絞り部の開度が入出力シャフト２、３の相対回転量に応じて変化する。例えば図２に示すように、制御バルブ３０は、第１バルブ部材３１の内周における複数の第１溝４８の軸方向縁と、第２バルブ部材３２の外周における複数の第２溝４９の軸方向縁との間が絞り部Ａ、Ｂ、Ｃ、Ｄとされる。一方の油室２２に通じる第１溝４８と、他方の油室２３に通じる第１溝４８とが周方向において交互に配置される。ポンプ４２に通じる第２溝４９と、タンク４３に通じる第２溝４９とが周方向において交互に配置される。なお、タンク４３に通じる第２溝４９は、入力シャフト２に形成された油通路２ａと、トーションバー６の外周と入力シャフト２の内周との間を介してタンク４３に接続されるポート４３ａに通じる。これにより、図３に示す油圧回路が構成される。操舵が行なわれていない時は、各絞り部Ａ、Ｂ、Ｃ、Ｄが開き油圧は上昇しないので操舵補助力は発生しない。右操舵時は、入力シャフト２と出力シャフト３の相対回転量に応じて絞り部Ａ、Ｄの開度が大きくなり、絞り部Ｂ、Ｃの開度が小さくなり、一方の油室２２に圧油が供給され、他方の油室２３からタンク４３に油が還流し、その相対回転量に応じた右方向への操舵補助力を油圧シリンダ２０は発生する。左操舵時は、絞り部Ａ、Ｂ、Ｃ、Ｄの開度が右操舵時と逆になり、その相対回転量に応じた左方向への操舵補助力を油圧シリンダ２０は発生する。   A rotary hydraulic control valve 30 that controls the hydraulic pressure of the pressure oil supplied to the hydraulic cylinder 20 according to the relative rotation amount of the input shaft 2 and the output shaft 3 is provided. The control valve 30 includes a cylindrical first valve member 31 that is rotatably inserted into the housing 7, and a second valve member 32 that is inserted into the first valve member 31 so as to be relatively rotatable about a coaxial center. Yes. The first valve member 31 is connected to the output shaft 3 via a pin 33 so as to rotate along the same axis. The second valve member 32 is integrally formed on the outer periphery of the input shaft 2, whereby the second valve member 32 rotates along the same axis as the input shaft 2. The housing 7 includes a port 42 a connected to the pressure oil discharge pump 42, a port 43 a connected to the tank 43, a port 22 a connected to one oil chamber 22 of the hydraulic cylinder 20, and the other oil chamber 23. Ports 22b connected to each other are provided, and each port communicates with each other via an inter-valve flow path 27 between the first valve member 31 and the second valve member 32. The opening degree of the throttle portion in the inter-valve flow path 27 changes according to the relative rotation amount of the input / output shafts 2 and 3. For example, as shown in FIG. 2, the control valve 30 includes axial edges of the plurality of first grooves 48 on the inner periphery of the first valve member 31 and shafts of the plurality of second grooves 49 on the outer periphery of the second valve member 32. Apertures A, B, C, and D are defined between the direction edges. The first grooves 48 communicating with one oil chamber 22 and the first grooves 48 communicating with the other oil chamber 23 are alternately arranged in the circumferential direction. The second grooves 49 that communicate with the pump 42 and the second grooves 49 that communicate with the tank 43 are alternately arranged in the circumferential direction. The second groove 49 communicating with the tank 43 has a port 43a connected to the tank 43 via the oil passage 2a formed in the input shaft 2 and between the outer periphery of the torsion bar 6 and the inner periphery of the input shaft 2. Leads to Thereby, the hydraulic circuit shown in FIG. 3 is configured. When the steering is not performed, the throttle portions A, B, C, and D are opened and the hydraulic pressure does not increase, so that the steering assist force is not generated. During right steering, the apertures of the throttles A and D are increased according to the relative rotation amounts of the input shaft 2 and the output shaft 3, and the apertures of the throttles B and C are decreased. Oil is supplied, the oil flows back to the tank 43 from the other oil chamber 23, and the hydraulic cylinder 20 generates a steering assist force in the right direction corresponding to the relative rotation amount. During left steering, the apertures of the throttles A, B, C, and D are opposite to those during right steering, and the hydraulic cylinder 20 generates a steering assist force in the left direction corresponding to the relative rotation amount.

車両の運転状態に応じた量だけ移動する移動体５１を有する移動機構５０が設けられている。本実施形態の移動体５１は、入出力シャフト２、３に対して軸方向移動すると共に入力シャフト２に同行回転するように連結され、出力シャフト３に対して相対回転し、車両の運転状態に応じて油圧の大きさを調節する油圧調節機構６０による調節油圧の大きさに応じて移動する。すなわち、図４、図５に示すように、移動体５１は円筒形状を有し、制御バルブ３０の上方においてハウジング７に軸方向相対移動可能に挿入され、その中心孔に入力シャフト２が同心に軸方向相対移動可能に挿入されている。移動体５１の外周とハウジング７の内周との間、および、移動体５１の内周と入力シャフト２の外周との間は、それぞれシール部材５５、５６を介して油密状にシールされる。これにより、移動体５１とハウジング７の上端との間に油室５２が形成されている。また、入力シャフト２の外周に周方向間隔をおいて設けられた複数の軸方向溝と、移動体５１の内周に周方向間隔をおいて設けられた複数の軸方向溝との間にボール５３が挟み込まれることで、移動体５１は入力シャフト２と同行回転する。移動体５１と第１バルブ部材３１との間において圧縮復帰バネ５４が入力シャフト２に嵌め合わされている。   A moving mechanism 50 having a moving body 51 that moves by an amount corresponding to the driving state of the vehicle is provided. The moving body 51 of the present embodiment is connected so as to move in the axial direction with respect to the input / output shafts 2 and 3 and to rotate together with the input shaft 2, and relatively rotates with respect to the output shaft 3, so that the vehicle is in a driving state. In accordance with the magnitude of the hydraulic pressure adjusted by the hydraulic pressure adjustment mechanism 60 that adjusts the magnitude of the hydraulic pressure accordingly. That is, as shown in FIGS. 4 and 5, the moving body 51 has a cylindrical shape, is inserted into the housing 7 so as to be axially movable relative to the control valve 30, and the input shaft 2 is concentrically disposed in the center hole thereof. It is inserted so that it can move in the axial direction. The space between the outer periphery of the moving body 51 and the inner periphery of the housing 7 and the space between the inner periphery of the moving body 51 and the outer periphery of the input shaft 2 are sealed in an oil-tight manner via seal members 55 and 56, respectively. . Thereby, an oil chamber 52 is formed between the moving body 51 and the upper end of the housing 7. Further, a ball is provided between a plurality of axial grooves provided on the outer periphery of the input shaft 2 at circumferential intervals and a plurality of axial grooves provided on the inner periphery of the moving body 51 at circumferential intervals. The moving body 51 rotates together with the input shaft 2 by 53 being sandwiched. A compression return spring 54 is fitted to the input shaft 2 between the moving body 51 and the first valve member 31.

油室５２はポンプ４２に油圧調節機構６０を介して接続される。油圧調節機構６０は、移動体５１に作用させる油圧を車両の運転状態に応じて調節する。図６に示すように、油圧調節機構６０は、ハウジング７に形成された保持孔６１に相対回転しないように挿入された筒状スリーブ６２と、スリーブ６２に自身の軸中心に相対回転可能に挿入されたスプール６３を備えている。スリーブ６２に、制御バルブ３０を介してポンプ４２に通じる圧油導入ポート６２ａと、油室５２に通じる圧油送り出しポート６２ｂが形成されている。スプール６３に、圧油導入ポート６２ａに通じる外周溝６３ａと、圧油送り出しポート６２ｂと重なる位置に配置される通孔６３ｂと、外周溝６３ａと通孔６３ｂを接続する圧油通路６３ｃと、通孔６３ｂを保持孔６１に接続する絞り通路６３ｄが形成される。保持孔６１内はドレン流路６３ｅを介してタンク４３に通じる。図７に示すように、スリーブ６２の圧油送り出しポート６２ｂとスプール６３の通孔６３ｂとの重なり部分（図においてハッチングで示す）は可変絞り６０ａを構成し、可変絞り６０ａの開度はスプール６３の回転量に応じて変化する。スプール６３は減速機構６５を介してモータ６６に接続され、モータ６６の回転量は制御装置６７により制御される。モータ６６として例えばステッピングモータを用いることができる。制御装置６７は、車両の運転状態を検知するセンサからの信号に応じてモータ６６を制御する。本実施形態の制御装置６７は、車両の運転状態として車速を検出するセンサからの車速信号に基づき、車速が高速になる程に可変絞り６０ａの開度が大きくなるようにモータ６６を制御する。すなわち、高速走行時には可変絞り６０ａの開度を大きくすることで移動体５１に作用させる油圧を大きくし、これにより移動体５１は復帰バネ５４の弾力に抗して図中下方への移動量が増加する。車速が低下する程に可変絞り６０ａの開度を小さくすることで移動体５１に作用させる油圧を小さくし、これにより移動体５１は復帰バネ５４の弾力により図中上方への移動量が増加する。   The oil chamber 52 is connected to the pump 42 via a hydraulic adjustment mechanism 60. The hydraulic adjustment mechanism 60 adjusts the hydraulic pressure applied to the moving body 51 according to the driving state of the vehicle. As shown in FIG. 6, the hydraulic adjustment mechanism 60 is inserted into the holding hole 61 formed in the housing 7 so as not to rotate relative to the cylindrical sleeve 62, and inserted into the sleeve 62 so as to be rotatable relative to its own axis. The spool 63 is provided. A pressure oil introduction port 62 a communicating with the pump 42 via the control valve 30 and a pressure oil delivery port 62 b communicating with the oil chamber 52 are formed in the sleeve 62. An outer peripheral groove 63a that communicates with the pressure oil introduction port 62a, a through hole 63b that is disposed at a position overlapping the pressure oil delivery port 62b, a pressure oil passage 63c that connects the outer peripheral groove 63a and the through hole 63b, and a passage through the spool 63. A throttle passage 63d that connects the hole 63b to the holding hole 61 is formed. The inside of the holding hole 61 communicates with the tank 43 through the drain channel 63e. As shown in FIG. 7, the overlapping portion (shown by hatching) of the pressure oil delivery port 62b of the sleeve 62 and the through-hole 63b of the spool 63 forms a variable throttle 60a. It changes according to the amount of rotation. The spool 63 is connected to the motor 66 via the speed reduction mechanism 65, and the rotation amount of the motor 66 is controlled by the control device 67. For example, a stepping motor can be used as the motor 66. The control device 67 controls the motor 66 according to a signal from a sensor that detects the driving state of the vehicle. The control device 67 of the present embodiment controls the motor 66 so that the opening degree of the variable throttle 60a increases as the vehicle speed increases, based on the vehicle speed signal from the sensor that detects the vehicle speed as the driving state of the vehicle. That is, the hydraulic pressure applied to the moving body 51 is increased by increasing the opening degree of the variable throttle 60a during high-speed traveling, so that the moving body 51 moves downward in the figure against the elasticity of the return spring 54. To increase. The hydraulic pressure applied to the moving body 51 is reduced by reducing the opening of the variable throttle 60a as the vehicle speed decreases, whereby the moving amount of the moving body 51 increases upward in the figure due to the elasticity of the return spring 54. .

図１、図４、図５に示すように、入出力シャフト２、３の相対回転を規制する弾力を、その相対回転量に応じて発生する弾性部材７０が設けられている。本実施形態の弾性部材７０は、ハウジング７内において第１バルブ部材３１と移動体５１の間に配置され、入出力シャフト２、３の軸心に平行な軸心を有する円柱形状を有する。弾性部材７０の一端は、第１バルブ部材３１に圧入等により固定される固定端とされ、その固定端は入出力シャフト２、３の軸心から偏心した位置で出力シャフト３と同行回転する。弾性部材７０の他端は固定端から入出力シャフト２、３の軸方向に離れた自由端とされている。なお、移動体５１の一部は弾性部材７０と干渉しないように切欠き部５１ａを有する。   As shown in FIGS. 1, 4, and 5, an elastic member 70 is provided that generates an elastic force that restricts the relative rotation of the input / output shafts 2 and 3 according to the amount of relative rotation. The elastic member 70 of the present embodiment is disposed between the first valve member 31 and the moving body 51 in the housing 7 and has a cylindrical shape having an axis parallel to the axis of the input / output shafts 2 and 3. One end of the elastic member 70 is a fixed end fixed to the first valve member 31 by press fitting or the like, and the fixed end rotates along with the output shaft 3 at a position eccentric from the axis of the input / output shafts 2 and 3. The other end of the elastic member 70 is a free end separated from the fixed end in the axial direction of the input / output shafts 2 and 3. A part of the moving body 51 has a notch 51 a so as not to interfere with the elastic member 70.

移動体５１の移動量に応じて弾性部材７０の発生弾力が変化するように弾性部材７０の剛性を調節する剛性調節機構８０が設けられている。本実施形態の剛性調節機構８０は、入出力シャフト２、３の軸心から偏心した位置で移動体５１と同行回転すると共に軸方向に同行移動する押し付け部８２′を有する。すなわち、移動体５１の下端に取り付けられたリング状プレート８２に設けられる開口８２ａの内周により押し付け部８２′が構成されている。その開口８２ａに弾性部材７０が挿入されることで、押し付け部８２′は入出力シャフト２、３の相対回転により弾性部材７０をその相対回転方向に沿って押し付ける位置に配置されている。押し付け部８２′の押し付けによる弾性部材７０の弾性的な曲げ変形により、入出力シャフト２、３の相対回転を規制する弾力が発生される。そして、運転状態に応じて移動体５１が移動することで入出力シャフト２、３の軸方向における押し付け部８２′による弾性部材７０の押し付け位置が変化する。その押し付け位置の変化に応じて弾性部材７０の曲げ剛性が変化する。すなわち、車速の増加により移動体５１は下方に移動するので、弾性部材７０の固定端から押し付け部８２′による押し付け位置までの距離が短くなり、弾性部材７０の曲げ剛性が大きくなる。車速の低下により移動体５１は上方に移動するので、弾性部材７０の固定端から押し付け部８２′による押し付け位置までの距離が長くなり、弾性部材７０の曲げ剛性が小さくなる。   A rigidity adjusting mechanism 80 is provided that adjusts the rigidity of the elastic member 70 so that the elastic force generated by the elastic member 70 changes according to the amount of movement of the moving body 51. The rigidity adjusting mechanism 80 of the present embodiment includes a pressing portion 82 ′ that rotates together with the moving body 51 at a position deviated from the axis of the input / output shafts 2 and 3 and moves in the axial direction. That is, the pressing portion 82 ′ is configured by the inner periphery of the opening 82 a provided in the ring-shaped plate 82 attached to the lower end of the moving body 51. By inserting the elastic member 70 into the opening 82 a, the pressing portion 82 ′ is disposed at a position where the elastic member 70 is pressed along the relative rotation direction by the relative rotation of the input / output shafts 2 and 3. Due to the elastic bending deformation of the elastic member 70 caused by the pressing of the pressing portion 82 ′, an elastic force that restricts the relative rotation of the input / output shafts 2 and 3 is generated. And the pressing position of the elastic member 70 by the pressing part 82 'in the axial direction of the input / output shafts 2 and 3 is changed by the movement of the moving body 51 according to the operating state. The bending rigidity of the elastic member 70 changes according to the change in the pressing position. That is, since the moving body 51 moves downward as the vehicle speed increases, the distance from the fixed end of the elastic member 70 to the pressing position by the pressing portion 82 ′ is shortened, and the bending rigidity of the elastic member 70 is increased. Since the moving body 51 moves upward due to the decrease in the vehicle speed, the distance from the fixed end of the elastic member 70 to the pressing position by the pressing portion 82 ′ increases, and the bending rigidity of the elastic member 70 decreases.

上記第１実施形態によれば、操舵トルクの作用により入出力シャフト２、３は相対回転し、その入出力シャフト２、３の相対回転はトーションバー６と弾性部材７０の発生弾力により規制される。弾性部材７０の曲げ剛性は、車両の運転状態に応じた量の移動体５１の移動により、押し付け部８２′による弾性部材７０の押し付け位置が変化することで調節される。よって、操舵トルクに応じた入出力シャフト２、３の相対回転量は車両の運転状態に応じて変化し、油圧制御バルブ３０により制御される操舵補助力発生用の油圧が変化する。すなわち、車速の増加により弾性部材７０の曲げ剛性が大きくなるので、入出力シャフト２、３の相対回転量が少なくなり操舵補助力が減少する。車速の減少により弾性部材７０の曲げ剛性が小さくなるので、入出力シャフト２、３の相対回転量が多くなり操舵補助力が増加する。   According to the first embodiment, the input / output shafts 2 and 3 are relatively rotated by the action of the steering torque, and the relative rotation of the input / output shafts 2 and 3 is restricted by the elastic force generated by the torsion bar 6 and the elastic member 70. . The bending rigidity of the elastic member 70 is adjusted by changing the pressing position of the elastic member 70 by the pressing portion 82 ′ by moving the moving body 51 by an amount corresponding to the driving state of the vehicle. Therefore, the relative rotation amounts of the input / output shafts 2 and 3 according to the steering torque change according to the driving state of the vehicle, and the hydraulic pressure for generating the steering assist force controlled by the hydraulic control valve 30 changes. That is, since the flexural rigidity of the elastic member 70 increases as the vehicle speed increases, the relative rotation amount of the input / output shafts 2 and 3 decreases, and the steering assist force decreases. Since the bending rigidity of the elastic member 70 is reduced due to the decrease in the vehicle speed, the relative rotation amount of the input / output shafts 2 and 3 is increased, and the steering assist force is increased.

図８、図９は本発明の第２実施形態を示し、第１実施形態と同様部分は同一符号で示して説明を省略し、相違点を説明する。   8 and 9 show a second embodiment of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof will be omitted. Differences will be described.

第２実施形態における移動機構１５０の移動体１５１は、入出力シャフト２、３に対して軸方向移動すると共に入出力シャフト２、３の軸方向の間隔をおいて相対配置される第１移動体片１５１ａと第２移動体片１５１ｂとを有する。また、第１バルブ部材３１の上部に同軸心に固定される筒部材１４１がハウジング７に相対回転可能に挿入され、これにより筒部材１４１は出力シャフト３と同行回転し、入力シャフト２に対して相対回転する。各移動体片１５１ａ、１５１ｂは円筒形状を有し、制御バルブ３０の上方において筒部材１４１に軸方向相対移動可能に挿入され、その中心孔に入力シャフト２が同心に軸方向相対移動可能に挿入されている。各移動体片１５１ａ、１５１ｂの外周と筒部材１４１の内周との間、および、各移動体片１５１ａ、１５１ｂの内周と入力シャフト２の外周との間は、それぞれ油密状にシールされる。これにより、第１移動体片１５１ａとハウジング７の上端との間に第１油室１５２ａが形成され、第２移動体片１５１ｂと制御バルブ３０との間に第２油室１５２ｂが形成されている。   The moving body 151 of the moving mechanism 150 according to the second embodiment moves in the axial direction with respect to the input / output shafts 2 and 3 and is relatively arranged with an axial interval between the input / output shafts 2 and 3. It has the piece 151a and the 2nd moving body piece 151b. In addition, a cylindrical member 141 that is coaxially fixed to the upper portion of the first valve member 31 is inserted into the housing 7 so as to be relatively rotatable. As a result, the cylindrical member 141 rotates along with the output shaft 3 and moves relative to the input shaft 2. Relative rotation. Each of the movable body pieces 151a and 151b has a cylindrical shape, and is inserted into the cylindrical member 141 so as to be axially movable relative to the control valve 30, and the input shaft 2 is inserted into the center hole thereof so as to be axially relatively movable. Has been. Between the outer periphery of each moving body piece 151a, 151b and the inner periphery of the cylindrical member 141, and between the inner periphery of each moving body piece 151a, 151b and the outer periphery of the input shaft 2, it is sealed in an oil-tight manner, respectively. The As a result, a first oil chamber 152a is formed between the first moving body piece 151a and the upper end of the housing 7, and a second oil chamber 152b is formed between the second moving body piece 151b and the control valve 30. Yes.

第２実施形態における剛性調節機構１８０は、両移動体片１５１ａ、１５１ｂの間において、入力シャフト２にねじ合わされると共に出力シャフト３に同行回転かつ軸方向相対移動可能に連結される変位部材１８１を有する。変位部材１８１の内周と入力シャフト２の外周に形成されたスクリュー溝内を循環するボール１８２を有するボールスクリューを介して変位部材１８１は入力シャフト２にねじ合わされている。変位部材１８１の外周に周方向間隔をおいて設けられた複数の軸方向溝と、筒部材１４１の内周に周方向間隔をおいて設けられた複数の軸方向溝との間にボール１５３が挟み込まれることで、変位部材１８１は出力シャフト３と同行回転する。これにより、入出力シャフト２、３の相対回転により変位部材１８１は入出力シャフト２、３に対して軸方向変位する。   The rigidity adjusting mechanism 180 according to the second embodiment includes a displacement member 181 that is screwed to the input shaft 2 and connected to the output shaft 3 so as to be able to rotate along with the output shaft 3 and move in the axial direction between the movable body pieces 151a and 151b. Have. The displacement member 181 is screwed to the input shaft 2 via a ball screw having a ball 182 that circulates in a screw groove formed on the inner periphery of the displacement member 181 and the outer periphery of the input shaft 2. Balls 153 are provided between a plurality of axial grooves provided on the outer periphery of the displacement member 181 at circumferential intervals and a plurality of axial grooves provided on the inner periphery of the cylindrical member 141 at circumferential intervals. By being sandwiched, the displacement member 181 rotates along with the output shaft 3. Accordingly, the displacement member 181 is displaced in the axial direction with respect to the input / output shafts 2 and 3 by the relative rotation of the input / output shafts 2 and 3.

第２実施形態における弾性部材１７０は、第１移動体片１５１ａと変位部材１８１との間に配置される圧縮コイルバネである第１バネ片１７０ａと、第２移動体片１５１ｂと変位部材１８１との間に配置される圧縮コイルバネである第２バネ片１７０ｂとを有し、各バネ片１７０ａ、１７０ｂは入力シャフト２に嵌め合わされている。これにより、入出力シャフト２、３の相対回転による変位部材１８１の変位により、各バネ片１７０ａ、１７０ｂは入出力シャフト２、３の軸方向に沿って弾性変形する。この弾性変形により入出力シャフト２、３の相対回転を規制する弾力が、入出力シャフト２、３の相対回転量に応じて発生する。   The elastic member 170 according to the second embodiment includes a first spring piece 170a that is a compression coil spring disposed between the first moving body piece 151a and the displacement member 181, and a second moving body piece 151b and the displacement member 181. And a second spring piece 170b which is a compression coil spring disposed between the spring pieces 170a and 170b. Accordingly, the spring pieces 170 a and 170 b are elastically deformed along the axial direction of the input / output shafts 2 and 3 due to the displacement of the displacement member 181 due to the relative rotation of the input / output shafts 2 and 3. Due to this elastic deformation, elasticity that restricts the relative rotation of the input / output shafts 2 and 3 is generated according to the relative rotation amount of the input / output shafts 2 and 3.

第２実施形態においては、油圧調節機構６０の圧油送り出しポート６２ｂは第１油室１５２ａと第２油室１５２ｂとに通じる。高速走行時には両移動体片１５１ａ、１５１ｂに作用する油圧が大きくなり、これにより、両移動体片１５１ａ、１５１ｂは両バネ片１７０ａ、１７０ｂの弾力に抗して互いに近接する方向への移動量が増加する。車速が低下する程に両移動体片１５１ａ、１５１ｂに作用する油圧は小さくなり、これにより両移動体片１５１ａ、１５１ｂは両バネ片１７０ａ、１７０ｂの弾力により互いに離隔する方向への移動量が増加する。すなわち、第１移動体片１５１ａと第２移動体片１５１ｂは、車両の運転状態に応じた量だけ互いに逆方向に移動する。第２実施形態においては第１実施形態の復帰バネ５４は不要である。   In the second embodiment, the pressure oil delivery port 62b of the hydraulic adjustment mechanism 60 communicates with the first oil chamber 152a and the second oil chamber 152b. When traveling at a high speed, the hydraulic pressure acting on both moving body pieces 151a and 151b increases, so that both moving body pieces 151a and 151b move in the direction toward each other against the elasticity of both spring pieces 170a and 170b. To increase. As the vehicle speed decreases, the hydraulic pressure acting on both moving body pieces 151a and 151b decreases, and as a result, the amount of movement of both moving body pieces 151a and 151b in the direction away from each other increases due to the elasticity of both spring pieces 170a and 170b. To do. That is, the first moving body piece 151a and the second moving body piece 151b move in opposite directions by an amount corresponding to the driving state of the vehicle. In the second embodiment, the return spring 54 of the first embodiment is not necessary.

各バネ片１７０ａ、１７０ｂは、入出力シャフト２、３の軸方向に沿った弾性変形量に応じて縦弾性係数が変化する非線形バネとされている。これにより、運転状態に応じて両移動体片１５１ａ、１５１ｂが移動すると、各バネ片１７０ａ、１７０ｂは軸方向に沿って弾性変形するので縦弾性係数が変化する。すなわち、車速の増加により両移動体片１５１ａ、１５１ｂが互いに近接すると、各バネ片１７０ａ、１７０ｂの縦弾性係数は大きくなる。車速の低下により両移動体片１５１ａ、１５１ｂは互いに離隔すると、各バネ片１７０ａ、１７０ｂの縦弾性係数は小さくなる。他は第１実施形態と同様とされている。   Each of the spring pieces 170a and 170b is a non-linear spring whose longitudinal elastic coefficient changes according to the amount of elastic deformation along the axial direction of the input / output shafts 2 and 3. Thereby, when both the moving body pieces 151a and 151b move according to the operating state, the spring pieces 170a and 170b are elastically deformed along the axial direction, so that the longitudinal elastic modulus changes. That is, when the moving body pieces 151a and 151b come close to each other due to an increase in the vehicle speed, the longitudinal elastic modulus of each of the spring pieces 170a and 170b increases. When the moving body pieces 151a and 151b are separated from each other due to a decrease in the vehicle speed, the longitudinal elastic modulus of each of the spring pieces 170a and 170b becomes small. Others are the same as in the first embodiment.

上記第２実施形態によれば、操舵トルクの作用により入出力シャフト２、３は相対回転し、その入出力シャフト２、３の相対回転はトーションバー６と両バネ片１７０ａ、１７０ｂの発生弾力により規制される。両バネ片１７０ａ、１７０ｂの縦弾性係数は、車両の運転状態に応じた量の両移動体片１５１ａ、１５１ｂの移動により、両バネ片１７０ａ、１７０ｂの弾性変形量が変化することで調節される。よって、操舵トルクに応じた入出力シャフト２、３の相対回転量は車両の運転状態に応じて変化し、油圧制御バルブ３０により制御される操舵補助力発生用の油圧が変化する。すなわち、車速の増加により両バネ片１７０ａ、１７０ｂの剛性が大きくなるので、入出力シャフト２、３の相対回転量が少なくなり操舵補助力が減少する。車速の減少により両バネ片１７０ａ、１７０ｂの剛性が小さくなるので、入出力シャフト２、３の相対回転量が多くなり操舵補助力が増加する。   According to the second embodiment, the input / output shafts 2 and 3 are rotated relative to each other by the action of the steering torque, and the relative rotation of the input / output shafts 2 and 3 is caused by the elasticity generated by the torsion bar 6 and the two spring pieces 170a and 170b. Be regulated. The longitudinal elastic modulus of the two spring pieces 170a and 170b is adjusted by changing the amount of elastic deformation of the two spring pieces 170a and 170b by the movement of the two moving body pieces 151a and 151b in an amount corresponding to the driving state of the vehicle. . Therefore, the relative rotation amounts of the input / output shafts 2 and 3 according to the steering torque change according to the driving state of the vehicle, and the hydraulic pressure for generating the steering assist force controlled by the hydraulic control valve 30 changes. That is, since the rigidity of both the spring pieces 170a and 170b increases as the vehicle speed increases, the relative rotation amount of the input / output shafts 2 and 3 decreases, and the steering assist force decreases. Since the rigidity of both spring pieces 170a and 170b is reduced due to the reduction in the vehicle speed, the relative rotation amount of the input / output shafts 2 and 3 is increased, and the steering assist force is increased.

図１０、図１１は本発明の第３実施形態を示し、第１実施形態と同様部分は同一符号で示して説明を省略し、相違点を説明する。   FIGS. 10 and 11 show a third embodiment of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals, the description thereof will be omitted, and different points will be described.

第３実施形態における移動機構２５０の移動体２５１は、入出力シャフト２、３に対して軸方向移動すると共に入力シャフト２に同行回転するように連結され、出力シャフト３に対して相対回転する。すなわち、移動体２５１は 円筒形状を有し、制御バルブ３０の上方においてハウジング７に軸方向相対移動可能に挿入され、その中心孔に入力シャフト２が同心に軸方向相対移動可能に挿入されている。移動体２５１の外周とハウジング７の内周との間、および、移動体２５１の内周と入力シャフト２の外周との間は、シール部材５５、５６によりそれぞれ油密状にシールされる。これにより、移動体２５１とハウジング７の上端との間に油室２５２が形成されている。また、第１実施形態と同様に、入力シャフト２の外周に周方向間隔をおいて設けられた複数の軸方向溝と、移動体２５１の内周に周方向間隔をおいて設けられた複数の軸方向溝との間にボール５３が挟み込まれることで、移動体２５１は入力シャフト２と同行回転する。   The moving body 251 of the moving mechanism 250 in the third embodiment is connected to the input shaft 2 so as to move in the axial direction with respect to the input / output shafts 2 and 3, and rotate relative to the output shaft 3. That is, the movable body 251 has a cylindrical shape, is inserted into the housing 7 so as to be axially movable relative to the control valve 30, and the input shaft 2 is inserted into the center hole thereof so as to be axially relatively movable. . The space between the outer periphery of the moving body 251 and the inner periphery of the housing 7 and the space between the inner periphery of the moving body 251 and the outer periphery of the input shaft 2 are sealed in an oil-tight manner by seal members 55 and 56, respectively. Thereby, an oil chamber 252 is formed between the moving body 251 and the upper end of the housing 7. Further, similarly to the first embodiment, a plurality of axial grooves provided on the outer periphery of the input shaft 2 at circumferential intervals, and a plurality of grooves provided on the inner periphery of the moving body 251 at circumferential intervals. When the ball 53 is sandwiched between the axial grooves, the moving body 251 rotates along with the input shaft 2.

第３実施形態の剛性調節機構２８０は、出力シャフト３と同行回転すると共に、移動体２５１から入力シャフト２の軸方向の間隔をおいて配置される受け部２８１を有する。本実施形態の受け部２８１は第１バルブ部材３１の上端部により構成される。   The rigidity adjusting mechanism 280 according to the third embodiment includes a receiving portion 281 that rotates along with the output shaft 3 and is disposed at a distance from the moving body 251 in the axial direction of the input shaft 2. The receiving portion 281 of this embodiment is configured by the upper end portion of the first valve member 31.

第３実施形態の弾性部材２７０は、移動体２５１に同行回転するように連結される一端部２７０ａと受け部２８１に同行回転するように連結される他端部２７０ｂとを有し、且つ、移動体２５１と受け部２８１との間で圧縮されている。本実施形態の弾性部材２７０は、中心孔が形成された円錐台形状を有し、入出力シャフト２、３の軸方向における圧縮量に応じて捩れ剛性が変化するゴムとされている。弾性部材２７０の一端部２７０ａは移動体２５１の下面に、他端部２７０ｂは受け部２８１に、例えば凹凸嵌合部や接着剤を介して同行回転するように連結される。これにより、入出力シャフト２、３の相対回転による弾性部材２７０の弾性的な捩れ変形により、入出力シャフト２、３の相対回転を規制する弾力が、入出力シャフト２、３の相対回転量に応じて発生する。   The elastic member 270 of the third embodiment has one end 270a connected to the moving body 251 so as to rotate together and the other end 270b connected so as to rotate accompanying the receiving portion 281. It is compressed between the body 251 and the receiving part 281. The elastic member 270 of this embodiment has a truncated cone shape with a central hole, and is a rubber whose torsional rigidity changes according to the amount of compression in the axial direction of the input / output shafts 2 and 3. One end portion 270a of the elastic member 270 is connected to the lower surface of the moving body 251, and the other end portion 270b is connected to the receiving portion 281 so as to rotate together with, for example, an uneven fitting portion or an adhesive. As a result, the elastic force that restricts the relative rotation of the input / output shafts 2 and 3 due to the elastic torsional deformation of the elastic member 270 due to the relative rotation of the input / output shafts 2 and 3 causes the relative rotation amount of the input / output shafts 2 and 3 In response.

油圧調節機構６０の圧油送り出しポート６２ｂは油室２５２に通じる。高速走行時には移動体２５１に作用する油圧が大きくなる。これにより移動体２５１は弾性部材２７０の弾力に抗して図中下方への移動量が増加する。車速が低下する程に移動体２５１に作用する油圧が小さくなる。これにより移動体２５１は弾性部材２７０の弾力により図中上方への移動量が増加する。第３実施形態においては第１実施形態の復帰バネ５４は不要である。   A pressure oil delivery port 62 b of the hydraulic adjustment mechanism 60 leads to the oil chamber 252. When traveling at high speed, the hydraulic pressure acting on the moving body 251 increases. Thereby, the moving body 251 increases the amount of movement downward in the figure against the elasticity of the elastic member 270. The hydraulic pressure acting on the moving body 251 decreases as the vehicle speed decreases. As a result, the moving amount of the moving body 251 increases upward in the figure due to the elasticity of the elastic member 270. In the third embodiment, the return spring 54 of the first embodiment is not necessary.

運転状態に応じて移動体２５１が移動すると、移動体２５１と受け部２８１との間での入出力シャフト２、３の軸方向における弾性部材２７０の圧縮量が変化し、その変化に応じて弾性部材２７０の捩れ剛性が変化する。すなわち、車速の増加により移動体２５１は下方に移動するので、弾性部材２７０は圧縮量が増加して捩れ剛性が大きくなる。車速の低下により移動体２５１は上方に移動するので、弾性部材２７０は圧縮量が減少して捩れ剛性が小さくなる。他は第１実施形態と同様とされている。   When the moving body 251 moves according to the operating state, the amount of compression of the elastic member 270 in the axial direction of the input / output shafts 2 and 3 between the moving body 251 and the receiving portion 281 changes, and the elasticity changes according to the change. The torsional rigidity of the member 270 changes. That is, since the moving body 251 moves downward as the vehicle speed increases, the compression amount of the elastic member 270 increases and the torsional rigidity increases. Since the moving body 251 moves upward due to the decrease in the vehicle speed, the elastic member 270 has a reduced compression amount and a reduced torsional rigidity. Others are the same as in the first embodiment.

なお、弾性部材２７０を入力シャフト２に嵌め合わされる捩れコイルバネであって、入出力シャフト２、３の軸方向における圧縮量の変化に応じて捩れ剛性が変化するものにより構成してもよい。   The elastic member 270 may be a torsion coil spring that is fitted to the input shaft 2 and has a torsional rigidity that changes in accordance with a change in the compression amount in the axial direction of the input / output shafts 2 and 3.

上記第３実施形態によれば、操舵トルクの作用により入出力シャフト２、３は相対回転し、その入出力シャフト２、３の相対回転はトーションバー６と弾性部材２７０の発生弾力により規制される。弾性部材２７０の捩れ剛性は、車両の運転状態に応じた量の移動体２５１の移動により、弾性部材２７０の圧縮量が変化することで調節される。よって、操舵トルクに応じた入出力シャフト２、３の相対回転量は車両の運転状態に応じて変化し、油圧制御バルブ３０により制御される操舵補助力発生用の油圧が変化する。すなわち、車速の増加により弾性部材２７０の捩れ剛性が大きくなるので、入出力シャフト２、３の相対回転量が少なくなり操舵補助力が減少する。車速の減少により弾性部材２７０の捩れ剛性が小さくなるので、入出力シャフト２、３の相対回転量が多くなり操舵補助力が増加する。しかも、入出力シャフト２、３の相対回転を直接に弾性部材２７０の捩れ変形に変換できるので、構造を簡単化できる。   According to the third embodiment, the input / output shafts 2 and 3 are relatively rotated by the action of the steering torque, and the relative rotation of the input / output shafts 2 and 3 is restricted by the elastic force generated by the torsion bar 6 and the elastic member 270. . The torsional rigidity of the elastic member 270 is adjusted by changing the amount of compression of the elastic member 270 by the movement of the moving body 251 according to the driving state of the vehicle. Therefore, the relative rotation amounts of the input / output shafts 2 and 3 according to the steering torque change according to the driving state of the vehicle, and the hydraulic pressure for generating the steering assist force controlled by the hydraulic control valve 30 changes. That is, since the torsional rigidity of the elastic member 270 increases as the vehicle speed increases, the relative rotation amount of the input / output shafts 2 and 3 decreases, and the steering assist force decreases. As the vehicle speed decreases, the torsional rigidity of the elastic member 270 decreases, so that the relative rotation amount of the input / output shafts 2 and 3 increases and the steering assist force increases. In addition, since the relative rotation of the input / output shafts 2 and 3 can be directly converted into the torsional deformation of the elastic member 270, the structure can be simplified.

図１２は本発明の第４実施形態を示し、第３実施形態と同様部分は同一符号で示して説明を省略し、相違点を説明する。
第４実施形態においては、入出力シャフト２、３の径方向における弾性部材２７０の変形を阻止する阻止部３９０が設けられている。本実施形態の阻止部３９０は、弾性部材２７０の外周上部を囲むもので横断面円環形状を有し、その外周面は円柱面に沿い、その内周面は弾性部材２７０の外周円錐面に沿い、その上端は移動体２５１の下端面に一体化されている。これにより、弾性部材２７０の軸方向圧縮量の変化に応じた捩れ剛性の変化が径方向変形により抑制されるのを防止でき、弾性部材２７０の材料選択範囲を拡げて設計の自由度を増し、また、高速直進走行時における剛性を大きくして走行安定性を向上できる。他は第３実施形態と同様とされている。 FIG. 12 shows a fourth embodiment of the present invention. The same parts as those of the third embodiment are denoted by the same reference numerals, and the description thereof will be omitted. Differences will be described.
In the fourth embodiment, a blocking portion 390 that prevents deformation of the elastic member 270 in the radial direction of the input / output shafts 2 and 3 is provided. The blocking portion 390 of the present embodiment surrounds the upper outer periphery of the elastic member 270 and has an annular shape in cross section. The outer peripheral surface is along a cylindrical surface, and the inner peripheral surface is an outer peripheral conical surface of the elastic member 270. The upper end is integrated with the lower end surface of the moving body 251. As a result, it is possible to prevent a change in torsional rigidity according to a change in the axial compression amount of the elastic member 270 from being suppressed by radial deformation, and to expand the material selection range of the elastic member 270 to increase the degree of design freedom, In addition, the running stability can be improved by increasing the rigidity during high-speed straight running. Others are the same as in the third embodiment.

図１３、図１４は本発明の第５実施形態を示し、第３実施形態と同様部分は同一符号で示して説明を省略し、相違点を説明する。
第５実施形態においては、入出力シャフト２、３の径方向における弾性部材２７０の変形を阻止する阻止部４９０が設けられている。本実施形態の阻止部４９０は、弾性部材２７０の外周上部を囲むように配置された複数（図示例では４つ）の阻止片４９０ａにより構成され、各阻止片４９０ａは弾性部材２７０の周方向における間隔をおいて配置され、その配置状態において外周面は円柱面に沿い、内周面は弾性部材２７０の外周円錐面に沿う。また、各阻止片４９０ａの外周に周溝４９０ａ′が形成され、それら周溝４９０ａ′にバンド４９１が嵌め合わされることで組み立て時に各阻止片４９０ａが分散するのが防止される。また、移動体２５１の外周とハウジング７の内周との間のシールに代えて、阻止部４９０の外周とハウジング７の内周との間がシール部材５５により油密状にシールされている。これにより、油室２５２の圧油が移動体２５１の外周とハウジング７の内周との間の隙間を通り、各阻止片４９０ａの外周とハウジング７の内周との間に至る。よって、油圧により各阻止片４９０ａにより弾性部材２７０を径方向に沿い押し付け、入出力シャフト２、３の径方向における弾性部材２７０の変形を効果的に阻止することができる。他は第４実施形態と同様とされている。 FIGS. 13 and 14 show a fifth embodiment of the present invention. The same parts as those of the third embodiment are denoted by the same reference numerals, description thereof is omitted, and differences will be described.
In the fifth embodiment, a blocking portion 490 that prevents deformation of the elastic member 270 in the radial direction of the input / output shafts 2 and 3 is provided. The blocking portion 490 of the present embodiment is configured by a plurality (four in the illustrated example) of blocking pieces 490a arranged so as to surround the upper outer periphery of the elastic member 270, and each blocking piece 490a is in the circumferential direction of the elastic member 270. In the arrangement state, the outer peripheral surface is along the cylindrical surface, and the inner peripheral surface is along the outer peripheral conical surface of the elastic member 270. In addition, circumferential grooves 490a ′ are formed on the outer periphery of each blocking piece 490a, and the band 491 is fitted into these circumferential grooves 490a ′, thereby preventing the blocking pieces 490a from being dispersed during assembly. Further, instead of the seal between the outer periphery of the moving body 251 and the inner periphery of the housing 7, the outer periphery of the blocking portion 490 and the inner periphery of the housing 7 are sealed in an oil-tight manner by the seal member 55. As a result, the pressure oil in the oil chamber 252 passes through the gap between the outer periphery of the movable body 251 and the inner periphery of the housing 7, and reaches between the outer periphery of each blocking piece 490 a and the inner periphery of the housing 7. Therefore, the elastic member 270 can be pressed along the radial direction by the blocking pieces 490a by hydraulic pressure, and deformation of the elastic member 270 in the radial direction of the input / output shafts 2 and 3 can be effectively blocked. Others are the same as in the fourth embodiment.

本発明は上記実施形態に限定されない。例えば、入力シャフトと出力シャフトをトーションバーを用いることなく弾性部材のみを介して連結してもよい。車両の運転状態は車速に限定されず、例えば舵角に応じて油圧調節機構により油圧を調節するようにしてもよい。また、油圧調節機構を用いることなく、車両の運転状態に応じて移動する電動アクチュエータにより移動部材を移動させるようにしてもよい。第１実施形態において、移動体が出力シャフトと同行回転するようにし、弾性部材が入力シャフトと同行回転するようにしてもよい。第２実施形態において変位部材は出力シャフトにねじ合わされ、入力シャフトに同行回転すると共に軸方向相対移動するように連結されてもよい。第３〜第５実施形態において、移動体が出力シャフトと同行回転するようにし、受け部が入力シャフトと同行回転するようにしてもよい。本発明はラックピニオン式以外の油圧パワーステアリング装置にも適用でき、例えば出力シャフトがボールスクリューシャフトに一体化されている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, the input shaft and the output shaft may be connected via only an elastic member without using a torsion bar. The driving state of the vehicle is not limited to the vehicle speed. For example, the hydraulic pressure may be adjusted by a hydraulic pressure adjustment mechanism in accordance with the steering angle. Further, the moving member may be moved by an electric actuator that moves according to the driving state of the vehicle without using the hydraulic pressure adjusting mechanism. In the first embodiment, the moving body may rotate along with the output shaft, and the elastic member may rotate along with the input shaft. In the second embodiment, the displacement member may be screwed onto the output shaft and connected to the input shaft so as to rotate along with the input shaft and move relative to the axial direction. In the third to fifth embodiments, the moving body may rotate along with the output shaft, and the receiving portion may rotate along with the input shaft. The present invention can be applied to hydraulic power steering devices other than the rack and pinion type. For example, the present invention may be applied to a ball screw type hydraulic power steering device in which an output shaft is integrated with a ball screw shaft.

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縦断面図1 is a longitudinal sectional view of a hydraulic power steering apparatus according to a first embodiment of the present invention. 本発明の第１実施形態の油圧パワーステアリング装置における制御バルブの横断面図1 is a cross-sectional view of a control valve in a hydraulic power steering apparatus according to a first embodiment of the present invention. 本発明の第１実施形態の油圧パワーステアリング装置における油圧回路Hydraulic circuit in hydraulic power steering apparatus of first embodiment of the present invention 本発明の第１実施形態の油圧パワーステアリング装置における要部の縦断面図The longitudinal cross-sectional view of the principal part in the hydraulic power steering device of 1st Embodiment of this invention 図４のＶ−Ｖ線断面図VV line sectional view of FIG. 本発明の実施形態の油圧パワーステアリング装置における油圧調節機構の断面図Sectional drawing of the hydraulic adjustment mechanism in the hydraulic power steering apparatus of embodiment of this invention 本発明の実施形態の油圧パワーステアリング装置における油圧調節機構の作用説明図Action explanatory drawing of the hydraulic adjustment mechanism in the hydraulic power steering device of the embodiment of the present invention 本発明の第２実施形態の油圧パワーステアリング装置における要部の縦断面図The longitudinal section of the important section in the hydraulic power steering device of a 2nd embodiment of the present invention. 図８のＩＸ−ＩＸ線断面図IX-IX sectional view of FIG. 本発明の第３実施形態の油圧パワーステアリング装置における要部の縦断面図The longitudinal cross-sectional view of the principal part in the hydraulic power steering device of 3rd Embodiment of this invention 図１０のＸＩ−ＸＩ線断面図XI-XI line sectional view of FIG. 本発明の第４実施形態の油圧パワーステアリング装置における要部の縦断面図The longitudinal cross-sectional view of the principal part in the hydraulic power steering device of 4th Embodiment of this invention 本発明の第５実施形態の油圧パワーステアリング装置における要部の縦断面図The longitudinal section of the important section in the hydraulic power steering device of a 5th embodiment of the present invention. 図１３のＸＩＶ−ＸＩＶ線断面図XIV-XIV line sectional view of FIG.

符号の説明Explanation of symbols

２ 入力シャフト
３ 出力シャフト
２０ 油圧シリンダ（油圧アクチュエータ）
３０ 油圧制御バルブ
５０、１５０、２５０ 移動機構
５１、１５１、２５１ 移動体
７０、１７０、２７０ 弾性部材
８０、１８０、２８０ 剛性調節機構
８２′ 押し付け部
１５１ａ 第１移動体片
１５１ｂ 第２移動体片
１７０ａ 第１バネ片
１７０ｂ 第２バネ片
１８１ 変位部材
２７０ａ 一端部
２７０ｂ 他端部
２８１ 受け部
３９０ 阻止部 2 Input shaft 3 Output shaft 20 Hydraulic cylinder (hydraulic actuator)
30 Hydraulic control valve 50, 150, 250 Moving mechanism 51, 151, 251 Moving body 70, 170, 270 Elastic member 80, 180, 280 Rigidity adjusting mechanism 82 'Pressing portion 151a First moving body piece 151b Second moving body piece 170a First spring piece 170b Second spring piece 181 Displacement member 270a One end 270b Other end 281 Receiving portion 390 Blocking portion

Claims (5)

入力シャフトと、
前記入力シャフトに操舵トルクに応じて弾性的に相対回転可能に連結される出力シャフトと、
操舵補助力発生用油圧アクチュエータと、
前記油圧アクチュエータに供給される圧油の油圧を、前記入出力シャフトの相対回転量に応じて制御する油圧制御バルブと、
車両の運転状態に応じた量だけ移動する移動体を有する移動機構と、
前記入出力シャフトの相対回転を規制する弾力を、その相対回転量に応じて発生する弾性部材と、
前記移動体の移動量に応じて前記弾力が変化するように前記弾性部材の剛性を調節する剛性調節機構とを備える油圧パワーステアリング装置。 An input shaft;
An output shaft coupled to the input shaft in an elastically rotatable manner according to a steering torque;
A hydraulic actuator for generating steering assist force;
A hydraulic control valve for controlling the hydraulic pressure of the pressure oil supplied to the hydraulic actuator according to the relative rotation amount of the input / output shaft;
A moving mechanism having a moving body that moves by an amount according to the driving state of the vehicle;
An elastic member that generates an elastic force that restricts relative rotation of the input / output shaft according to the amount of relative rotation;
A hydraulic power steering apparatus comprising: a stiffness adjusting mechanism that adjusts the stiffness of the elastic member so that the elasticity changes according to the amount of movement of the movable body. 前記移動体は、前記入出力シャフトに対して軸方向移動すると共に前記入出力シャフトの中の一方に同行回転するように連結され、
前記弾性部材は、前記入出力シャフトの軸心から偏心した位置で前記入出力シャフトの中の他方と同行回転する固定端と、固定端から入出力シャフトの軸方向に離れた自由端を有し、
前記剛性調節機構は、前記移動体と同行回転すると共に軸方向に同行移動する押し付け部を有し、
前記押し付け部は、前記入出力シャフトの相対回転により前記弾性部材を押し付ける位置に配置され、
前記押し付け部の押し付けによる前記弾性部材の弾性的な曲げ変形により前記弾力が発生され、
前記入出力シャフトの軸方向における前記押し付け部による押し付け位置の変化に応じて、前記弾性部材の曲げ剛性が変化する請求項１に記載の油圧パワーステアリング装置。 The moving body is connected so as to move in the axial direction with respect to the input / output shaft and rotate along with one of the input / output shafts,
The elastic member has a fixed end that rotates together with the other of the input / output shafts at a position eccentric from the axis of the input / output shaft, and a free end separated from the fixed end in the axial direction of the input / output shaft. ,
The rigidity adjusting mechanism has a pressing portion that rotates along with the moving body and moves along the axial direction.
The pressing portion is disposed at a position where the elastic member is pressed by relative rotation of the input / output shaft.
The elasticity is generated by elastic bending deformation of the elastic member by pressing of the pressing portion,
2. The hydraulic power steering apparatus according to claim 1, wherein a bending rigidity of the elastic member changes according to a change in a pressing position by the pressing portion in an axial direction of the input / output shaft. 前記移動体は、前記入出力シャフトに対して軸方向移動すると共に前記入出力シャフトの軸方向の間隔をおいて相対配置される第１移動体片と第２移動体片とを有し、
前記第１移動体片と前記第２移動体片は、車両の運転状態に応じた量だけ互いに逆方向に移動し、
前記剛性調節機構は、前記両移動体片の間において、前記入力シャフトと前記出力シャフトの中の一方にねじ合わされると共に、他方に同行回転かつ軸方向相対移動可能に連結される変位部材を有し、
前記弾性部材は、前記第１移動体片と前記変位部材との間に配置される第１バネ片と、前記第２移動体片と前記変位部材との間に配置される第２バネ片とを有し、
前記変位部材は、前記入出力シャフトの相対回転により前記入出力シャフトに対して軸方向変位され、
前記変位部材の変位による前記各バネ片の前記入出力シャフトの軸方向に沿った弾性変形により前記弾力が発生され、
前記各バネ片は、前記入出力シャフトの軸方向に沿った弾性変形量に応じて縦弾性係数が変化する非線形バネとされている請求項１に記載の油圧パワーステアリング装置。 The moving body has a first moving body piece and a second moving body piece that move in the axial direction with respect to the input / output shaft and are relatively disposed with an interval in the axial direction of the input / output shaft.
The first moving body piece and the second moving body piece move in opposite directions by an amount corresponding to the driving state of the vehicle,
The rigidity adjusting mechanism includes a displacement member that is screwed to one of the input shaft and the output shaft between the two moving body pieces, and is connected to the other so as to be able to rotate together and move in the axial direction. And
The elastic member includes a first spring piece disposed between the first moving body piece and the displacement member, and a second spring piece disposed between the second moving body piece and the displacement member. Have
The displacement member is axially displaced with respect to the input / output shaft by relative rotation of the input / output shaft,
The elasticity is generated by elastic deformation along the axial direction of the input / output shaft of each spring piece due to the displacement of the displacement member,
2. The hydraulic power steering apparatus according to claim 1, wherein each of the spring pieces is a non-linear spring whose longitudinal elastic coefficient changes in accordance with an elastic deformation amount along an axial direction of the input / output shaft. 前記移動体は、前記入出力シャフトに対して軸方向移動すると共に前記入出力シャフトの中の一方に同行回転するように連結され、
前記剛性調節機構は、前記入出力シャフトの中の他方と同行回転すると共に、前記移動体から前記入出力シャフトの軸方向の間隔をおいて配置される受け部を有し、
前記弾性部材は、前記移動体に同行回転するように連結される一端部と前記受け部に同行回転するように連結される他端部とを有し、且つ、前記移動体と前記受け部との間で圧縮され、
前記入出力シャフトの相対回転による前記弾性部材の弾性的な捩れ変形により前記弾力が発生され、
前記移動体と前記受け部との間での前記入出力シャフトの軸方向における圧縮量の変化に応じて、前記弾性部材の捩れ剛性が変化する請求項１に記載の油圧パワーステアリング装置。 The moving body is connected so as to move in the axial direction with respect to the input / output shaft and rotate along with one of the input / output shafts,
The rigidity adjusting mechanism has a receiving portion that rotates along with the other of the input / output shafts and is disposed at an interval in the axial direction of the input / output shaft from the moving body,
The elastic member has one end connected to the moving body to rotate along with the moving body and the other end connected to rotate along with the receiving section, and the moving body and the receiving section Compressed between
The elasticity is generated by elastic torsional deformation of the elastic member due to relative rotation of the input / output shaft,
2. The hydraulic power steering apparatus according to claim 1, wherein the torsional rigidity of the elastic member changes in accordance with a change in compression amount in the axial direction of the input / output shaft between the moving body and the receiving portion. 前記入出力シャフトの径方向における前記弾性部材の変形を阻止する阻止部を備える請求項４に記載の油圧パワーステアリング装置。 The hydraulic power steering device according to claim 4, further comprising a blocking portion that blocks deformation of the elastic member in a radial direction of the input / output shaft.
JP2004266366A 2004-02-06 2004-09-14 Hydraulic power steering device Pending JP2005247290A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007314107A (en) * 2006-05-29 2007-12-06 Kayaba Ind Co Ltd Fluid pressure power steering system

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5929568A (en) * 1982-08-13 1984-02-16 Kayaba Ind Co Ltd Hydraulic reaction force device for power steering
JPS6053464A (en) * 1983-09-05 1985-03-27 Toyota Motor Corp Power steering device
JPH07117694A (en) * 1993-10-26 1995-05-09 Honda Motor Co Ltd Power steering device
JPH07165090A (en) * 1993-12-13 1995-06-27 Honda Motor Co Ltd Variable spring rate mechanism
JPH0995242A (en) * 1995-09-29 1997-04-08 Suzuki Motor Corp Rigidity changing device for steering system
JPH1016805A (en) * 1996-07-05 1998-01-20 Toyota Motor Corp Power steering device

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5929568A (en) * 1982-08-13 1984-02-16 Kayaba Ind Co Ltd Hydraulic reaction force device for power steering
JPS6053464A (en) * 1983-09-05 1985-03-27 Toyota Motor Corp Power steering device
JPH07117694A (en) * 1993-10-26 1995-05-09 Honda Motor Co Ltd Power steering device
JPH07165090A (en) * 1993-12-13 1995-06-27 Honda Motor Co Ltd Variable spring rate mechanism
JPH0995242A (en) * 1995-09-29 1997-04-08 Suzuki Motor Corp Rigidity changing device for steering system
JPH1016805A (en) * 1996-07-05 1998-01-20 Toyota Motor Corp Power steering device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007314107A (en) * 2006-05-29 2007-12-06 Kayaba Ind Co Ltd Fluid pressure power steering system

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