JP6879242B2 - Valve device - Google Patents

Valve device Download PDF

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Publication number
JP6879242B2
JP6879242B2 JP2018054664A JP2018054664A JP6879242B2 JP 6879242 B2 JP6879242 B2 JP 6879242B2 JP 2018054664 A JP2018054664 A JP 2018054664A JP 2018054664 A JP2018054664 A JP 2018054664A JP 6879242 B2 JP6879242 B2 JP 6879242B2
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valve
circumferential direction
valve body
annular groove
groove portion
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JP2019167997A (en
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哲朗 満谷
哲朗 満谷
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Denso Corp
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Denso Corp
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Priority to JP2018054664A priority Critical patent/JP6879242B2/en
Priority to PCT/JP2019/011205 priority patent/WO2019181863A1/en
Priority to DE112019001462.5T priority patent/DE112019001462T5/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/14—Check valves with flexible valve members
    • F16K15/144—Check valves with flexible valve members the closure elements being fixed along all or a part of their periphery
    • F16K15/145—Check valves with flexible valve members the closure elements being fixed along all or a part of their periphery the closure elements being shaped as a solids of revolution, e.g. cylindrical or conical
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/18—Check valves with actuating mechanism; Combined check valves and actuated valves
    • F16K15/182—Check valves with actuating mechanism; Combined check valves and actuated valves with actuating mechanism
    • F16K15/1825—Check valves with actuating mechanism; Combined check valves and actuated valves with actuating mechanism for check valves with flexible valve members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/04—Construction of housing; Use of materials therefor of sliding valves
    • F16K27/041—Construction of housing; Use of materials therefor of sliding valves cylindrical slide valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0476—Camshaft bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/3443—Solenoid driven oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
    • F01L2001/3444—Oil filters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34469—Lock movement parallel to camshaft axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34479—Sealing of phaser devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/04—Camshaft drives characterised by their transmission means the camshaft being driven by belts

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Valve Device For Special Equipments (AREA)
  • Check Valves (AREA)

Description

本発明は、弁装置に関する。 The present invention relates to a valve device.

従来、流体の流れを制御可能な弁装置が知られている。例えば特許文献１には、油圧アクチュエータに供給する作動流体を制御する弁装置が開示されている。特許文献１の弁装置は、筒部材およびチェック弁を備えている。筒部材は、内周壁から径方向外側へ凹みつつ周方向に延びて環状に形成された環状溝部、および、環状溝部の底面と外壁とを連通する流入穴を有している。 Conventionally, a valve device capable of controlling the flow of a fluid is known. For example, Patent Document 1 discloses a valve device that controls a working fluid supplied to a hydraulic actuator. The valve device of Patent Document 1 includes a tubular member and a check valve. The tubular member has an annular groove portion formed in an annular shape extending in the circumferential direction while denting radially outward from the inner peripheral wall, and an inflow hole communicating the bottom surface of the annular groove portion with the outer wall.

特許第６００５９５９号公報Japanese Patent No. 6005959

特許文献１の弁装置では、流入穴は、環状溝部の周方向に等間隔で複数形成されている。チェック弁は、単一の板材を長手方向が周方向に沿うよう巻くことにより筒状に形成された弁本体を有し、弁本体の周方向が環状溝部の底面の周方向に沿うよう環状溝部に設けられ、流入穴を経由して筒部材の内側へ向かう流体の流れを許容し、筒部材の内側から流入穴へ向かう流体の流れを規制可能である。なお、チェック弁は、流入穴を経由して筒部材の内側へ向かう流体の流れにより径が縮小し開弁する。また、弁本体の周方向の両端部のそれぞれには周方向に延びる長穴が形成されており、互いに重なった２つの長穴を通るよう環状溝部の底面から突出するピンが設けられている。ここで、ピンは、長穴を係止することにより、弁本体の外径が筒部材の内周壁の内径より小さくならないよう規制している。また、チェック弁は、弁本体の軸方向の長さである幅が他の部位の幅より大きい幅広部を有している。幅広部は、弁本体の周方向に略等間隔で複数形成されている。 In the valve device of Patent Document 1, a plurality of inflow holes are formed at equal intervals in the circumferential direction of the annular groove portion. The check valve has a valve body formed in a tubular shape by winding a single plate material so that the longitudinal direction is along the circumferential direction, and the annular groove portion is formed so that the circumferential direction of the valve body is along the circumferential direction of the bottom surface of the annular groove portion. It is possible to allow the flow of fluid toward the inside of the tubular member via the inflow hole and regulate the flow of fluid from the inside of the tubular member toward the inflow hole. The check valve opens with a reduced diameter due to the flow of fluid toward the inside of the tubular member via the inflow hole. Further, elongated holes extending in the circumferential direction are formed at both ends of the valve body in the circumferential direction, and pins protruding from the bottom surface of the annular groove portion are provided so as to pass through two elongated holes overlapping each other. Here, the pin regulates the outer diameter of the valve body so as not to be smaller than the inner diameter of the inner peripheral wall of the tubular member by locking the elongated hole. Further, the check valve has a wide portion in which the width, which is the axial length of the valve body, is larger than the width of other portions. A plurality of wide portions are formed at substantially equal intervals in the circumferential direction of the valve body.

特許文献１の弁装置では、チェック弁は、径が縮小する開弁時、環状溝部の内側において振れ回り振動するおそれがある。このとき、チェック弁が、環状溝部の周方向の特定の箇所において径方向外側へ寄った場合、一部の幅広部が環状溝部から径方向内側すなわち内周壁側へ飛び出るおそれがある。この状態で、チェック弁が拡径するよう閉弁すると、幅広部が筒部材の内周壁と環状溝部との角部に衝突し、弁本体または筒部材の内周壁が損傷するおそれがある。特に、弁装置が、高速で回転する回転体に設けられて使用される場合、チェック弁の振れ回りが発生し易く、上記問題が顕著になるおそれがある。 In the valve device of Patent Document 1, the check valve may swing around and vibrate inside the annular groove portion when the valve is opened when the diameter is reduced. At this time, if the check valve is moved outward in the radial direction at a specific portion in the circumferential direction of the annular groove portion, a part of the wide portion may protrude inward in the radial direction, that is, toward the inner peripheral wall side from the annular groove portion. If the check valve is closed so as to expand its diameter in this state, the wide portion may collide with the corner portion between the inner peripheral wall of the tubular member and the annular groove portion, and the valve body or the inner peripheral wall of the tubular member may be damaged. In particular, when the valve device is provided on a rotating body that rotates at high speed and is used, the check valve tends to swing around, and the above problem may become remarkable.

本発明の目的は、チェック弁と筒部材の内周壁との衝突による損傷を抑制可能な弁装置を提供することにある。 An object of the present invention is to provide a valve device capable of suppressing damage due to a collision between a check valve and an inner peripheral wall of a tubular member.

本発明に係る弁装置（１１）は、筒部材（５０）とチェック弁（７１、７２）と回転規制部（９０）とを備えている。筒部材は、内周壁（５４）から径方向外側へ凹みつつ周方向に延びて環状に形成された環状溝部（５５、５１１、５１２）、および、環状溝部の周方向に不等間隔で複数形成され環状溝部の底面（５５０）と外壁（５３、５３１、５３２）とを連通する流入穴（ＯＲｓ、ＯＡｓ）を有している。チェック弁は、単一の板材を長手方向が周方向に沿うよう巻くことにより筒状に形成された弁本体（７００）を有し、弁本体の周方向が環状溝部の底面の周方向に沿うよう環状溝部に設けられ、流入穴を経由して筒部材の内側へ向かう流体の流れを許容し、筒部材の内側から流入穴へ向かう流体の流れを規制可能である。回転規制部は、環状溝部の周方向における弁本体の回転位置を所定範囲内に規制可能である。 The valve device (11) according to the present invention includes a tubular member (50), check valves (71, 72), and a rotation control unit (90). A plurality of tubular members are formed in an annular groove portion (55, 511, 512) formed in an annular direction while denting radially outward from the inner peripheral wall (54) and at irregular intervals in the circumferential direction of the annular groove portion. It has inflow holes (ORs, OAs) that communicate the bottom surface (550) of the annular groove portion and the outer wall (53, 531, 532). The check valve has a valve body (700) formed in a tubular shape by winding a single plate material so that the longitudinal direction is along the circumferential direction, and the circumferential direction of the valve body is along the circumferential direction of the bottom surface of the annular groove portion. It is provided in the annular groove portion so as to allow the flow of fluid toward the inside of the tubular member via the inflow hole, and can regulate the flow of fluid from the inside of the tubular member toward the inflow hole. The rotation regulating unit can regulate the rotation position of the valve body in the circumferential direction of the annular groove portion within a predetermined range.

チェック弁は、弁本体の周方向の一部に形成された幅狭部（７１０）、および、弁本体の周方向の幅狭部以外の部位に形成され弁本体の軸方向の長さである幅が幅狭部の幅より大きい幅広部（７２１、７２２）を有している。幅広部の少なくとも一部は、環状溝部の周方向において隣り合う流入穴間の距離のうち最大距離となる区間である最大距離区間（Ｓｂｄ）内に位置する。 The check valve is formed in a portion other than the narrow portion (710) formed in a part of the valve body in the circumferential direction and the narrow portion in the circumferential direction of the valve body, and is the axial length of the valve body. It has a wide portion (721, 722) whose width is larger than the width of the narrow portion . At least a portion of the width wide portion, it located a maximum distance interval (Sbd) within a period of maximum distance among distances between the inflow holes adjacent in the circumferential direction of the annular groove.

流体が流入穴を経由して筒部材の内側へ向かうとき、チェック弁は、外周壁が流体により押され、縮径しつつ開弁する。ここで、流入穴は環状溝部の周方向に不等間隔で複数形成され、幅広部の少なくとも一部は最大距離区間内に位置するため、チェック弁が開弁すると、幅広部は、最大距離区間において少なくとも一部が環状溝部の底面に押し付けられる。これにより、環状溝部の内側におけるチェック弁の振れ回りを抑制するとともに、幅広部が環状溝部から径方向内側すなわち内周壁側へ飛び出るのを抑制できる。そのため、チェック弁の閉弁時に幅広部が筒部材の内周壁と環状溝部との角部に衝突するのを抑制できる。したがって、チェック弁と筒部材の内周壁との衝突による損傷を抑制できる。 When the fluid goes to the inside of the tubular member through the inflow hole, the outer peripheral wall of the check valve is pushed by the fluid and the check valve opens while reducing the diameter. Here, the inflow hole is formed in plurality at unequal intervals in the circumferential direction of the annular groove, at least in part, because that you located a maximum distance in the interval of width wide portion, the check valve is opened, the wide portion, At least part of it is pressed against the bottom surface of the annular groove in the maximum distance section. As a result, it is possible to suppress the runout of the check valve inside the annular groove portion and to prevent the wide portion from jumping out from the annular groove portion to the inner side in the radial direction, that is, to the inner peripheral wall side. Therefore, it is possible to prevent the wide portion from colliding with the corner portion between the inner peripheral wall of the tubular member and the annular groove portion when the check valve is closed. Therefore, damage due to collision between the check valve and the inner peripheral wall of the tubular member can be suppressed.

第１実施形態による弁装置を適用したバルブタイミング調整装置を示す断面図。FIG. 5 is a cross-sectional view showing a valve timing adjusting device to which the valve device according to the first embodiment is applied. 図１のＩＩ−ＩＩ線断面図。FIG. 1 is a sectional view taken along line II-II of FIG. 第１実施形態による弁装置を示す断面図。The cross-sectional view which shows the valve device by 1st Embodiment. 図３のＩＶ−ＩＶ線断面図。FIG. 3 is a sectional view taken along line IV-IV of FIG. 第１実施形態による弁装置の回転規制部およびその近傍を示す断面斜視図。The cross-sectional perspective view which shows the rotation regulation part of the valve device by 1st Embodiment and the vicinity thereof. 第１実施形態による弁装置のチェック弁を示す斜視図。The perspective view which shows the check valve of the valve device by 1st Embodiment. 第１実施形態による弁装置のチェック弁を展開した状態を示す図。The figure which shows the state which expanded the check valve of the valve device by 1st Embodiment. 比較形態による弁装置のチェック弁を展開した状態を示す図。The figure which shows the state which expanded the check valve of the valve device by the comparative form. 第１実施形態による弁装置の作動時の状態を示す断面図。The cross-sectional view which shows the state at the time of operation of the valve device by 1st Embodiment. 第２実施形態による弁装置のチェック弁を示す斜視図。The perspective view which shows the check valve of the valve device by 2nd Embodiment. 第３実施形態による弁装置の回転規制部およびその近傍を示す断面図。The cross-sectional view which shows the rotation regulation part of the valve device by 3rd Embodiment and the vicinity thereof.

以下、本発明の複数の実施形態による弁装置およびバルブタイミング調整装置を図面に基づき説明する。なお、複数の実施形態において実質的に同一の構成部位には同一の符号を付し、説明を省略する。また、複数の実施形態において実質的に同一の構成部位は、同一または同様の作用効果を奏する。 Hereinafter, a valve device and a valve timing adjusting device according to a plurality of embodiments of the present invention will be described with reference to the drawings. In the plurality of embodiments, substantially the same constituent parts are designated by the same reference numerals, and the description thereof will be omitted. In addition, substantially the same constituent sites in a plurality of embodiments exhibit the same or similar effects.

（第１実施形態）
第１実施形態による弁装置、および、それを用いたバルブタイミング調整装置を図１、２に示す。バルブタイミング調整装置１０は、内燃機関としてのエンジン１のクランク軸２に対するカム軸３の回転位相を変化させることによって、カム軸３が開閉駆動する吸気弁４または排気弁５のうち吸気弁４のバルブタイミングを調整するものである。バルブタイミング調整装置１０は、クランク軸２からカム軸３までの動力伝達経路に設けられている。クランク軸２は、「駆動軸」に対応する。カム軸３は、「従動軸」に対応する。吸気弁４、排気弁５は、「バルブ」に対応する。 (First Embodiment)
The valve device according to the first embodiment and the valve timing adjusting device using the valve device are shown in FIGS. 1 and 2. The valve timing adjusting device 10 is the intake valve 4 of the intake valve 4 or the exhaust valve 5 in which the cam shaft 3 is driven to open and close by changing the rotation phase of the cam shaft 3 with respect to the crank shaft 2 of the engine 1 as an internal combustion engine. It adjusts the valve timing. The valve timing adjusting device 10 is provided in the power transmission path from the crankshaft 2 to the camshaft 3. The crankshaft 2 corresponds to a "drive shaft". The camshaft 3 corresponds to a "driven shaft". The intake valve 4 and the exhaust valve 5 correspond to "valves".

バルブタイミング調整装置１０の構成について図１、２に基づき説明する。バルブタイミング調整装置１０は、位相変換部ＰＣ、作動油供給源ＯＳ、「弁装置」としての作動油制御部ＯＣ、オイル排出部ＯＤ、遅角供給油路ＲＲｓ、進角供給油路ＲＡｓ、ドレン油路としての遅角ドレン油路ＲＲｄおよび進角ドレン油路ＲＡｄ等を備えている。 The configuration of the valve timing adjusting device 10 will be described with reference to FIGS. 1 and 2. The valve timing adjusting device 10 includes a phase conversion unit PC, a hydraulic oil supply source OS, a hydraulic oil control unit OC as a "valve device", an oil discharge unit OD, a retard angle supply oil passage RRs, an advance angle supply oil passage RAs, and a drain. It is provided with a retarded drain oil passage RRd and an advanced drain oil passage RAd as oil passages.

位相変換部ＰＣは、ハウジング２０、ベーンロータ３０を有している。ハウジング２０は、ギア部２１およびケース２２を有している。ケース２２は、筒部２２１、板部２２２、２２３を有している。筒部２２１は、筒状に形成されている。板部２２２は、筒部２２１の一端を塞ぐよう筒部２２１と一体に形成されている。板部２２３は、筒部２２１の他端を塞ぐよう設けられている。これにより、ハウジング２０の内側に空間２００が形成されている。板部２２３は、ボルト１２により筒部２２１に固定されている。ギア部２１は、板部２２３の外縁部に形成されている。 The phase conversion unit PC has a housing 20 and a vane rotor 30. The housing 20 has a gear portion 21 and a case 22. The case 22 has a tubular portion 221 and a plate portion 222, 223. The tubular portion 221 is formed in a tubular shape. The plate portion 222 is integrally formed with the tubular portion 221 so as to close one end of the tubular portion 221. The plate portion 223 is provided so as to close the other end of the tubular portion 221. As a result, the space 200 is formed inside the housing 20. The plate portion 223 is fixed to the cylinder portion 221 by a bolt 12. The gear portion 21 is formed on the outer edge portion of the plate portion 223.

板部２２３は、カム軸３の端部に嵌合している。カム軸３は、ハウジング２０を回転可能に支持している。チェーン６は、ギア部２１とクランク軸２とに巻き掛けられている。ギア部２１は、クランク軸２と連動して回転する。ケース２２は、筒部２２１から径方向内側に突き出す複数の隔壁部２３を形成している。ケース２２の板部２２２の中央には、ケース２２の外側の空間に開口する開口部２４が形成されている。開口部２４は、ベーンロータ３０に対してカム軸３とは反対側に位置する。 The plate portion 223 is fitted to the end portion of the cam shaft 3. The cam shaft 3 rotatably supports the housing 20. The chain 6 is wound around the gear portion 21 and the crankshaft 2. The gear portion 21 rotates in conjunction with the crankshaft 2. The case 22 forms a plurality of partition wall portions 23 protruding inward in the radial direction from the tubular portion 221. An opening 24 that opens into the space outside the case 22 is formed in the center of the plate portion 222 of the case 22. The opening 24 is located on the side opposite to the cam shaft 3 with respect to the vane rotor 30.

ベーンロータ３０は、ボス３１、および、複数のベーン３２を有している。ボス３１は、筒状であり、カム軸３の端部に固定されている。ベーン３２は、ボス３１から径方向外側に向かって各隔壁部２３間に突き出している。ハウジング２０の内側の空間２００は、ベーン３２により遅角室２０１と進角室２０２とに仕切られている。すなわち、ハウジング２０は、ベーンロータ３０との間に遅角室２０１および進角室２０２を形成している。遅角室２０１は、ベーン３２に対して周方向の一方に位置している。進角室２０２は、ベーン３２に対して周方向の他方に位置している。ベーンロータ３０は、遅角室２０１および進角室２０２の油圧に応じて、ハウジング２０に対して遅角方向または進角方向へ相対回転する。 The vane rotor 30 has a boss 31 and a plurality of vanes 32. The boss 31 has a tubular shape and is fixed to the end of the cam shaft 3. The vane 32 projects radially outward from the boss 31 between the partition walls 23. The space 200 inside the housing 20 is divided into a retard chamber 201 and an advance chamber 202 by a vane 32. That is, the housing 20 forms a retard chamber 201 and an advance chamber 202 with the vane rotor 30. The retard chamber 201 is located on one side of the vane 32 in the circumferential direction. The advance chamber 202 is located on the other side of the vane 32 in the circumferential direction. The vane rotor 30 rotates relative to the housing 20 in the retard direction or the advance direction according to the hydraulic pressure of the retard chamber 201 and the advance chamber 202.

本実施形態では、作動油制御部ＯＣは、弁装置１１である。弁装置１１は、スリーブ４００、スプール６０、「チェック弁」としての遅角供給チェック弁７１および進角供給チェック弁７２、回転規制部９０等を備えている。弁装置１１は、流体としての作動油の流れを制御し、遅角室２０１および進角室２０２への作動油の供給、ならびに、遅角室２０１および進角室２０２からの作動油の排出を制御する。 In the present embodiment, the hydraulic oil control unit OC is the valve device 11. The valve device 11 includes a sleeve 400, a spool 60, a check valve 71 as a "check valve", an advance check valve 72, a rotation control unit 90, and the like. The valve device 11 controls the flow of the hydraulic oil as a fluid, supplies the hydraulic oil to the retard chamber 201 and the advance chamber 202, and discharges the hydraulic oil from the retard chamber 201 and the advance chamber 202. Control.

本実施形態では、弁装置１１は、ハウジング２０およびベーンロータ３０の中央部に設けられている（図１、２参照）。すなわち、弁装置１１は、少なくとも一部がハウジング２０の内側に位置するよう設けられている。スリーブ４００は、アウタースリーブ４０、「筒部材」としてのインナースリーブ５０を有している。 In this embodiment, the valve device 11 is provided at the center of the housing 20 and the vane rotor 30 (see FIGS. 1 and 2). That is, the valve device 11 is provided so that at least a part thereof is located inside the housing 20. The sleeve 400 has an outer sleeve 40 and an inner sleeve 50 as a "cylinder member".

アウタースリーブ４０は、例えば鉄を含む比較的硬度が高い材料により略円筒状に形成されている。アウタースリーブ４０は、内周壁が略円筒面状に形成されている。図３に示すように、アウタースリーブ４０の一方の端部の外周壁には、ねじ部４１が形成されている。アウタースリーブ４０の他方の端部側には、外周壁から径方向外側へ環状に延びる係止部４９が形成されている。 The outer sleeve 40 is formed in a substantially cylindrical shape by a material having a relatively high hardness including iron, for example. The outer sleeve 40 has an inner peripheral wall formed in a substantially cylindrical surface shape. As shown in FIG. 3, a threaded portion 41 is formed on the outer peripheral wall of one end of the outer sleeve 40. On the other end side of the outer sleeve 40, a locking portion 49 extending radially outward from the outer peripheral wall is formed.

カム軸３のバルブタイミング調整装置１０側の端部には、軸穴部１００、供給穴部１０１が形成されている。軸穴部１００は、カム軸３のバルブタイミング調整装置１０側の端面の中央からカム軸３の軸方向に延びるようにして形成されている。供給穴部１０１は、カム軸３の外壁から径方向内側に延びて軸穴部１００に連通するよう形成されている。 A shaft hole portion 100 and a supply hole portion 101 are formed at the end of the camshaft 3 on the valve timing adjusting device 10 side. The shaft hole portion 100 is formed so as to extend in the axial direction of the cam shaft 3 from the center of the end surface of the cam shaft 3 on the valve timing adjusting device 10 side. The supply hole portion 101 is formed so as to extend radially inward from the outer wall of the cam shaft 3 and communicate with the shaft hole portion 100.

カム軸３の軸穴部１００の内壁には、アウタースリーブ４０のねじ部４１にねじ結合可能な軸側ねじ部１１０が形成されている。アウタースリーブ４０は、ベーンロータ３０のボス３１の内側を通り、ねじ部４１がカム軸３の軸側ねじ部１１０に結合するようにしてカム軸３に固定される。このとき、係止部４９は、ベーンロータ３０のボス３１のカム軸３とは反対側の端面を係止する。これにより、ベーンロータ３０は、カム軸３と係止部４９とに挟み込まれるようにしてカム軸３に固定される。このように、アウタースリーブ４０は、ベーンロータ３０の中央部に設けられる。 On the inner wall of the shaft hole portion 100 of the cam shaft 3, a shaft-side threaded portion 110 that can be screwed to the threaded portion 41 of the outer sleeve 40 is formed. The outer sleeve 40 passes through the inside of the boss 31 of the vane rotor 30 and is fixed to the cam shaft 3 so that the screw portion 41 is coupled to the shaft side screw portion 110 of the cam shaft 3. At this time, the locking portion 49 locks the end surface of the vane rotor 30 on the side opposite to the cam shaft 3 of the boss 31. As a result, the vane rotor 30 is fixed to the cam shaft 3 so as to be sandwiched between the cam shaft 3 and the locking portion 49. In this way, the outer sleeve 40 is provided at the center of the vane rotor 30.

本実施形態では、作動油供給源ＯＳは、オイルポンプ８である。また、オイル排出部ＯＤは、オイルパン７である。オイルポンプ８は、供給穴部１０１に接続される。オイルポンプ８は、オイルパン７に貯留されている作動油を汲み上げ、供給穴部１０１に供給する。これにより、軸穴部１００には、作動油が流入する。 In this embodiment, the hydraulic oil supply source OS is the oil pump 8. The oil discharge unit OD is the oil pan 7. The oil pump 8 is connected to the supply hole 101. The oil pump 8 pumps the hydraulic oil stored in the oil pan 7 and supplies it to the supply hole 101. As a result, hydraulic oil flows into the shaft hole portion 100.

「筒部材」としてのインナースリーブ５０は、例えばアルミニウムを含む比較的硬度が低い材料により略円筒状に形成されている。つまり、インナースリーブ５０は、アウタースリーブ４０よりも硬度が低い材料により形成されている。インナースリーブ５０は、外周壁が略円筒面状に形成されている。 The inner sleeve 50 as the "cylindrical member" is formed in a substantially cylindrical shape by a material having a relatively low hardness, for example, aluminum. That is, the inner sleeve 50 is made of a material having a hardness lower than that of the outer sleeve 40. The outer peripheral wall of the inner sleeve 50 is formed in a substantially cylindrical surface shape.

図３に示すように、インナースリーブ５０は、外周壁がアウタースリーブ４０の内周壁に嵌合するようアウタースリーブ４０の内側に設けられている。インナースリーブ５０は、アウタースリーブ４０に対し相対移動不能である。 As shown in FIG. 3, the inner sleeve 50 is provided inside the outer sleeve 40 so that the outer peripheral wall fits into the inner peripheral wall of the outer sleeve 40. The inner sleeve 50 is immovable relative to the outer sleeve 40.

インナースリーブ５０の一端には、スリーブ封止部５１が設けられている。スリーブ封止部５１は、インナースリーブ５０の一端を塞いでいる。 A sleeve sealing portion 51 is provided at one end of the inner sleeve 50. The sleeve sealing portion 51 closes one end of the inner sleeve 50.

スプール６０は、例えば金属により略円筒状に形成されている。スプール６０は、外周壁がインナースリーブ５０の内周壁５４と摺動し、軸方向に往復移動可能なようインナースリーブ５０の内側に設けられている。 The spool 60 is formed of, for example, a metal in a substantially cylindrical shape. The spool 60 is provided inside the inner sleeve 50 so that the outer peripheral wall slides on the inner peripheral wall 54 of the inner sleeve 50 and can reciprocate in the axial direction.

スプール６０の一端には、スプール封止部６２が設けられている。スプール封止部６２は、スプール６０の一端を塞いでいる。インナースリーブ５０の内側におけるスリーブ封止部５１とスプール６０の他端との間には、容積可変空間Ｓｖが形成されている。容積可変空間Ｓｖは、スプール６０がインナースリーブ５０に対し軸方向へ移動するとき、容積が変化する。すなわち、スリーブ封止部５１は、スプール６０との間に、容積が変化する容積可変空間Ｓｖを形成している。 A spool sealing portion 62 is provided at one end of the spool 60. The spool sealing portion 62 closes one end of the spool 60. A variable volume space Sv is formed between the sleeve sealing portion 51 inside the inner sleeve 50 and the other end of the spool 60. The volume of the variable volume space Sv changes when the spool 60 moves in the axial direction with respect to the inner sleeve 50. That is, the sleeve sealing portion 51 forms a volume variable space Sv whose volume changes with the spool 60.

容積可変空間Ｓｖには、スプリング６３が設けられている。スプリング６３は、所謂コイルスプリングであり、一端がスリーブ封止部５１に当接し、他端がスプール６０の他端に当接している。スプリング６３は、スプール６０をスリーブ封止部５１とは反対側へ付勢している。 A spring 63 is provided in the variable volume space Sv. The spring 63 is a so-called coil spring, one end of which is in contact with the sleeve sealing portion 51 and the other end of which is in contact with the other end of the spool 60. The spring 63 urges the spool 60 to the side opposite to the sleeve sealing portion 51.

アウタースリーブ４０の他方の端部の径方向内側には、係止部６５が設けられている。係止部６５は有底筒状に形成され、外周壁がアウタースリーブ４０の内周壁に嵌合するよう設けられている。係止部６５の底部の中央には、穴部が形成されており、当該穴部の内側にスプール封止部６２が位置している。 A locking portion 65 is provided inside the other end of the outer sleeve 40 in the radial direction. The locking portion 65 is formed in a bottomed tubular shape, and the outer peripheral wall is provided so as to fit into the inner peripheral wall of the outer sleeve 40. A hole is formed in the center of the bottom of the locking portion 65, and the spool sealing portion 62 is located inside the hole.

係止部６５は、底部により、スプール６０の一端を係止可能である。係止部６５は、スプール６０のスリーブ封止部５１とは反対側への移動を規制可能である。これにより、スプール６０は、インナースリーブ５０の内側からの脱落が抑制されている。 The locking portion 65 can lock one end of the spool 60 by the bottom portion. The locking portion 65 can regulate the movement of the spool 60 to the side opposite to the sleeve sealing portion 51. As a result, the spool 60 is prevented from falling off from the inside of the inner sleeve 50.

スプール６０は、係止部６５に当接する位置から、スリーブ封止部５１に当接する位置まで、軸方向に移動可能である。すなわち、係止部６５に当接する位置（図３参照）から、スリーブ封止部５１に当接する位置までが、スリーブ４００に対する移動可能範囲である。以下、このスプール６０の移動可能範囲を「ストローク区間」と呼ぶ。 The spool 60 can move in the axial direction from the position where it abuts on the locking portion 65 to the position where it abuts on the sleeve sealing portion 51. That is, the movable range with respect to the sleeve 400 is from the position of contact with the locking portion 65 (see FIG. 3) to the position of contact with the sleeve sealing portion 51. Hereinafter, the movable range of the spool 60 is referred to as a “stroke section”.

図３に示すように、インナースリーブ５０のスリーブ封止部５１側の端部は、外径がアウタースリーブ４０の内径より小さく形成されている。これにより、インナースリーブ５０のスリーブ封止部５１側の端部の外周壁とアウタースリーブ４０の内周壁との間には、略円筒状の空間である筒状空間Ｓｔ１が形成されている。 As shown in FIG. 3, the outer diameter of the end of the inner sleeve 50 on the sleeve sealing portion 51 side is formed to be smaller than the inner diameter of the outer sleeve 40. As a result, a tubular space St1 which is a substantially cylindrical space is formed between the outer peripheral wall of the end portion of the inner sleeve 50 on the sleeve sealing portion 51 side and the inner peripheral wall of the outer sleeve 40.

また、インナースリーブ５０には、環状凹部Ｈｔが形成されている。環状凹部Ｈｔは、インナースリーブ５０の外周壁の係止部４９に対応する位置から径方向内側へ環状に凹むよう形成されている。これにより、環状凹部Ｈｔとアウタースリーブ４０の内周壁との間には、環状の空間である環状空間Ｓｔ２が形成されている。 Further, the inner sleeve 50 is formed with an annular recess Ht. The annular recess Ht is formed so as to be annularly recessed inward in the radial direction from a position corresponding to the locking portion 49 of the outer peripheral wall of the inner sleeve 50. As a result, an annular space St2, which is an annular space, is formed between the annular recess Ht and the inner peripheral wall of the outer sleeve 40.

また、インナースリーブ５０には、流路溝部５２が形成されている。流路溝部５２は、インナースリーブ５０の外周壁から径方向内側へ凹み、かつ、インナースリーブ５０の軸方向へ延びるようにして形成されている。流路溝部５２は、軸方向供給油路ＲｓＡを形成している。すなわち、軸方向供給油路ＲｓＡは、アウタースリーブ４０とインナースリーブ５０との界面Ｔ１においてスリーブ４００の軸方向に延びるよう形成されている。軸方向供給油路ＲｓＡは、一端が筒状空間Ｓｔ１に接続し、他端が環状空間Ｓｔ２に接続している。 Further, the inner sleeve 50 is formed with a flow path groove portion 52. The flow path groove portion 52 is formed so as to be recessed inward in the radial direction from the outer peripheral wall of the inner sleeve 50 and extend in the axial direction of the inner sleeve 50. The flow path groove portion 52 forms an axial supply oil passage RsA. That is, the axial supply oil passage RsA is formed so as to extend in the axial direction of the sleeve 400 at the interface T1 between the outer sleeve 40 and the inner sleeve 50. One end of the axial supply oil passage RsA is connected to the tubular space St1 and the other end is connected to the annular space St2.

また、インナースリーブ５０には、環状溝部５５が形成されている。環状溝部５５は、遅角環状溝部５１１、進角環状溝部５１２を有している。遅角環状溝部５１１は、インナースリーブ５０の内周壁５４の筒状空間Ｓｔ１の端部に対応する位置から径方向外側へ凹みつつ周方向に延びて環状に形成されている。進角環状溝部５１２は、インナースリーブ５０の内周壁５４の環状凹部Ｈｔに対応する位置から径方向外側へ凹みつつ周方向に延びて環状に形成されている。 Further, the inner sleeve 50 is formed with an annular groove portion 55. The annular groove portion 55 has a retarded annular groove portion 511 and an advance angle annular groove portion 512. The retarded annular groove portion 511 is formed in an annular shape so as to extend in the circumferential direction while being recessed radially outward from a position corresponding to the end portion of the tubular space St1 of the inner peripheral wall 54 of the inner sleeve 50. The advance annular groove portion 512 is formed in an annular shape so as to extend in the circumferential direction while being recessed radially outward from a position corresponding to the annular recess Ht of the inner peripheral wall 54 of the inner sleeve 50.

スリーブ４００は、「流入穴」としての遅角供給開口部ＯＲｓ、「流入穴」としての進角供給開口部ＯＡｓ、遅角開口部ＯＲ、進角開口部ＯＡを有している。 The sleeve 400 has a retarded angle supply opening ORs as an "inflow hole", an advance angle supply opening OAs as an "inflow hole", a retarded angle opening OR, and an advance angle opening OA.

遅角供給開口部ＯＲｓは、インナースリーブ５０の遅角環状溝部５１１の底面５５０と、インナースリーブ５０の外壁５３のうち筒状空間Ｓｔ１の端部に対応する外壁である遅角外壁５３１とを連通するよう形成されている。これにより、遅角供給開口部ＯＲｓは、インナースリーブ５０の内側の空間と筒状空間Ｓｔ１および軸方向供給油路ＲｓＡとを接続している。ここで、遅角環状溝部５１１の底面５５０、および、遅角外壁５３１は、略円筒状に形成されている。 The retard angle supply openings ORs communicate the bottom surface 550 of the retard angle annular groove portion 511 of the inner sleeve 50 and the retard angle outer wall 531 which is an outer wall corresponding to the end portion of the tubular space St1 in the outer wall 53 of the inner sleeve 50. It is formed to do. As a result, the retard angle supply openings ORs connect the space inside the inner sleeve 50 with the tubular space St1 and the axial supply oil passage RsA. Here, the bottom surface 550 of the retarded annular groove portion 511 and the retarded outer wall 531 are formed in a substantially cylindrical shape.

また、図４に示すように、遅角供給開口部ＯＲｓは、遅角環状溝部５１１の周方向に複数形成されている。本実施形態では、遅角供給開口部ＯＲｓは、５つ形成されている。５つの遅角供給開口部ＯＲｓは、１番目から５番目までが周方向に４５度の等間隔で形成され、５番目から１番目までが１８０度の間隔となるよう形成されている。つまり、遅角供給開口部ＯＲｓは、遅角環状溝部５１１の周方向の全範囲のうち概ね半分の範囲に形成されている。すなわち、遅角供給開口部ＯＲｓは、遅角環状溝部５１１の周方向における特定の部位に偏って形成されている。このように、遅角供給開口部ＯＲｓは、遅角環状溝部５１１の周方向の全範囲においては、不等間隔で複数形成されている。 Further, as shown in FIG. 4, a plurality of retard angle supply openings ORs are formed in the circumferential direction of the retard angle annular groove portion 511. In this embodiment, five retard angle supply openings ORs are formed. The five retarded angle supply openings ORs are formed so that the first to fifth positions are formed at equal intervals of 45 degrees in the circumferential direction, and the fifth to first positions are formed at intervals of 180 degrees. That is, the retard angle supply openings ORs are formed in approximately half of the entire circumferential range of the retard angle annular groove portion 511. That is, the retard angle supply openings ORs are formed unevenly in a specific portion in the circumferential direction of the retard angle annular groove portion 511. As described above, a plurality of retard angle supply openings ORs are formed at unequal intervals in the entire circumferential direction of the retard angle annular groove portion 511.

進角供給開口部ＯＡｓは、インナースリーブ５０の進角環状溝部５１２の底面５５０と、インナースリーブ５０の外壁５３のうち環状凹部Ｈｔに対応する外壁である進角外壁５３２とを連通するよう形成されている。これにより、進角供給開口部ＯＡｓは、インナースリーブ５０の内側の空間と環状空間Ｓｔ２および軸方向供給油路ＲｓＡとを接続している。ここで、進角環状溝部５１２の底面５５０、および、進角外壁５３２は、略円筒状に形成されている。 The advance angle supply opening OAs is formed so as to communicate the bottom surface 550 of the advance angle annular groove portion 512 of the inner sleeve 50 and the advance angle outer wall 532 which is an outer wall corresponding to the annular recess Ht in the outer wall 53 of the inner sleeve 50. ing. As a result, the advance angle supply opening OAs connects the space inside the inner sleeve 50 with the annular space St2 and the axial supply oil passage RsA. Here, the bottom surface 550 of the advance angle annular groove portion 512 and the advance angle outer wall 532 are formed in a substantially cylindrical shape.

また、進角供給開口部ＯＡｓは、遅角供給開口部ＯＲｓと同様、進角環状溝部５１２の周方向に複数形成されている。本実施形態では、進角供給開口部ＯＡｓは、５つ形成されている。５つの進角供給開口部ＯＡｓは、１番目から５番目までが周方向に４５度の等間隔で形成され、５番目から１番目までが１８０度の間隔となるよう形成されている。つまり、進角供給開口部ＯＡｓは、進角環状溝部５１２の周方向の全範囲のうち概ね半分の範囲に形成されている。すなわち、進角供給開口部ＯＡｓは、進角環状溝部５１２の周方向における特定の部位に偏って形成されている。このように、進角供給開口部ＯＡｓは、進角環状溝部５１２の周方向の全範囲においては、不等間隔で複数形成されている。 Further, a plurality of advance angle supply openings OAs are formed in the circumferential direction of the advance angle annular groove portion 512, similarly to the retard angle supply opening openings ORs. In this embodiment, five advance angle supply openings OAs are formed. The five advance feed openings OAs are formed so that the first to fifth are formed at equal intervals of 45 degrees in the circumferential direction, and the fifth to first are formed at intervals of 180 degrees. That is, the advance angle supply opening OAs is formed in approximately half of the entire circumferential range of the advance angle annular groove portion 512. That is, the advance angle supply opening OAs is formed unevenly at a specific portion in the circumferential direction of the advance angle annular groove portion 512. As described above, a plurality of advance angle supply openings OAs are formed at unequal intervals in the entire circumferential direction of the advance angle annular groove portion 512.

遅角開口部ＯＲは、スリーブ４００の径方向に延びてインナースリーブ５０の内側の空間とアウタースリーブ４０の外側の空間とを接続するよう形成されている。遅角開口部ＯＲは、スリーブ４００の周方向に複数形成されている。遅角開口部ＯＲは、遅角油路３０１を経由して遅角室２０１に連通している。 The retarded opening OR is formed so as to extend in the radial direction of the sleeve 400 and connect the space inside the inner sleeve 50 and the space outside the outer sleeve 40. A plurality of retard angle openings OR are formed in the circumferential direction of the sleeve 400. The retard angle opening OR communicates with the retard angle chamber 201 via the retard angle oil passage 301.

進角開口部ＯＡは、スリーブ４００の径方向に延びてインナースリーブ５０の内側の空間とアウタースリーブ４０の外側の空間とを接続するよう形成されている。進角開口部ＯＡは、遅角開口部ＯＲに対し係止部４９側に形成されている。進角開口部ＯＡは、スリーブ４００の周方向に複数形成されている。進角開口部ＯＡは、進角油路３０２を経由して進角室２０２に連通している。 The advance opening OA is formed so as to extend in the radial direction of the sleeve 400 and connect the space inside the inner sleeve 50 and the space outside the outer sleeve 40. The advance opening OA is formed on the locking portion 49 side with respect to the retard opening OR. A plurality of advance angle openings OA are formed in the circumferential direction of the sleeve 400. The advance angle opening OA communicates with the advance angle chamber 202 via the advance angle oil passage 302.

スプール６０は、遅角供給凹部ＨＲｓ、遅角ドレン凹部ＨＲｄ、進角ドレン凹部ＨＡｄ、進角供給凹部ＨＡｓ、ドレン開口部Ｏｄ１、Ｏｄ２を有している。遅角供給凹部ＨＲｓ、遅角ドレン凹部ＨＲｄ、進角ドレン凹部ＨＡｄ、進角供給凹部ＨＡｓは、それぞれ、スプール６０の外周壁から径方向内側へ凹むようにして環状に形成されている。遅角供給凹部ＨＲｓ、遅角ドレン凹部ＨＲｄ、進角ドレン凹部ＨＡｄ、進角供給凹部ＨＡｓは、この順でスプール６０の軸方向に並ぶよう形成されている。また、遅角ドレン凹部ＨＲｄと進角ドレン凹部ＨＡｄとは、一体に形成されている。遅角ドレン凹部ＨＲｄおよび進角ドレン凹部ＨＡｄは、インナースリーブ５０の内周壁との間に特定空間Ｓｓを形成している。すなわち、スプール６０は、スリーブ４００との間に特定空間Ｓｓを形成している。 The spool 60 has a retard angle supply recess HRs, a retard angle drain recess HRd, an advance angle drain recess HAd, an advance angle supply recess HAs, and drain openings Od1 and Od2. The retard angle supply recess HRs, the retard angle drain recess HRd, the advance angle drain recess HAd, and the advance angle supply recess HAs are each formed in an annular shape so as to be recessed inward in the radial direction from the outer peripheral wall of the spool 60. The retard angle supply recess HRs, the retard angle drain recess HRd, the advance angle drain recess HAd, and the advance angle supply recess HAs are formed so as to be arranged in this order in the axial direction of the spool 60. Further, the retarded drain recess HRd and the advanced drain recess HAd are integrally formed. The retarded drain recess HRd and the advanced drain recess HAd form a specific space Ss with the inner peripheral wall of the inner sleeve 50. That is, the spool 60 forms a specific space Ss with the sleeve 400.

ドレン開口部Ｏｄ１は、スプール６０の内側の空間と遅角ドレン凹部ＨＲｄおよび進角ドレン凹部ＨＡｄ、すなわち、特定空間Ｓｓとを連通するよう形成されている。ドレン開口部Ｏｄ２は、スプール６０のスプール封止部６２側の端部において内側の空間と外側の空間とを連通するよう形成されている。なお、ドレン開口部Ｏｄ１、Ｏｄ２は、それぞれ、スプール６０の周方向に複数形成されている。 The drain opening Od1 is formed so as to communicate the space inside the spool 60 with the retarded drain recess HRd and the advanced drain recess HAd, that is, the specific space Ss. The drain opening Od2 is formed so as to communicate the inner space and the outer space at the end of the spool 60 on the spool sealing portion 62 side. A plurality of drain openings Od1 and Od2 are formed in the circumferential direction of the spool 60, respectively.

遅角供給油路ＲＲｓは、弁装置１１を経由してオイルポンプ８と遅角室２０１とを接続している。進角供給油路ＲＡｓは、弁装置１１を経由してオイルポンプ８と進角室２０２とを接続している。ドレン油路としての遅角ドレン油路ＲＲｄは、遅角室２０１とオイルパン７とを接続している。ドレン油路としての進角ドレン油路ＲＡｄは、進角室２０２とオイルパン７とを接続している。 The retard angle supply oil passages RRs connect the oil pump 8 and the retard angle chamber 201 via the valve device 11. The advance angle supply oil passage RAs connects the oil pump 8 and the advance angle chamber 202 via the valve device 11. The retard angle drain oil passage RRd as a drain oil passage connects the retard angle chamber 201 and the oil pan 7. The advance angle drain oil passage RAd as a drain oil passage connects the advance angle chamber 202 and the oil pan 7.

遅角供給油路ＲＲｓは、供給穴部１０１、軸穴部１００、筒状空間Ｓｔ１、軸方向供給油路ＲｓＡ、遅角供給開口部ＯＲｓ、遅角環状溝部５１１、遅角供給凹部ＨＲｓ、遅角開口部ＯＲ、遅角油路３０１を経由して、オイルポンプ８と遅角室２０１とを接続している。 The retard angle supply oil passages RRs include a supply hole portion 101, a shaft hole portion 100, a tubular space St1, an axial supply oil passage RsA, a retard angle supply opening ORs, a retard angle annular groove portion 511, a retard angle supply recess HRs, and a retard. The oil pump 8 and the retarded chamber 201 are connected via the corner opening OR and the retarded oil passage 301.

進角供給油路ＲＡｓは、供給穴部１０１、軸穴部１００、筒状空間Ｓｔ１、軸方向供給油路ＲｓＡ、進角供給開口部ＯＡｓ、進角環状溝部５１２、進角供給凹部ＨＡｓ、進角開口部ＯＡ、進角油路３０２を経由して、オイルポンプ８と進角室２０２とを接続している。 The advance angle supply oil passage RAs includes a supply hole portion 101, a shaft hole portion 100, a tubular space St1, an axial supply oil passage RsA, an advance angle supply opening OAs, an advance angle annular groove portion 512, an advance angle supply recess HAs, and an advance angle supply recess HAs. The oil pump 8 and the advance chamber 202 are connected via the corner opening OA and the advance oil passage 302.

遅角ドレン油路ＲＲｄは、遅角油路３０１、遅角開口部ＯＲ、遅角ドレン凹部ＨＲｄ、ドレン開口部Ｏｄ１、Ｏｄ２を経由して、遅角室２０１とオイルパン７とを接続している。 The retard angle drain oil passage RRd connects the retard angle chamber 201 and the oil pan 7 via the retard angle oil passage 301, the retard angle opening OR, the retard angle drain recess HRd, the drain openings Od1 and Od2. There is.

進角ドレン油路ＲＡｄは、進角油路３０２、進角開口部ＯＡ、進角ドレン凹部ＨＡｄ、ドレン開口部Ｏｄ１、Ｏｄ２を経由して、進角室２０２とオイルパン７とを接続している。このように、遅角供給油路ＲＲｓ、進角供給油路ＲＡｓ、遅角ドレン油路ＲＲｄ、進角ドレン油路ＲＡｄは、一部が弁装置１１の内部に形成されている。 The advance drain oil passage RAd connects the advance chamber 202 and the oil pan 7 via the advance oil passage 302, the advance opening OA, the advance drain recess HAd, the drain openings Od1 and Od2. There is. As described above, a part of the retard angle supply oil passage RRs, the advance angle supply oil passage RAs, the retard angle drain oil passage RRd, and the advance angle drain oil passage RAd is formed inside the valve device 11.

スプール６０が係止部６５に当接しているとき（図３参照）、すなわち、スプール６０がストローク区間の一方の端部に位置するとき、スプール６０が遅角開口部ＯＲを開いているため、オイルポンプ８は、遅角供給油路ＲＲｓの供給穴部１０１、軸穴部１００、筒状空間Ｓｔ１、軸方向供給油路ＲｓＡ、遅角供給開口部ＯＲｓ、遅角環状溝部５１１、遅角供給凹部ＨＲｓ、遅角開口部ＯＲ、遅角油路３０１を経由して遅角室２０１に連通する。これにより、オイルポンプ８から遅角供給油路ＲＲｓを経由して遅角室２０１に作動油を供給することができる。また、このとき、進角室２０２は、進角ドレン油路ＲＡｄの進角油路３０２、進角開口部ＯＡ、進角ドレン凹部ＨＡｄ、ドレン開口部Ｏｄ１、Ｏｄ２を経由してオイルパン７に連通する。これにより、進角室２０２から進角ドレン油路ＲＡｄを経由してオイルパン７に作動油を排出することができる。 When the spool 60 is in contact with the locking portion 65 (see FIG. 3), that is, when the spool 60 is located at one end of the stroke section, the spool 60 has the retard opening OR open. The oil pump 8 includes a supply hole portion 101 of a retard angle supply oil passage RRs, a shaft hole portion 100, a tubular space St1, an axial supply oil passage RsA, a retard angle supply opening ORs, a retard angle annular groove portion 511, and a retard angle supply. It communicates with the retard angle chamber 201 via the recess HRs, the retard angle opening OR, and the retard angle oil passage 301. As a result, the hydraulic oil can be supplied from the oil pump 8 to the retard angle chamber 201 via the retard angle supply oil passage RRs. At this time, the advance chamber 202 is connected to the oil pan 7 via the advance oil passage 302 of the advance drain oil passage RAd, the advance opening OA, the advance drain recess HAd, the drain openings Od1 and Od2. Communicate. As a result, the hydraulic oil can be discharged from the advance angle chamber 202 to the oil pan 7 via the advance angle drain oil passage RAd.

スプール６０が係止部６５とスリーブ封止部５１との間に位置しているとき、すなわち、スプール６０がストローク区間の中間に位置するとき、オイルポンプ８は、進角供給油路ＲＡｓの供給穴部１０１、軸穴部１００、筒状空間Ｓｔ１、軸方向供給油路ＲｓＡ、進角供給開口部ＯＡｓ、進角環状溝部５１２、進角供給凹部ＨＡｓ、進角開口部ＯＡ、進角油路３０２を経由して進角室２０２に連通する。なお、このとき、遅角供給油路ＲＲｓによりオイルポンプ８と遅角室２０１とは連通している。これにより、オイルポンプ８から遅角供給油路ＲＲｓ、進角供給油路ＲＡｓを経由して遅角室２０１、進角室２０２に作動油を供給することができる。ただし、スプール６０により遅角ドレン油路ＲＲｄおよび進角ドレン油路ＲＡｄは閉じられている、すなわち、遮断されているため、作動油は遅角室２０１および進角室２０２からオイルパン７に排出されない。 When the spool 60 is located between the locking portion 65 and the sleeve sealing portion 51, that is, when the spool 60 is located in the middle of the stroke section, the oil pump 8 supplies the lead angle supply oil passage RAs. Hole 101, Shaft hole 100, Cylindrical space St1, Axial supply oil passage RsA, Advance angle supply opening OAs, Advance angle annular groove 512, Advance angle supply recess HAs, Advance angle opening OA, Advance angle oil passage It communicates with the advance chamber 202 via 302. At this time, the oil pump 8 and the retard angle chamber 201 communicate with each other by the retard angle supply oil passage RRs. As a result, hydraulic oil can be supplied from the oil pump 8 to the retard angle chamber 201 and the advance angle chamber 202 via the retard angle supply oil passage RRs and the advance angle supply oil passage RAs. However, since the retard angle drain oil passage RRd and the advance angle drain oil passage RAd are closed by the spool 60, that is, they are shut off, the hydraulic oil is discharged from the retard angle chamber 201 and the advance angle chamber 202 to the oil pan 7. Not done.

スプール６０がスリーブ封止部５１に当接しているとき、すなわち、スプール６０がストローク区間の他方の端部に位置するとき、遅角室２０１は、遅角ドレン油路ＲＲｄの遅角油路３０１、遅角開口部ＯＲ、遅角ドレン凹部ＨＲｄ、ドレン開口部Ｏｄ１、Ｏｄ２を経由してオイルパン７に連通する。なお、このとき、進角供給油路ＲＡｓによりオイルポンプ８と進角室２０２とは連通している。これにより、遅角室２０１から遅角ドレン油路ＲＲｄを経由してオイルパン７に作動油を排出することができるとともに、オイルポンプ８から進角供給油路ＲＡｓを経由して進角室２０２に作動油を供給することができる。 When the spool 60 is in contact with the sleeve sealing portion 51, that is, when the spool 60 is located at the other end of the stroke section, the retard chamber 201 is the retard oil passage 301 of the retard drain oil passage RRd. , The retard angle opening OR, the retard angle drain recess HRd, and the drain openings Od1 and Od2 are communicated with the oil pan 7. At this time, the oil pump 8 and the advance chamber 202 communicate with each other by the advance angle supply oil passage RAs. As a result, the hydraulic oil can be discharged from the retard chamber 201 to the oil pan 7 via the retard drain oil passage RRd, and the advance chamber 202 is discharged from the oil pump 8 via the advance supply oil passage RAs. Can be supplied with hydraulic oil.

アウタースリーブ４０のスリーブ封止部５１側の端部の内側、すなわち、遅角供給油路ＲＲｓおよび進角供給油路ＲＡｓの途中には、フィルタ６６が設けられている。フィルタ６６は、例えば円板状のメッシュである。フィルタ６６は、作動油に含まれる異物を捕集可能である。そのため、フィルタ６６の下流側、すなわち、オイルポンプ８とは反対側に異物が流れるのを抑制することができる。 A filter 66 is provided inside the end of the outer sleeve 40 on the sleeve sealing portion 51 side, that is, in the middle of the retard angle supply oil passage RRs and the advance angle supply oil passage RAs. The filter 66 is, for example, a disk-shaped mesh. The filter 66 can collect foreign matter contained in the hydraulic oil. Therefore, it is possible to suppress the flow of foreign matter to the downstream side of the filter 66, that is, the side opposite to the oil pump 8.

「チェック弁」としての遅角供給チェック弁７１は、弁本体７００を有している。弁本体７００は、単一の板材を長手方向が周方向に沿うよう巻くことにより筒状に形成されている。より具体的には、弁本体７００は、例えば長方形の金属薄板を長手方向が周方向に沿うよう曲げて巻くことにより略円筒状に形成されている。弁本体７００は、径方向に弾性変形可能である。図６は、遅角供給チェック弁７１の斜視図である。なお、弁本体７００は、周方向において両端部が重なるようにして形成されている。 The check valve 71 as a "check valve" has a valve body 700. The valve body 700 is formed in a tubular shape by winding a single plate member so that the longitudinal direction is along the circumferential direction. More specifically, the valve body 700 is formed in a substantially cylindrical shape, for example, by bending and winding a rectangular thin metal plate so that the longitudinal direction is along the circumferential direction. The valve body 700 is elastically deformable in the radial direction. FIG. 6 is a perspective view of the retard angle supply check valve 71. The valve body 700 is formed so that both ends overlap in the circumferential direction.

遅角供給チェック弁７１は、弁本体７００の周方向が遅角環状溝部５１１の底面５５０の周方向に沿うよう遅角環状溝部５１１に設けられ、遅角供給開口部ＯＲｓを経由してインナースリーブ５０の内側へ向かう作動油の流れを許容し、インナースリーブ５０の内側から遅角供給開口部ＯＲｓへ向かう作動油の流れを規制可能である。 The retard angle supply check valve 71 is provided in the retard angle annular groove portion 511 so that the circumferential direction of the valve body 700 is along the circumferential direction of the bottom surface 550 of the retard angle annular groove portion 511, and the inner sleeve is provided via the retard angle supply opening ORs. It is possible to allow the flow of hydraulic oil toward the inside of the inner sleeve 50 and regulate the flow of hydraulic oil from the inside of the inner sleeve 50 toward the retarded angle supply openings ORs.

より具体的には、作動油が遅角供給油路ＲＲｓにおいて遅角供給開口部ＯＲｓ側から遅角供給凹部ＨＲｓ側へ流れるとき、遅角供給チェック弁７１の弁本体７００は、外周壁が作動油により押され径方向内側へ縮まるよう、すなわち、内径が縮小するようにして変形する。これにより、遅角供給チェック弁７１の弁本体７００の外周壁が遅角供給開口部ＯＲｓおよび遅角環状溝部５１１の底面５５０から離間し、作動油は、遅角供給チェック弁７１を経由して遅角供給凹部ＨＲｓ側へ流れることができる。このとき、弁本体７００は、両端部の重なり範囲の長さを拡大しながら一部が重なった状態を維持している。 More specifically, when the hydraulic oil flows from the retard angle supply opening ORs side to the retard angle supply recess HRs side in the retard angle supply oil passage RRs, the outer peripheral wall of the valve body 700 of the retard angle supply check valve 71 operates. It is deformed so that it is pushed by oil and shrinks inward in the radial direction, that is, the inner diameter shrinks. As a result, the outer peripheral wall of the valve body 700 of the check valve 71 for the retard angle is separated from the retard angle supply opening ORs and the bottom surface 550 of the annular groove portion 511 for the retard angle, and the hydraulic oil passes through the check valve 71 for the retard angle supply. It can flow to the retarded angle supply recess HRs side. At this time, the valve body 700 maintains a partially overlapped state while expanding the length of the overlapping range at both ends.

遅角供給油路ＲＲｓを流れる作動油の流量が所定値以下になると、遅角供給チェック弁７１の弁本体７００は、径方向外側へ拡がるよう、すなわち、内径が拡大するようにして変形する。さらに、作動油が遅角供給凹部ＨＲｓ側から遅角供給開口部ＯＲｓ側へ流れる場合、遅角供給チェック弁７１の弁本体７００の内周壁が作動油により径方向外側へ押され、弁本体７００の外周壁が遅角供給開口部ＯＲｓおよび遅角環状溝部５１１の底面５５０に当接する。これにより、遅角供給凹部ＨＲｓ側から遅角供給開口部ＯＲｓ側への作動油の流れが規制される。ここで、遅角環状溝部５１１の底面５５０は、「弁座面」に対応している。 When the flow rate of the hydraulic oil flowing through the retard angle supply oil passage RRs becomes equal to or less than a predetermined value, the valve body 700 of the retard angle supply check valve 71 is deformed so as to expand outward in the radial direction, that is, to expand the inner diameter. Further, when the hydraulic oil flows from the retarded angle supply recess HRs side to the retarded angle supply opening ORs side, the inner peripheral wall of the valve body 700 of the retarded angle supply check valve 71 is pushed outward in the radial direction by the hydraulic oil, and the valve body 700. The outer peripheral wall of the is abutted against the retarded angle supply openings ORs and the bottom surface 550 of the retarded annular groove 511. As a result, the flow of hydraulic oil from the retard angle supply recess HRs side to the retard angle supply opening ORs side is restricted. Here, the bottom surface 550 of the retarded annular groove portion 511 corresponds to the "valve seat surface".

このように、遅角供給チェック弁７１は、逆止弁として機能し、遅角供給開口部ＯＲｓ側から遅角供給凹部ＨＲｓ側への作動油の流れを許容し、遅角供給凹部ＨＲｓ側から遅角供給開口部ＯＲｓ側への作動油の流れを規制可能である。 In this way, the retard angle supply check valve 71 functions as a check valve, allows the flow of hydraulic oil from the retard angle supply opening ORs side to the retard angle supply recess HRs side, and allows the hydraulic oil to flow from the retard angle supply recess HRs side. It is possible to regulate the flow of hydraulic oil to the retarded angle supply opening ORs side.

進角供給チェック弁７２は、遅角供給チェック弁７１と同様、弁本体７００を有している。進角供給チェック弁７２の弁本体７００の構成は、遅角供給チェック弁７１の弁本体７００の構成と同様である（図６参照）。 The advance angle supply check valve 72 has a valve body 700 like the retard angle supply check valve 71. The configuration of the valve body 700 of the advance check valve 72 is the same as the configuration of the valve body 700 of the check valve 71 (see FIG. 6).

進角供給チェック弁７２は、弁本体７００の周方向が進角環状溝部５１２の底面５５０の周方向に沿うよう進角環状溝部５１２に設けられ、進角供給開口部ＯＡｓを経由してインナースリーブ５０の内側へ向かう作動油の流れを許容し、インナースリーブ５０の内側から進角供給開口部ＯＡｓへ向かう作動油の流れを規制可能である。 The advance angle supply check valve 72 is provided in the advance angle annular groove portion 512 so that the circumferential direction of the valve body 700 is along the circumferential direction of the bottom surface 550 of the advance angle annular groove portion 512, and the inner sleeve is provided via the advance angle supply opening OAs. It is possible to allow the flow of hydraulic oil toward the inside of the inner sleeve 50 and regulate the flow of hydraulic oil from the inside of the inner sleeve 50 toward the advance angle supply opening OAs.

より具体的には、作動油が進角供給油路ＲＡｓにおいて進角供給開口部ＯＡｓ側から進角供給凹部ＨＡｓ側へ流れるとき、進角供給チェック弁７２の弁本体７００は、外周壁が作動油により押され径方向内側へ縮まるよう、すなわち、内径が縮小するようにして変形する。これにより、進角供給チェック弁７２の弁本体７００の外周壁が進角供給開口部ＯＡｓおよび進角環状溝部５１２の底面５５０から離間し、作動油は、進角供給チェック弁７２を経由して進角供給凹部ＨＡｓ側へ流れることができる。このとき、弁本体７００は、両端部の重なり範囲の長さを拡大しながら一部が重なった状態を維持している。 More specifically, when the hydraulic oil flows from the advance angle supply opening OAs side to the advance angle supply recess HAs side in the advance angle supply oil passage RAs, the outer peripheral wall of the valve body 700 of the advance angle supply check valve 72 operates. It is deformed so that it is pushed by oil and shrinks inward in the radial direction, that is, the inner diameter shrinks. As a result, the outer peripheral wall of the valve body 700 of the advance angle supply check valve 72 is separated from the advance angle supply opening OAs and the bottom surface 550 of the advance angle annular groove portion 512, and the hydraulic oil passes through the advance angle supply check valve 72. It can flow to the lead angle supply recess HAs side. At this time, the valve body 700 maintains a partially overlapped state while expanding the length of the overlapping range at both ends.

進角供給油路ＲＡｓを流れる作動油の流量が所定値以下になると、進角供給チェック弁７２の弁本体７００は、径方向外側へ拡がるよう、すなわち、内径が拡大するようにして変形する。さらに、作動油が進角供給凹部ＨＡｓ側から進角供給開口部ＯＡｓ側へ流れる場合、進角供給チェック弁７２の弁本体７００の内周壁が作動油により径方向外側へ押され、弁本体７００の外周壁が進角供給開口部ＯＡｓおよび進角環状溝部５１２の底面５５０に当接する。これにより、進角供給凹部ＨＡｓ側から進角供給開口部ＯＡｓ側への作動油の流れが規制される。ここで、進角環状溝部５１２の底面５５０は、「弁座面」に対応している。 When the flow rate of the hydraulic oil flowing through the advance angle supply oil passage RAs becomes equal to or less than a predetermined value, the valve body 700 of the advance angle supply check valve 72 is deformed so as to expand outward in the radial direction, that is, to increase the inner diameter. Further, when the hydraulic oil flows from the advance angle supply recess HAs side to the advance angle supply opening OAs side, the inner peripheral wall of the valve body 700 of the advance angle supply check valve 72 is pushed outward in the radial direction by the hydraulic oil, and the valve body 700. The outer peripheral wall of the above abuts the advance angle supply opening OAs and the bottom surface 550 of the advance angle annular groove portion 512. As a result, the flow of hydraulic oil from the advance angle supply recess HAs side to the advance angle supply opening OAs side is regulated. Here, the bottom surface 550 of the advance angle annular groove portion 512 corresponds to the "valve seat surface".

このように、進角供給チェック弁７２は、逆止弁として機能し、進角供給開口部ＯＡｓ側から進角供給凹部ＨＡｓ側への作動油の流れを許容し、進角供給凹部ＨＡｓ側から進角供給開口部ＯＡｓ側への作動油の流れを規制可能である。 In this way, the advance angle supply check valve 72 functions as a check valve, allows the flow of hydraulic oil from the advance angle supply opening OAs side to the advance angle supply recess HAs side, and allows the flow of hydraulic oil from the advance angle supply recess HAs side. The flow of hydraulic oil to the advance supply opening OAs side can be regulated.

次に、「チェック弁」としての遅角供給チェック弁７１の構成等について、詳細に説明する。図５〜７に示すように、遅角供給チェック弁７１は、幅狭部７１０、幅広部７２１、幅広部７２２、弁穴部７３１、弁穴部７３２を有している。幅狭部７１０は、弁本体７００の周方向の一部である中央に形成されている。幅広部７２１は、弁本体７００の幅狭部７１０以外の部位である弁本体７００の周方向の一方の端部に形成されている。幅広部７２２は、弁本体７００の幅狭部７１０以外の部位である弁本体７００の周方向の他方の端部に形成されている。幅広部７２１および幅広部７２２は、弁本体７００の軸方向の長さである幅ｗ２が幅狭部７１０の幅ｗ１より大きい（図６、７参照）。なお、幅広部７２１と幅広部７２２とは、遅角供給チェック弁７１が遅角環状溝部５１１に設けられた状態において、互いに弁本体７００の周方向で重なっている（図４、５参照）。ここで、幅広部７２１は、幅広部７２２に対し径方向外側に位置している。 Next, the configuration of the retarded angle supply check valve 71 as the "check valve" and the like will be described in detail. As shown in FIGS. 5 to 7, the check valve 71 having a retard angle supply has a narrow portion 710, a wide portion 721, a wide portion 722, a valve hole portion 731, and a valve hole portion 732. The narrow portion 710 is formed in the center, which is a part of the valve body 700 in the circumferential direction. The wide portion 721 is formed at one end in the circumferential direction of the valve body 700, which is a portion other than the narrow portion 710 of the valve body 700. The wide portion 722 is formed at the other end of the valve body 700 in the circumferential direction, which is a portion other than the narrow portion 710 of the valve body 700. In the wide portion 721 and the wide portion 722, the width w2, which is the axial length of the valve body 700, is larger than the width w1 of the narrow portion 710 (see FIGS. 6 and 7). The wide portion 721 and the wide portion 722 overlap each other in the circumferential direction of the valve body 700 in a state where the check valve 71 is provided in the retard annular groove portion 511 (see FIGS. 4 and 5). Here, the wide portion 721 is located radially outward with respect to the wide portion 722.

弁穴部７３１は、幅広部７２１を板厚方向に貫くよう形成されている。弁穴部７３２は、幅広部７２２を板厚方向に貫くよう形成されている。弁穴部７３１、弁穴部７３２は、いずれも、弁本体７００の周方向に延びる長穴状に形成されている。弁穴部７３１と弁穴部７３２とは、遅角供給チェック弁７１が遅角環状溝部５１１に設けられた状態において、互いに少なくとも一部が弁本体７００の周方向で重なっている（図４、５参照）。 The valve hole portion 731 is formed so as to penetrate the wide portion 721 in the plate thickness direction. The valve hole portion 732 is formed so as to penetrate the wide portion 722 in the plate thickness direction. Both the valve hole portion 731 and the valve hole portion 732 are formed in an elongated hole shape extending in the circumferential direction of the valve body 700. At least a part of the valve hole portion 731 and the valve hole portion 732 overlap each other in the circumferential direction of the valve body 700 in a state where the check valve 71 is provided in the retarded annular groove portion 511 (FIG. 4, FIG. 5).

図４に示すように、回転規制部９０は、インナースリーブ５０に設けられている。回転規制部９０は、例えば金属により形成され、規制突起部９１、鍔部９２を有している。規制突起部９１は、略円柱状に形成されている。鍔部９２は、規制突起部９１の一方の端部から径方向外側へ環状に延びるよう形成されている。 As shown in FIG. 4, the rotation restricting portion 90 is provided on the inner sleeve 50. The rotation regulating portion 90 is formed of, for example, metal, and has a regulating protrusion 91 and a flange portion 92. The regulation protrusion 91 is formed in a substantially columnar shape. The flange portion 92 is formed so as to extend radially outward from one end of the regulation protrusion 91 in an annular shape.

インナースリーブ５０には、規制穴部９３が形成されている。規制穴部９３は、遅角供給開口部ＯＲｓと同様、インナースリーブ５０の遅角環状溝部５１１の底面５５０と、インナースリーブ５０の外壁５３のうち筒状空間Ｓｔ１の端部に対応する外壁である遅角外壁５３１とを連通するよう形成されている。ここで、規制穴部９３は、遅角環状溝部５１１の周方向の一部において等間隔（４５度）で５つ並ぶ遅角供給開口部ＯＲｓのうち３番目のものに対し、インナースリーブ５０の軸を挟んで反対側に形成されている。 A regulation hole 93 is formed in the inner sleeve 50. Similar to the retard angle supply opening ORs, the regulation hole portion 93 is an outer wall corresponding to the bottom surface 550 of the retard angle annular groove portion 511 of the inner sleeve 50 and the end portion of the tubular space St1 of the outer wall 53 of the inner sleeve 50. It is formed so as to communicate with the retarded outer wall 531. Here, the regulation hole portion 93 is the inner sleeve 50 with respect to the third of the five retard angle supply openings ORs arranged at equal intervals (45 degrees) in a part of the circumferential direction of the retard angle annular groove portion 511. It is formed on the opposite side of the shaft.

規制穴部９３の内径は、規制突起部９１の外径よりやや大きい。また、弁穴部７３１および弁穴部７３２の短手方向の大きさは規制突起部９１の外径よりやや大きく、弁穴部７３１および弁穴部７３２の長手方向の大きさは規制突起部９１の外径より十分大きい。回転規制部９０は、規制突起部９１が規制穴部９３の内側に位置し、鍔部９２がインナースリーブ５０の外側に位置するようインナースリーブ５０に設けられている。ここで、規制突起部９１は、遅角供給チェック弁７１の弁穴部７３１および弁穴部７３２を通るよう遅角環状溝部５１１の底面５５０からインナースリーブ５０の径方向内側へ延びている。そのため、弁本体７００は、弁穴部７３１または弁穴部７３２が規制突起部９１に係止されることにより、遅角環状溝部５１１の周方向における回転位置が規制される。つまり、弁本体７００は、遅角環状溝部５１１の周方向において、弁穴部７３１または弁穴部７３２が規制突起部９１により係止される範囲で回転可能である。また、弁本体７００は、開弁時、両端部（幅広部７２１、幅広部７２２）の重なり面積を拡大させながら縮径する。ここで、弁穴部７３１および弁穴部７３２のそれぞれの端部が規制突起部９１に係止されると、弁本体７００の縮径が規制される。 The inner diameter of the regulation hole 93 is slightly larger than the outer diameter of the regulation protrusion 91. Further, the size of the valve hole portion 731 and the valve hole portion 732 in the lateral direction is slightly larger than the outer diameter of the regulation protrusion portion 91, and the size of the valve hole portion 731 and the valve hole portion 732 in the longitudinal direction is the regulation protrusion portion 91. It is sufficiently larger than the outer diameter of. The rotation regulating portion 90 is provided on the inner sleeve 50 so that the regulating protrusion 91 is located inside the regulating hole portion 93 and the flange portion 92 is located outside the inner sleeve 50. Here, the regulation protrusion 91 extends radially inward from the bottom surface 550 of the retard annular groove portion 511 so as to pass through the valve hole portion 731 and the valve hole portion 732 of the retard angle supply check valve 71. Therefore, in the valve body 700, the valve hole portion 731 or the valve hole portion 732 is locked to the regulation protrusion 91, so that the rotational position of the retarded annular groove portion 511 in the circumferential direction is restricted. That is, the valve body 700 can rotate in the circumferential direction of the retarded annular groove portion 511 within a range in which the valve hole portion 731 or the valve hole portion 732 is locked by the regulation protrusion 91. Further, when the valve is opened, the valve body 700 is reduced in diameter while expanding the overlapping area of both end portions (wide portion 721 and wide portion 722). Here, when the respective ends of the valve hole portion 731 and the valve hole portion 732 are locked to the regulation protrusion 91, the diameter reduction of the valve body 700 is regulated.

上述のように、回転規制部９０は、遅角環状溝部５１１の周方向における遅角供給チェック弁７１の弁本体７００の回転位置を所定範囲内に規制可能である。より具体的には、回転規制部９０は、幅広部７２１、幅広部７２２の少なくとも一部が、遅角環状溝部５１１の周方向において隣り合う遅角供給開口部ＯＲｓ間の距離のうち最大距離となる区間である最大距離区間Ｓｂｄ内に位置するよう弁本体７００の回転位置を規制する（図４参照）。そのため、遅角環状溝部５１１の周方向の特定の部位に偏って配置された遅角供給開口部ＯＲｓからインナースリーブ５０の内側へ作動油が流入すると、弁本体７００は、径が縮小して開弁するとともに、幅広部７２１、幅広部７２２が遅角環状溝部５１１の底面５５０のうち最大距離区間Ｓｂｄに対応する部位に押し付けられる（図９参照）。これにより、遅角環状溝部５１１の内側における遅角供給チェック弁７１の振れ回りを抑制するとともに、幅広部７２１、幅広部７２２が遅角環状溝部５１１から径方向内側すなわち内周壁５４側へ飛び出るのを抑制できる。そのため、遅角供給チェック弁７１の閉弁時に幅広部７２１、幅広部７２２がインナースリーブ５０の内周壁５４と遅角環状溝部５１１との角部に衝突するのを抑制できる。なお、ベーンロータ３０の中央部に設けられた弁装置１１は、エンジン１の運転中、高速で回転するため、遅角供給チェック弁７１の開弁時、弁本体７００は、遠心力によっても、遅角環状溝部５１１の底面５５０のうち最大距離区間Ｓｂｄに対応する部位側に押し付けられた状態が維持される。 As described above, the rotation restricting unit 90 can regulate the rotation position of the valve body 700 of the retard angle supply check valve 71 in the circumferential direction of the retard angle annular groove portion 511 within a predetermined range. More specifically, in the rotation regulating unit 90, at least a part of the wide portion 721 and the wide portion 722 is the maximum distance among the distances between the retard angle supply openings ORs adjacent to each other in the circumferential direction of the retard angle annular groove portion 511. The rotation position of the valve body 700 is regulated so as to be located within the maximum distance section Sbd which is the section (see FIG. 4). Therefore, when the hydraulic oil flows into the inner sleeve 50 from the retarded angle supply openings ORs arranged unevenly in a specific portion in the circumferential direction of the retarded angle annular groove portion 511, the diameter of the valve body 700 is reduced and opened. Along with the valve, the wide portion 721 and the wide portion 722 are pressed against the portion of the bottom surface 550 of the retarded annular groove portion 511 corresponding to the maximum distance section Sbd (see FIG. 9). As a result, the swing of the retard supply check valve 71 inside the retarded annular groove portion 511 is suppressed, and the wide portion 721 and the wide portion 722 protrude from the retarded annular groove portion 511 in the radial direction, that is, toward the inner peripheral wall 54 side. Can be suppressed. Therefore, it is possible to prevent the wide portion 721 and the wide portion 722 from colliding with the corner portion between the inner peripheral wall 54 of the inner sleeve 50 and the retarded annular groove portion 511 when the check valve 71 is closed. Since the valve device 11 provided at the center of the vane rotor 30 rotates at a high speed during the operation of the engine 1, when the retard angle supply check valve 71 is opened, the valve body 700 is delayed due to centrifugal force. The state of being pressed against the portion of the bottom surface 550 of the angular annular groove portion 511 corresponding to the maximum distance section Sbd is maintained.

進角供給チェック弁７２も、遅角供給チェック弁７１と同様の構成であり、弁本体７００には、幅狭部７１０、幅広部７２１、幅広部７２２、弁穴部７３１、弁穴部７３２が形成されている（図示せず）。また、進角環状溝部５１２にも、遅角環状溝部５１１と同様、回転規制部９０が設けられている（図示せず）。この回転規制部９０は、進角環状溝部５１２の周方向における進角供給チェック弁７２の弁本体７００の回転位置を所定範囲内に規制可能である。具体的な規制範囲は、遅角環状溝部５１１に設けられた回転規制部９０と同様のため、説明を省略する。 The advance angle supply check valve 72 has the same configuration as the retard angle supply check valve 71, and the valve body 700 includes a narrow portion 710, a wide portion 721, a wide portion 722, a valve hole portion 731, and a valve hole portion 732. It is formed (not shown). Further, the advance angle annular groove portion 512 is also provided with the rotation restricting portion 90 (not shown) as in the retard angle annular groove portion 511. The rotation regulating unit 90 can regulate the rotation position of the valve body 700 of the advance angle supply check valve 72 in the circumferential direction of the advance angle annular groove portion 512 within a predetermined range. Since the specific regulation range is the same as that of the rotation regulation portion 90 provided in the retarded annular groove portion 511, the description thereof will be omitted.

次に、比較形態による弁装置のチェック弁を示すことにより、比較形態に対する本実施形態の優位な点を明らかにする。図８に示すように、比較形態による遅角供給チェック弁７１は、幅狭部７１０、幅狭部７１１、幅狭部７１２、幅広部７２１、幅広部７２２、弁穴部７３１、弁穴部７３２を有している。幅狭部７１０は、弁本体７００の周方向の一部である中央に形成されている。幅狭部７１１は、弁本体７００の周方向の一方の端部に形成されている。幅狭部７１２は、弁本体７００の周方向の他方の端部に形成されている。幅広部７２１は、弁本体７００の幅狭部７１０、幅狭部７１１、幅狭部７１２以外の部位である幅狭部７１０と幅狭部７１１との間に形成されている。幅広部７２２は、弁本体７００の幅狭部７１０、幅狭部７１１、幅狭部７１２以外の部位である幅狭部７１０と幅狭部７１２との間に形成されている。弁穴部７３１は、幅狭部７１１を板厚方向に貫くよう形成されている。弁穴部７３２は、幅狭部７１２を板厚方向に貫くよう形成されている。 Next, by showing the check valve of the valve device according to the comparative embodiment, the advantages of the present embodiment over the comparative embodiment will be clarified. As shown in FIG. 8, the check valve 71 according to the comparative form has a narrow portion 710, a narrow portion 711, a narrow portion 712, a wide portion 721, a wide portion 722, a valve hole portion 731, and a valve hole portion 732. have. The narrow portion 710 is formed in the center, which is a part of the valve body 700 in the circumferential direction. The narrow portion 711 is formed at one end of the valve body 700 in the circumferential direction. The narrow portion 712 is formed at the other end of the valve body 700 in the circumferential direction. The wide portion 721 is formed between the narrow portion 710 and the narrow portion 711, which are portions other than the narrow portion 710, the narrow portion 711, and the narrow portion 712 of the valve body 700. The wide portion 722 is formed between the narrow portion 710 and the narrow portion 712, which are portions other than the narrow portion 710, the narrow portion 711, and the narrow portion 712 of the valve body 700. The valve hole portion 731 is formed so as to penetrate the narrow portion 711 in the plate thickness direction. The valve hole portion 732 is formed so as to penetrate the narrow portion 712 in the plate thickness direction.

比較形態において、幅広部７２１および幅広部７２２は、弁本体７００の軸方向の長さである幅ｗ４が幅狭部７１０、幅狭部７１１、幅狭部７１２の幅ｗ３より大きい（図８参照）。ここで、比較形態において、弁穴部７３１、弁穴部７３２が形成された幅狭部７１１、幅狭部７１２の剛性を、本実施形態の弁穴部７３１、弁穴部７３２が形成された幅広部７２１、幅広部７２２の剛性と同程度に確保する場合、幅狭部７１０、幅狭部７１１、幅狭部７１２の幅ｗ３を、本実施形態の幅広部７２１、幅広部７２２の幅ｗ２（図６、７参照）と同じにする必要がある。そうすると、比較形態の幅広部７２１、幅広部７２２の幅ｗ４は、本実施形態の幅広部７２１、幅広部７２２の幅ｗ２より大きくなる。そのため、比較形態の弁本体７００の軸方向の長さ（幅ｗ４）が大きくなるおそれがある。 In the comparative form, in the wide portion 721 and the wide portion 722, the width w4, which is the axial length of the valve body 700, is larger than the width w3 of the narrow portion 710, the narrow portion 711, and the narrow portion 712 (see FIG. 8). ). Here, in the comparative embodiment, the valve hole portion 731 and the valve hole portion 732 of the present embodiment are formed with the rigidity of the narrow portion 711 and the narrow portion 712 in which the valve hole portion 731 is formed. When ensuring the same degree of rigidity as the wide portion 721 and the wide portion 722, the width w3 of the narrow portion 710, the narrow portion 711, and the narrow portion 712 is set to the width w2 of the wide portion 721 and the wide portion 722 of the present embodiment. It should be the same as (see FIGS. 6 and 7). Then, the width w4 of the wide portion 721 and the wide portion 722 of the comparative embodiment becomes larger than the width w2 of the wide portion 721 and the wide portion 722 of the present embodiment. Therefore, the axial length (width w4) of the valve body 700 in the comparative form may increase.

一方、本実施形態では、弁穴部７３１、弁穴部７３２が幅広部７２１、幅広部７２２に形成されているため（図６、７参照）、幅広部７２１、幅広部７２２の剛性を確保しつつ、弁本体７００の軸方向の長さ（幅ｗ２）を小さくすることができる。 On the other hand, in the present embodiment, since the valve hole portion 731 and the valve hole portion 732 are formed in the wide portion 721 and the wide portion 722 (see FIGS. 6 and 7), the rigidity of the wide portion 721 and the wide portion 722 is ensured. At the same time, the axial length (width w2) of the valve body 700 can be reduced.

スプール６０のカム軸３とは反対側には、リニアソレノイド９が設けられる。リニアソレノイド９は、スプール封止部６２に当接するようにして設けられる。リニアソレノイド９は、通電により、スプール封止部６２を介してスプール６０をスプリング６３の付勢力に抗してカム軸３側へ押圧する。これにより、スプール６０は、ストローク区間においてスリーブ４００に対する軸方向の位置が変化する。 A linear solenoid 9 is provided on the side of the spool 60 opposite to the cam shaft 3. The linear solenoid 9 is provided so as to come into contact with the spool sealing portion 62. When energized, the linear solenoid 9 presses the spool 60 toward the cam shaft 3 side against the urging force of the spring 63 via the spool sealing portion 62. As a result, the position of the spool 60 in the axial direction with respect to the sleeve 400 changes in the stroke section.

容積可変空間Ｓｖは、遅角ドレン油路ＲＲｄおよび進角ドレン油路ＲＡｄに連通している。そのため、容積可変空間Ｓｖは、遅角ドレン油路ＲＲｄおよび進角ドレン油路ＲＡｄのドレン開口部Ｏｄ２を経由して大気に開放されている。これにより、容積可変空間Ｓｖの圧力を大気圧と同等にすることができる。そのため、スプール６０の軸方向の移動を円滑にすることができる。 The variable volume space Sv communicates with the retard angle drain oil passage RRd and the advance angle drain oil passage RAd. Therefore, the variable volume space Sv is open to the atmosphere via the drain opening Od2 of the retard angle drain oil passage RRd and the advance angle drain oil passage RAd. Thereby, the pressure of the volume variable space Sv can be made equal to the atmospheric pressure. Therefore, the spool 60 can be smoothly moved in the axial direction.

本実施形態は、ロックピン３３をさらに備えている（図１、２参照）。ロックピン３３は、有底円筒状に形成され、ベーン３２に形成された収容穴部３２１に軸方向に往復移動可能に収容されている。ロックピン３３の内側には、スプリング３４が設けられている。スプリング３４は、ロックピン３３をケース２２の板部２２２側へ付勢している。ケース２２の板部２２２のベーン３２側には、嵌入凹部２５が形成されている。 The present embodiment further includes a lock pin 33 (see FIGS. 1 and 2). The lock pin 33 is formed in a bottomed cylindrical shape, and is housed in a housing hole portion 321 formed in the vane 32 so as to be reciprocally movable in the axial direction. A spring 34 is provided inside the lock pin 33. The spring 34 urges the lock pin 33 toward the plate portion 222 side of the case 22. A fitting recess 25 is formed on the vane 32 side of the plate portion 222 of the case 22.

ロックピン３３は、ハウジング２０に対しベーンロータ３０が最遅角位置にあるとき、嵌入凹部２５に嵌入可能である。ロックピン３３が嵌入凹部２５に嵌入しているとき、ハウジング２０に対するベーンロータ３０の相対回転が規制される。一方、ロックピン３３が嵌入凹部２５に嵌入していないとき、ハウジング２０に対するベーンロータ３０の相対回転が許容される。 The lock pin 33 can be fitted into the fitting recess 25 when the vane rotor 30 is at the most retarded position with respect to the housing 20. When the lock pin 33 is fitted in the fitting recess 25, the relative rotation of the vane rotor 30 with respect to the housing 20 is restricted. On the other hand, when the lock pin 33 is not fitted in the fitting recess 25, the relative rotation of the vane rotor 30 with respect to the housing 20 is allowed.

ベーン３２のロックピン３３と進角室２０２との間には、進角室２０２に連通するピン制御油路３０４が形成されている（図２参照）。進角室２０２からピン制御油路３０４に流入する作動油の圧力は、ロックピン３３がスプリング３４の付勢力に抗して嵌入凹部２５から抜け出す方向に働く。 A pin control oil passage 304 communicating with the advance chamber 202 is formed between the lock pin 33 of the vane 32 and the advance chamber 202 (see FIG. 2). The pressure of the hydraulic oil flowing from the advance chamber 202 into the pin control oil passage 304 acts in the direction in which the lock pin 33 escapes from the fitting recess 25 against the urging force of the spring 34.

以上のように構成されたバルブタイミング調整装置１０では、進角室２０２に作動油が供給されると、ピン制御油路３０４に作動油が流入し、ロックピン３３が嵌入凹部２５から抜け出し、ハウジング２０に対するベーンロータ３０の相対回転が許容された状態となる。 In the valve timing adjusting device 10 configured as described above, when the hydraulic oil is supplied to the advance chamber 202, the hydraulic oil flows into the pin control oil passage 304, the lock pin 33 comes out of the fitting recess 25, and the housing The relative rotation of the vane rotor 30 with respect to 20 is allowed.

次に、バルブタイミング調整装置１０の作動について説明する。バルブタイミング調整装置１０は、リニアソレノイド９の駆動により弁装置１１のスプール６０を押圧し、弁装置１１を、オイルポンプ８と遅角室２０１とを接続しつつ進角室２０２とオイルパン７とを接続する第１作動状態と、オイルポンプ８と進角室２０２とを接続しつつ遅角室２０１とオイルパン７とを接続する第２作動状態と、オイルポンプ８と遅角室２０１および進角室２０２とを接続しつつ遅角室２０１および進角室２０２とオイルパン７との間を遮断し位相変換部ＰＣの位相を保持する位相保持状態と、に作動させる。 Next, the operation of the valve timing adjusting device 10 will be described. The valve timing adjusting device 10 presses the spool 60 of the valve device 11 by driving the linear solenoid 9, and connects the valve device 11 to the advance chamber 202 and the oil pan 7 while connecting the oil pump 8 and the retard chamber 201. The first operating state for connecting the oil pump 8 and the advance chamber 202, and the second operating state for connecting the retard chamber 201 and the oil pan 7 while connecting the oil pump 8 and the advance chamber 202, and the oil pump 8 and the retard chamber 201 and the advance. While connecting to the corner chamber 202, the retard chamber 201, the advance chamber 202, and the oil pan 7 are cut off from each other to maintain the phase of the phase conversion unit PC.

第１作動状態では、遅角供給油路ＲＲｓを経由して遅角室２０１に作動油が供給されつつ、進角ドレン油路ＲＡｄを経由して進角室２０２から作動油がオイルパン７に戻される。第２作動状態では、進角供給油路ＲＡｓを経由して進角室２０２に作動油が供給されつつ、遅角ドレン油路ＲＲｄを経由して遅角室２０１から作動油がオイルパン７に戻される。位相保持状態では、遅角供給油路ＲＲｓおよび進角供給油路ＲＡｓを経由して遅角室２０１および進角室２０２に作動油が供給されつつ、遅角室２０１および進角室２０２の作動油の排出が規制される。 In the first operating state, the hydraulic oil is supplied to the retard chamber 201 via the retard supply oil passage RRs, and the hydraulic oil is supplied to the oil pan 7 from the advance chamber 202 via the advance drain oil passage RAd. Returned. In the second operating state, the hydraulic oil is supplied to the advance chamber 202 via the advance feed oil passage RAs, and the hydraulic oil is supplied to the oil pan 7 from the retard chamber 201 via the retard drain oil passage RRd. Returned. In the phase holding state, the retard chamber 201 and the advance chamber 202 are operated while hydraulic oil is supplied to the retard chamber 201 and the advance chamber 202 via the retard supply oil passage RRs and the advance supply oil passage RAs. Oil emissions are regulated.

バルブタイミング調整装置１０は、カム軸３の回転位相が目標値よりも進角側である場合、弁装置１１を第１作動状態とする。これにより、ベーンロータ３０がハウジング２０に対して遅角方向へ相対回転し、カム軸３の回転位相が遅角側へ変化する。 When the rotation phase of the cam shaft 3 is on the advance angle side of the target value, the valve timing adjusting device 10 puts the valve device 11 in the first operating state. As a result, the vane rotor 30 rotates relative to the housing 20 in the retard direction, and the rotation phase of the cam shaft 3 changes to the retard side.

また、バルブタイミング調整装置１０は、カム軸３の回転位相が目標値よりも遅角側である場合、弁装置１１を第２作動状態とする。これにより、ベーンロータ３０がハウジング２０に対して進角方向へ相対回転し、カム軸３の回転位相が進角側へ変化する。 Further, the valve timing adjusting device 10 puts the valve device 11 in the second operating state when the rotation phase of the cam shaft 3 is on the retard side of the target value. As a result, the vane rotor 30 rotates relative to the housing 20 in the advance angle direction, and the rotation phase of the cam shaft 3 changes to the advance angle side.

また、バルブタイミング調整装置１０は、カム軸３の回転位相が目標値と一致する場合、弁装置１１を位相保持状態とする。これにより、カム軸３の回転位相が保持される。 Further, the valve timing adjusting device 10 puts the valve device 11 in the phase holding state when the rotation phase of the cam shaft 3 matches the target value. As a result, the rotation phase of the cam shaft 3 is maintained.

以上説明したように、＜１＞本実施形態による弁装置１１は、筒部材としてのインナースリーブ５０とチェック弁としての遅角供給チェック弁７１および進角供給チェック弁７２と回転規制部９０とを備えている。インナースリーブ５０は、内周壁５４から径方向外側へ凹みつつ周方向に延びて環状に形成された環状溝部５５としての遅角環状溝部５１１および進角環状溝部５１２、ならびに、遅角環状溝部５１１、進角環状溝部５１２の周方向に不等間隔で複数形成され遅角環状溝部５１１、進角環状溝部５１２の底面５５０と外壁５３とを連通する流入穴としての遅角供給開口部ＯＲｓ、進角供給開口部ＯＡｓを有している。遅角供給チェック弁７１、進角供給チェック弁７２は、単一の板材を長手方向が周方向に沿うよう巻くことにより筒状に形成された弁本体７００を有し、弁本体７００の周方向が遅角環状溝部５１１、進角環状溝部５１２の底面５５０の周方向に沿うよう遅角環状溝部５１１、進角環状溝部５１２に設けられ、遅角供給開口部ＯＲｓ、進角供給開口部ＯＡｓを経由してインナースリーブ５０の内側へ向かう作動油の流れを許容し、インナースリーブ５０の内側から遅角供給開口部ＯＲｓ、進角供給開口部ＯＡｓへ向かう作動油の流れを規制可能である。回転規制部９０は、遅角環状溝部５１１、進角環状溝部５１２の周方向における弁本体７００の回転位置を所定範囲内に規制可能である。 As described above, <1> The valve device 11 according to the present embodiment includes an inner sleeve 50 as a tubular member, a check valve 71 as a check valve, an advance check valve 72, and a rotation control unit 90. I have. The inner sleeve 50 includes a retarded annular groove 511 and an advance annular groove 512 as an annular groove 55 formed in an annular direction while being recessed radially outward from the inner peripheral wall 54, and a retarded annular groove 511. A plurality of retarded annular grooves 511 formed at irregular intervals in the circumferential direction of the advanced annular groove 512, retarded supply openings ORs as inflow holes communicating the bottom surface 550 of the advanced annular groove 512 and the outer wall 53, and advance angles. It has a supply opening OAs. The retard angle supply check valve 71 and the advance angle supply check valve 72 have a valve body 700 formed in a tubular shape by winding a single plate material so that the longitudinal direction is along the circumferential direction, and the valve body 700 has a circumferential direction. Are provided in the retarded annular groove 511 and the advanced annular groove 512 so as to follow the circumferential direction of the bottom surface 550 of the retarded annular groove 511 and the advance annular groove 512, and provide the retard supply opening ORs and the advance supply opening OAs. It is possible to allow the flow of hydraulic oil toward the inside of the inner sleeve 50 via the inner sleeve 50, and regulate the flow of hydraulic oil from the inside of the inner sleeve 50 toward the retard angle supply opening ORs and the advance angle supply opening OAs. The rotation regulating unit 90 can regulate the rotation position of the valve body 700 in the circumferential direction of the retarded annular groove portion 511 and the advancing annular groove portion 512 within a predetermined range.

遅角供給チェック弁７１、進角供給チェック弁７２は、それぞれ、弁本体７００の周方向の一部に形成された幅狭部７１０、および、弁本体７００の周方向の幅狭部７１０以外の部位に形成され弁本体７００の軸方向の長さである幅ｗ２が幅狭部７１０の幅ｗ１より大きい幅広部７２１、幅広部７２２を有している。回転規制部９０は、幅広部７２１、幅広部７２２の少なくとも一部が、遅角環状溝部５１１、進角環状溝部５１２の周方向において隣り合う遅角供給開口部ＯＲｓ、進角供給開口部ＯＡｓ間の距離のうち最大距離となる区間である最大距離区間Ｓｂｄ内に位置するよう弁本体７００の回転位置を規制する。 The retard angle supply check valve 71 and the advance angle supply check valve 72 are other than the narrow portion 710 formed in a part of the valve body 700 in the circumferential direction and the narrow portion 710 in the circumferential direction of the valve body 700, respectively. It has a wide portion 721 and a wide portion 722 in which the width w2 formed at the portion and which is the axial length of the valve body 700 is larger than the width w1 of the narrow portion 710. In the rotation regulating portion 90, at least a part of the wide portion 721 and the wide portion 722 is between the retard angle supply opening ORs and the advance angle supply opening OAs, which are adjacent to each other in the circumferential direction of the retard angle annular groove portion 511 and the advance angle annular groove portion 512. The rotation position of the valve body 700 is regulated so as to be located within the maximum distance section Sbd, which is the section that is the maximum distance among the distances of.

作動油が遅角供給開口部ＯＲｓ、進角供給開口部ＯＡｓを経由してインナースリーブ５０の内側へ向かうとき、遅角供給チェック弁７１、進角供給チェック弁７２は、外周壁が作動油により押され、縮径しつつ開弁する。ここで、遅角供給開口部ＯＲｓ、進角供給開口部ＯＡｓは遅角環状溝部５１１、進角環状溝部５１２の周方向に不等間隔で複数形成され、回転規制部９０は幅広部７２１、幅広部７２２の少なくとも一部が最大距離区間Ｓｂｄ内に位置するよう弁本体７００の回転位置を規制するため、遅角供給チェック弁７１、進角供給チェック弁７２が開弁すると、幅広部７２１、幅広部７２２は、最大距離区間Ｓｂｄにおいて少なくとも一部が遅角環状溝部５１１、進角環状溝部５１２の底面５５０に押し付けられる。これにより、遅角環状溝部５１１、進角環状溝部５１２の内側における遅角供給チェック弁７１、進角供給チェック弁７２の振れ回りを抑制するとともに、幅広部７２１、幅広部７２２が遅角環状溝部５１１、進角環状溝部５１２から径方向内側すなわち内周壁５４側へ飛び出るのを抑制できる。そのため、遅角供給チェック弁７１、進角供給チェック弁７２の閉弁時に幅広部７２１、幅広部７２２がインナースリーブ５０の内周壁５４と遅角環状溝部５１１、進角環状溝部５１２との角部に衝突するのを抑制できる。したがって、遅角供給チェック弁７１、進角供給チェック弁７２とインナースリーブ５０の内周壁５４との衝突による損傷を抑制できる。 When the hydraulic oil goes to the inside of the inner sleeve 50 via the retard angle supply opening ORs and the advance angle supply opening OAs, the outer peripheral walls of the retard angle supply check valve 71 and the advance angle supply check valve 72 are due to the hydraulic oil. It is pushed and the valve is opened while reducing the diameter. Here, a plurality of the retard angle supply opening ORs and the advance angle supply opening OAs are formed at unequal intervals in the circumferential direction of the retard angle annular groove portion 511 and the advance angle annular groove portion 512, and the rotation restricting portion 90 has a wide portion 721 and a wide portion. In order to regulate the rotation position of the valve body 700 so that at least a part of the portion 722 is located within the maximum distance section Sbd, when the retard angle supply check valve 71 and the advance angle supply check valve 72 are opened, the wide portion 721 and the wide portion 721 are wide. At least a part of the portion 722 is pressed against the bottom surface 550 of the retarded annular groove portion 511 and the advanced angle annular groove portion 512 in the maximum distance section Sbd. As a result, the retard angle supply check valve 71 and the advance angle supply check valve 72 inside the retard angle annular groove portion 511 and the advance angle annular groove portion 512 are suppressed from swinging, and the wide portion 721 and the wide portion 722 are formed into the retard angle annular groove portion. 511, it is possible to prevent the advance angle annular groove portion 512 from jumping out in the radial direction, that is, toward the inner peripheral wall 54 side. Therefore, when the check valve 71 for the retard and the check valve 72 for the advance angle are closed, the wide portion 721 and the wide portion 722 are the corner portions of the inner peripheral wall 54 of the inner sleeve 50 and the annular groove portion 511 for the advance angle and the annular groove portion 512 for the advance angle. Can be suppressed from colliding with. Therefore, damage due to the collision between the check valve 71 for the retard angle and the check valve 72 for the advance angle and the inner peripheral wall 54 of the inner sleeve 50 can be suppressed.

また、＜２＞本実施形態では、遅角供給チェック弁７１、進角供給チェック弁７２は、弁本体７００の周方向の一部において弁本体７００を板厚方向に貫くよう形成された弁穴部７３１、弁穴部７３２を有している。回転規制部９０は、弁穴部７３１、弁穴部７３２を通るよう遅角環状溝部５１１、進角環状溝部５１２の底面５５０からインナースリーブ５０の径方向内側へ延びる規制突起部９１を有し、規制突起部９１が弁穴部７３１、弁穴部７３２を係止することにより弁本体７００の回転位置を規制する。そのため、回転規制部９０を、比較的簡単に構成することができる。 <2> In the present embodiment, the check valve 71 for the retard angle and the check valve 72 for the advance angle supply are valve holes formed so as to penetrate the valve body 700 in the plate thickness direction in a part of the circumferential direction of the valve body 700. It has a portion 731 and a valve hole portion 732. The rotation regulating portion 90 has a retarded annular groove portion 511 so as to pass through the valve hole portion 731 and the valve hole portion 732, and a regulating protrusion 91 extending radially inward from the bottom surface 550 of the advancing annular groove portion 512. The regulation protrusion 91 regulates the rotation position of the valve body 700 by locking the valve hole portion 731 and the valve hole portion 732. Therefore, the rotation regulation unit 90 can be relatively easily configured.

また、＜３＞本実施形態では、弁穴部７３１、弁穴部７３２は、幅広部７２１、幅広部７２２に形成されている。そのため、弁穴部７３１、弁穴部７３２が形成された幅広部７２１、幅広部７２２の剛性を確保しつつ、弁本体７００の軸方向の長さを小さくすることができる。 <3> In the present embodiment, the valve hole portion 731 and the valve hole portion 732 are formed in the wide portion 721 and the wide portion 722. Therefore, the axial length of the valve body 700 can be reduced while ensuring the rigidity of the valve hole portion 731, the wide portion 721 in which the valve hole portion 732 is formed, and the wide portion 722.

また、＜４＞本実施形態では、弁穴部７３１は弁本体７００の周方向の一方の端部に形成され、弁穴部７３２は弁本体７００の周方向の他方の端部に形成されている。弁穴部７３１、弁穴部７３２は、いずれも弁本体７００の周方向に延びる長穴状に形成され、互いに少なくとも一部が弁本体７００の周方向で重なる。そのため、弁本体７００は、遅角環状溝部５１１、進角環状溝部５１２の周方向において、弁穴部７３１または弁穴部７３２が規制突起部９１により係止される範囲、すなわち、弁穴部７３１、弁穴部７３２の長手方向の長さの範囲で回転し得る。一方、弁本体７００は、開弁時、遅角環状溝部５１１、進角環状溝部５１２に対し両端が相対移動するよう変形可能なため、開弁作動のバランスを向上することができる。 <4> In the present embodiment, the valve hole portion 731 is formed at one end of the valve body 700 in the circumferential direction, and the valve hole portion 732 is formed at the other end of the valve body 700 in the circumferential direction. There is. Both the valve hole portion 731 and the valve hole portion 732 are formed in an elongated hole shape extending in the circumferential direction of the valve body 700, and at least a part of the valve hole portion 731 and the valve hole portion 732 overlap each other in the circumferential direction of the valve body 700. Therefore, in the valve body 700, the valve hole portion 731 or the valve hole portion 732 is locked by the regulation protrusion 91 in the circumferential direction of the retard angle annular groove portion 511 and the advance angle annular groove portion 512, that is, the valve hole portion 731. , The valve hole portion 732 can rotate within the longitudinal length range. On the other hand, since the valve body 700 can be deformed so that both ends move relative to the retarded annular groove portion 511 and the advance angle annular groove portion 512 when the valve is opened, the balance of the valve opening operation can be improved.

（第２実施形態）
第２実施形態による弁装置のチェック弁を図１０に示す。第２実施形態は、遅角供給チェック弁７１、進角供給チェック弁７２の構成が第１実施形態と異なる。 (Second Embodiment)
The check valve of the valve device according to the second embodiment is shown in FIG. In the second embodiment, the configurations of the check valve 71 for the retard angle supply and the check valve 72 for the advance angle supply are different from those in the first embodiment.

第２実施形態では、弁穴部７３１は、略円形に形成されている。弁穴部７３１の内径は、規制突起部９１の外径よりやや大きい。そのため、弁本体７００は、円形の弁穴部７３１が規制突起部９１により係止されることで、回転が規制される。 In the second embodiment, the valve hole portion 731 is formed in a substantially circular shape. The inner diameter of the valve hole portion 731 is slightly larger than the outer diameter of the regulation protrusion 91. Therefore, the rotation of the valve body 700 is restricted by locking the circular valve hole portion 731 by the regulating protrusion 91.

弁穴部７３２は、弁本体７００の周方向に延びる長穴状に形成されている。そのため、弁本体７００の開閉弁時、幅広部７２２は、幅広部７２１の内側において、弁穴部７３２の長手方向の長さの範囲で幅広部７２１に対し相対移動しながら変形可能である。その他の構成は、第１実施形態と同様である。 The valve hole portion 732 is formed in an elongated hole shape extending in the circumferential direction of the valve body 700. Therefore, at the time of the on-off valve of the valve body 700, the wide portion 722 can be deformed while moving relative to the wide portion 721 within the length range of the valve hole portion 732 in the longitudinal direction inside the wide portion 721. Other configurations are the same as those in the first embodiment.

以上説明したように、＜５＞本実施形態では、弁穴部７３１は弁本体７００の周方向の一方の端部に形成され、弁穴部７３２は弁本体７００の周方向の他方の端部に形成されている。弁穴部７３１は、円形に形成されている。弁穴部７３２は、弁本体７００の周方向に延びる長穴状に形成されている。弁穴部７３１、弁穴部７３２は、互いに少なくとも一部が弁本体７００の周方向で重なる。そのため、円形の弁穴部７３１を規制突起部９１により係止することで、弁本体７００の回転を規制することができる。 As described above, <5> In the present embodiment, the valve hole portion 731 is formed at one end in the circumferential direction of the valve body 700, and the valve hole portion 732 is formed at the other end in the circumferential direction of the valve body 700. Is formed in. The valve hole portion 731 is formed in a circular shape. The valve hole portion 732 is formed in an elongated hole shape extending in the circumferential direction of the valve body 700. At least a part of the valve hole portion 731 and the valve hole portion 732 overlap each other in the circumferential direction of the valve body 700. Therefore, the rotation of the valve body 700 can be regulated by locking the circular valve hole portion 731 with the regulating protrusion 91.

ここで、仮に、幅広部７２２において弁穴部７３２を円形に形成し、幅広部７２１において弁穴部７３１を長穴状に形成した場合、弁本体７００の開閉弁時、幅広部７２１は、幅広部７２２の外側において、弁穴部７３１の長手方向の長さの範囲で幅広部７２２に対し相対移動しながら変形可能である。しかしながら、幅広部７２１は、幅広部７２２と底面５５０とに挟まれているため、弁本体７００の円滑な変形、すなわち、開閉弁作動が阻害されるおそれがある。これに対し、本実施形態では、幅広部７２１の内側に位置する幅広部７２２において弁穴部７３２が長穴状に形成されているため、弁本体７００の開閉弁時、幅広部７２２は、幅広部７２１の内側において、弁穴部７３２の長手方向の長さの範囲で幅広部７２１に対し相対移動しながら変形可能である。よって、内側の弁穴部７３２を円形に形成し、外側の弁穴部７３１を長穴状に形成する場合と比べ、弁本体７００の変形、すなわち、開閉弁作動を円滑にすることができる。 Here, if the valve hole portion 732 is formed in a circular shape in the wide portion 722 and the valve hole portion 731 is formed in a long hole shape in the wide portion 721, the wide portion 721 is wide when the valve body 700 is opened and closed. On the outside of the portion 722, the valve hole portion 731 can be deformed while moving relative to the wide portion 722 within the length range in the longitudinal direction. However, since the wide portion 721 is sandwiched between the wide portion 722 and the bottom surface 550, the smooth deformation of the valve body 700, that is, the operation of the on-off valve may be hindered. On the other hand, in the present embodiment, since the valve hole portion 732 is formed in a long hole shape in the wide portion 722 located inside the wide portion 721, the wide portion 722 is wide when the valve body 700 is opened and closed. Inside the portion 721, the valve hole portion 732 can be deformed while moving relative to the wide portion 721 within the range of the length in the longitudinal direction. Therefore, as compared with the case where the inner valve hole portion 732 is formed in a circular shape and the outer valve hole portion 731 is formed in an elongated hole shape, the deformation of the valve body 700, that is, the operation of the on-off valve can be smoothed.

（第３実施形態）
第３実施形態による弁装置の一部を図１１に示す。第３実施形態は、チェック弁および回転規制部の構成等が第１実施形態と異なる。なお、図１１では、スプール６０、スプリング６３等の図示を省略している。 (Third Embodiment)
A part of the valve device according to the third embodiment is shown in FIG. The third embodiment is different from the first embodiment in the configuration of the check valve and the rotation control unit. Note that in FIG. 11, the spool 60, the spring 63, and the like are not shown.

第３実施形態では、「チェック弁」としての遅角供給チェック弁７１は、第１実施形態で示した弁穴部７３１、弁穴部７３２を有していない。環状溝部５５の遅角環状溝部５１１は、幅狭溝部５５１、幅広溝部５５２を有している。幅狭溝部５５１は、遅角環状溝部５１１の周方向の一部に形成されている。幅広溝部５５２は、遅角環状溝部５１１の周方向の幅狭溝部５５１以外の部位に形成され、遅角環状溝部５１１の軸方向の長さである幅ｗ１２が幅狭溝部５５１の幅ｗ１１より大きい。なお、幅広溝部５５２は、遅角環状溝部５１１の周方向において隣り合う遅角供給開口部ＯＲｓ間の距離のうち最大距離となる区間である最大距離区間Ｓｂｄ内に形成されている。 In the third embodiment, the check valve 71 as a "check valve" does not have the valve hole portion 731 and the valve hole portion 732 shown in the first embodiment. The retarded annular groove portion 511 of the annular groove portion 55 has a narrow groove portion 551 and a wide groove portion 552. The narrow groove portion 551 is formed in a part of the retarded annular groove portion 511 in the circumferential direction. The wide groove portion 552 is formed in a portion other than the width narrow groove portion 551 in the circumferential direction of the retard angle annular groove portion 511, and the width w12 which is the axial length of the retard angle annular groove portion 511 is larger than the width w11 of the narrow angle groove portion 551. .. The wide groove portion 552 is formed in the maximum distance section Sbd, which is the maximum distance among the distances between the retard angle supply openings ORs adjacent to each other in the circumferential direction of the retard angle annular groove portion 511.

回転規制部９０は、幅狭溝部５５１と幅広溝部５５２との間に形成された規制段差面９５を有している。回転規制部９０は、規制段差面９５が弁本体７００の幅狭部７１０と幅広部７２１、幅広部７２２との間の段差面７１９を係止することにより弁本体７００の回転位置を規制する。より具体的には、回転規制部９０は、第１実施形態と同様、幅広部７２１、幅広部７２２の少なくとも一部が、最大距離区間Ｓｂｄ内に位置するよう弁本体７００の回転位置を規制する。進角供給チェック弁７２、進角環状溝部５１２、および、進角環状溝部５１２に設けられる回転規制部９０の構成も、遅角供給チェック弁７１、遅角環状溝部５１１、および、遅角環状溝部５１１に設けられる回転規制部９０の構成と同様である。第３実施形態は、上述した点以外の構成は、第１実施形態と同様である。 The rotation regulating portion 90 has a regulating step surface 95 formed between the narrow groove portion 551 and the wide groove portion 552. The rotation regulating unit 90 regulates the rotation position of the valve body 700 by the regulation step surface 95 locking the step surface 719 between the narrow portion 710 of the valve body 700 and the wide portion 721 and the wide portion 722. More specifically, the rotation regulating unit 90 regulates the rotation position of the valve body 700 so that at least a part of the wide portion 721 and the wide portion 722 is located within the maximum distance section Sbd, as in the first embodiment. .. The configuration of the advance angle supply check valve 72, the advance angle annular groove portion 512, and the rotation restricting portion 90 provided in the advance angle annular groove portion 512 is also the same as the check valve 71, the retard angle annular groove portion 511, and the retard angle annular groove portion. The configuration is the same as that of the rotation control unit 90 provided in 511. The third embodiment has the same configuration as the first embodiment except for the above-mentioned points.

以上説明したように、本実施形態では、環状溝部５５は、環状溝部５５の周方向の一部に形成された幅狭溝部５５１、および、環状溝部５５の周方向の幅狭溝部５５１以外の部位に形成され環状溝部５５の軸方向の長さである幅が幅狭溝部５５１の幅より大きい幅広溝部５５２を有している。回転規制部９０は、幅狭溝部５５１と幅広溝部５５２との間に形成された規制段差面９５を有し、規制段差面９５が弁本体７００の幅狭部７１０と幅広部７２１、幅広部７２２との間の段差面７１９を係止することにより弁本体７００の回転位置を規制する。そのため、第１実施形態と比べ、回転規制部９０の部材点数を低減できる。 As described above, in the present embodiment, the annular groove portion 55 is a portion other than the narrow groove portion 551 formed in a part of the annular groove portion 55 in the circumferential direction and the narrow groove portion 551 in the circumferential direction of the annular groove portion 55. The annular groove portion 55 has a wide groove portion 552 having a width larger than the width of the narrow groove portion 551, which is the axial length of the annular groove portion 55. The rotation regulation portion 90 has a regulation step surface 95 formed between the narrow groove portion 551 and the wide groove portion 552, and the regulation step surface 95 is the narrow portion 710, the wide portion 721, and the wide portion 722 of the valve body 700. The rotation position of the valve body 700 is regulated by locking the stepped surface 719 between the valve body and the valve body 700. Therefore, the number of members of the rotation regulation unit 90 can be reduced as compared with the first embodiment.

（他の実施形態）
上述の実施形態では、回転規制部９０が、幅広部７２１、幅広部７２２の少なくとも一部が環状溝部５５の最大距離区間Ｓｂｄ内に位置するよう弁本体７００の回転位置を規制する例を示した。これに対し、本発明の他の実施形態では、回転規制部９０は、幅広部７２１、幅広部７２２の全ての部位が、最大距離区間Ｓｂｄ内に位置するよう弁本体７００の回転位置を規制することとしてもよい。つまり、回転規制部９０は、幅広部７２１、幅広部７２２が遅角環状溝部５１１の周方向において遅角供給開口部ＯＲｓと重ならないよう弁本体７００の回転位置を規制することとしてもよい。この場合、幅広部７２１、幅広部７２２が環状溝部５５から径方向内側すなわち内周壁５４側へ飛び出るのをより効果的に抑制できる。 (Other embodiments)
In the above-described embodiment, an example is shown in which the rotation restricting unit 90 restricts the rotation position of the valve body 700 so that at least a part of the wide portion 721 and the wide portion 722 is located within the maximum distance section Sbd of the annular groove portion 55. .. On the other hand, in another embodiment of the present invention, the rotation regulating unit 90 regulates the rotation position of the valve body 700 so that all the portions of the wide portion 721 and the wide portion 722 are located within the maximum distance section Sbd. It may be that. That is, the rotation restricting unit 90 may restrict the rotation position of the valve body 700 so that the wide portion 721 and the wide portion 722 do not overlap with the retard angle supply openings ORs in the circumferential direction of the retard angle annular groove portion 511. In this case, it is possible to more effectively prevent the wide portion 721 and the wide portion 722 from jumping out from the annular groove portion 55 in the radial direction, that is, toward the inner peripheral wall 54 side.

また、上述の実施形態では、弁穴部７３１、弁穴部７３２が、幅広部７２１、幅広部７２２に形成される例を示した。これに対し、本発明の他の実施形態では、弁穴部７３１、弁穴部７３２は、幅広部７２１、幅広部７２２以外の部位である幅狭部７１０に形成されていてもよい。 Further, in the above-described embodiment, an example is shown in which the valve hole portion 731 and the valve hole portion 732 are formed in the wide portion 721 and the wide portion 722. On the other hand, in another embodiment of the present invention, the valve hole portion 731 and the valve hole portion 732 may be formed in the narrow portion 710 which is a portion other than the wide portion 721 and the wide portion 722.

また、本発明の他の実施形態では、筒部材の流入穴は、環状溝部の周方向に不等間隔で配置されるのであれば、いくつ形成されていてもよい。 Further, in another embodiment of the present invention, any number of inflow holes of the tubular member may be formed as long as they are arranged at irregular intervals in the circumferential direction of the annular groove portion.

また、本発明の他の実施形態では、弁装置１１は、全ての部位がハウジング２０の外部に位置するよう設けられていてもよい。この場合、アウタースリーブ４０は、ねじ部４１を省略することができる。 Further, in another embodiment of the present invention, the valve device 11 may be provided so that all the portions are located outside the housing 20. In this case, the outer sleeve 40 can omit the screw portion 41.

また、本発明の他の実施形態では、チェーン６に代えて、例えばベルト等の伝達部材によりハウジング２０とクランク軸２とが連結されていてもよい。 Further, in another embodiment of the present invention, the housing 20 and the crankshaft 2 may be connected by a transmission member such as a belt instead of the chain 6.

また、上述の実施形態では、ベーンロータ３０がカム軸３の端部に固定され、ハウジング２０がクランク軸２に連動して回転する例を示した。これに対し、本発明の他の実施形態では、ベーンロータ３０がクランク軸２の端部に固定され、ハウジング２０がカム軸３に連動して回転することとしてもよい。 Further, in the above-described embodiment, an example is shown in which the vane rotor 30 is fixed to the end of the cam shaft 3 and the housing 20 rotates in conjunction with the crank shaft 2. On the other hand, in another embodiment of the present invention, the vane rotor 30 may be fixed to the end of the crankshaft 2 and the housing 20 may rotate in conjunction with the camshaft 3.

本発明のバルブタイミング調整装置１０は、エンジン１の排気弁５のバルブタイミングを調整することとしてもよい。 The valve timing adjusting device 10 of the present invention may adjust the valve timing of the exhaust valve 5 of the engine 1.

また、本発明の弁装置は、例えば上記特許文献１の油圧アクチュエータ等に供給する作動流体を制御するのに用いてもよい。また、本発明の弁装置は、バルブタイミング調整装置以外の装置等に供給する流体を制御するのに用いてもよい。
このように、本開示は、上記実施形態に限定されるものではなく、その要旨を逸脱しない範囲で種々の形態で実施可能である。 Further, the valve device of the present invention may be used to control the working fluid supplied to, for example, the hydraulic actuator of Patent Document 1. Further, the valve device of the present invention may be used to control the fluid supplied to a device other than the valve timing adjusting device.
As described above, the present disclosure is not limited to the above-described embodiment, and can be implemented in various forms without departing from the gist thereof.

１１ 弁装置、５０ インナースリーブ（筒部材）、５３ 外壁、５３１ 遅角外壁（外壁）、５３２ 進角外壁（外壁）、５４ 内周壁、５５ 環状溝部、５１１ 遅角環状溝部（環状溝部）、５１２ 進角環状溝部（環状溝部）、５５０ 底面、７１ 遅角供給チェック弁（チェック弁）、７２ 進角供給チェック弁（チェック弁）、７００ 弁本体、７１０ 幅狭部、７２１、７２２ 幅広部、９０ 回転規制部、ＯＲｓ 遅角供給開口部（流入穴）、ＯＡｓ 進角供給開口部（流入穴）、Ｓｂｄ 最大距離区間 11 Valve device, 50 Inner sleeve (cylindrical member), 53 Outer wall, 53 Declared outer wall (outer wall), 532 Advance angle outer wall (outer wall), 54 Inner peripheral wall, 55 Annular groove, 511 Deviated annular groove (annular groove), 512 Advance angle annular groove part (annular groove part), 550 bottom surface, 71 check valve, 72 advance angle supply check valve (check valve), 700 valve body, 710 narrow part, 721, 722 wide part, 90 Rotation control part, ORs check valve opening (inflow hole), OAs advance angle supply opening (inflow hole), Sbd maximum distance section

Claims (7)

内周壁（５４）から径方向外側へ凹みつつ周方向に延びて環状に形成された環状溝部（５５、５１１、５１２）、および、前記環状溝部の周方向に不等間隔で複数形成され前記環状溝部の底面（５５０）と外壁（５３、５３１、５３２）とを連通する流入穴（ＯＲｓ、ＯＡｓ）を有する筒部材（５０）と、
単一の板材を長手方向が周方向に沿うよう巻くことにより筒状に形成された弁本体（７００）を有し、前記弁本体の周方向が前記環状溝部の底面の周方向に沿うよう前記環状溝部に設けられ、前記流入穴を経由して前記筒部材の内側へ向かう流体の流れを許容し、前記筒部材の内側から前記流入穴へ向かう流体の流れを規制可能なチェック弁（７１、７２）と、
前記環状溝部の周方向における前記弁本体の回転位置を所定範囲内に規制可能な回転規制部（９０）と、を備え、
前記チェック弁は、前記弁本体の周方向の一部に形成された幅狭部（７１０）、および、前記弁本体の周方向の前記幅狭部以外の部位に形成され前記弁本体の軸方向の長さである幅が前記幅狭部の幅より大きい幅広部（７２１、７２２）を有し、
前記幅広部の少なくとも一部は、前記環状溝部の周方向において隣り合う前記流入穴間の距離のうち最大距離となる区間である最大距離区間（Ｓｂｄ）内に位置する弁装置（１１）。 An annular groove portion (55, 511, 512) formed in an annular direction extending from the inner peripheral wall (54) in the circumferential direction while denting outward in the radial direction, and a plurality of annular grooves formed at unequal intervals in the circumferential direction of the annular groove portion. A tubular member (50) having inflow holes (ORs, OAs) that communicate the bottom surface (550) of the groove and the outer wall (53, 531, 532).
The valve body (700) is formed in a tubular shape by winding a single plate material so that the longitudinal direction is along the circumferential direction, and the circumferential direction of the valve body is along the circumferential direction of the bottom surface of the annular groove portion. A check valve (71, which is provided in the annular groove portion and can allow the flow of fluid toward the inside of the tubular member via the inflow hole and regulate the flow of fluid from the inside of the tubular member toward the inflow hole. 72) and
A rotation regulating portion (90) capable of regulating the rotation position of the valve body in the circumferential direction of the annular groove portion within a predetermined range is provided.
The check valve is formed in a portion other than the narrow portion (710) formed in a part of the valve body in the circumferential direction and the narrow portion in the circumferential direction of the valve body, and is formed in the axial direction of the valve body. Has a wide portion (721, 722) in which the width, which is the length of the narrow portion, is larger than the width of the narrow portion.
At least in part, the valve device you located within a maximum distance interval (Sbd) is a section serving as a maximum distance among the distances between the inflow holes adjacent in the circumferential direction of the annular groove of the front Symbol wide portion (11) .. 前記幅広部は、前記弁本体の周方向の一方の端部および他方の端部に１つずつ形成され、 The wide portion is formed one by one at one end and the other end in the circumferential direction of the valve body.
前記幅狭部は、前記弁本体の周方向において２つの前記幅広部の間に１つ形成されている請求項１に記載の弁装置。 The valve device according to claim 1, wherein the narrow portion is formed between the two wide portions in the circumferential direction of the valve body. 前記幅広部の全ての部位は、前記最大距離区間内に位置する請求項１または２に記載の弁装置。 The valve device according to claim 1 or 2, wherein all the parts of the wide portion are located within the maximum distance section. 前記チェック弁は、前記弁本体の周方向の一部において前記弁本体を板厚方向に貫くよう形成された弁穴部（７３１、７３２）を有し、
前記回転規制部は、前記弁穴部を通るよう前記環状溝部の底面から前記筒部材の径方向内側へ延びる規制突起部（９１）を有し、前記規制突起部が前記弁穴部を係止することにより前記弁本体の回転位置を規制する請求項１〜３のいずれか一項に記載の弁装置。 The check valve has valve holes (731, 732) formed so as to penetrate the valve body in the plate thickness direction in a part of the valve body in the circumferential direction.
The rotation restricting portion has a regulating protrusion (91) extending radially inward from the bottom surface of the annular groove portion so as to pass through the valve hole portion, and the regulating protrusion locks the valve hole portion. The valve device according to any one of claims 1 to 3, wherein the rotational position of the valve body is regulated by the valve device. 前記弁穴部は、前記幅広部に形成されている請求項４に記載の弁装置。 The valve device according to claim 4 , wherein the valve hole portion is formed in the wide portion. 前記弁穴部は、前記弁本体の周方向の一方の端部に１つ、前記弁本体の周方向の他方の端部に１つ、前記弁本体に合計２つ形成されており、
２つの前記弁穴部は、いずれも前記弁本体の周方向に延びる長穴状に形成され、互いに少なくとも一部が前記弁本体の周方向で重なる請求項４または５に記載の弁装置。 The valve hole portion is formed at one end in the circumferential direction of the valve body, one at the other end in the circumferential direction of the valve body, and a total of two in the valve body.
The valve device according to claim 4 or 5 , wherein each of the two valve hole portions is formed in an elongated hole shape extending in the circumferential direction of the valve body, and at least a part thereof overlaps with each other in the circumferential direction of the valve body. 前記弁穴部は、前記弁本体の周方向の一方の端部に１つ、前記弁本体の周方向の他方の端部に１つ、前記弁本体に合計２つ形成されており、
２つの前記弁穴部のうち一方は、円形に形成され、
２つの前記弁穴部のうち他方は、前記弁本体の周方向に延びる長穴状に形成され、
２つの前記弁穴部は、互いに少なくとも一部が前記弁本体の周方向で重なる請求項４または５に記載の弁装置。 The valve hole portion is formed at one end in the circumferential direction of the valve body, one at the other end in the circumferential direction of the valve body, and a total of two in the valve body.
One of the two valve holes is formed in a circular shape.
The other of the two valve holes is formed in the shape of an elongated hole extending in the circumferential direction of the valve body.
The valve device according to claim 4 or 5 , wherein at least a part of the two valve holes overlap each other in the circumferential direction of the valve body.
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Publication number Priority date Publication date Assignee Title
US3882891A (en) * 1974-06-19 1975-05-13 Abex Corp Check valve
US6899199B2 (en) * 2002-10-24 2005-05-31 Barnes Group Inc. Flapper finger valve assembly
DE102005013085B3 (en) * 2005-03-18 2006-06-01 Hydraulik-Ring Gmbh Hydraulic valve for automobile, has check valve with band formed of closed ring, which serves as opening-free band and is made of spring steel, where steel forms ring by overlap of section of bands at about one hundred and eighty degree
US8225818B1 (en) * 2011-03-22 2012-07-24 Incova Technologies, Inc. Hydraulic valve arrangement with an annular check valve element
GB201310830D0 (en) * 2013-06-18 2013-07-31 Univ Brunel Radial flow non-return fluid valve assembly
DE102014216175A1 (en) * 2014-08-14 2016-02-18 Schaeffler Technologies AG & Co. KG Check valve for a control valve of a camshaft adjuster

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