JP2011220137A - Valve timing control device of internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve timing control device for an internal combustion engine capable of being embodied in a lightweight construction.SOLUTION: The valve timing control device of the internal combustion engine is equipped with a housing body 10 to form a plurality of accommodation chambers by a plurality of shoes 11-15 protruding inward, a housing member HSG furnished with a sealing member (rear plate 9) to seal the housing body 10 at its one end, at least, in the direction of a rotary shaft, vane members 6 installed inside the housing body 10 and partitioning each accommodation chamber into working chambers (angle advancing chambers A1-A5) by a plurality of vanes 61-65 protruding toward the periphery within the respective accommodation chambers so as to change the valve timing while they make relative rotation with respect to the housing member, and supply/exhaust passages (angle advance side supply/exhaust passages consisting of first grooves 515-519 and a second groove 111) having communications with the respective working chambers and performing supply and exhaust of the working fluid (working oil), wherein at least one of the supply/exhaust passages (passage consisting of the first groove 515 and the second groove 111) is open at the mating surface of at least the shoe 11 with the vane 61.

Description

  The present invention relates to a valve timing control device for an internal combustion engine.

  Conventionally, a shoe is protruded on the inner peripheral side of the housing member, and a vane member is installed inside the housing member, so that a working chamber is defined between the shoe and the vane, and hydraulic oil is supplied to these working chambers. There is known a valve timing control device for a so-called vane type internal combustion engine that converts a rotation angle of a vane member with respect to a housing member, that is, a relative rotation phase of a crankshaft and a camshaft by supplying and discharging. For example, in the device described in Patent Document 1, a groove is provided on the axial end surface on the inner peripheral side of the housing member as a supply / discharge passage for supplying and discharging hydraulic oil to and from the working chamber. A vane that contacts the shoe is provided, and the outer peripheral side of the vane is in contact with the shoe, and the inner peripheral side of the vane is separated from the shoe, so that the vane and the shoe are defined. The groove is opened in the working chamber.

JP 2002-235512 A

  However, it is difficult to reduce the weight of the conventional device. An object of the present invention is to provide a valve timing control device for an internal combustion engine that can be reduced in weight.

  In order to achieve the above object, in the apparatus of the present invention, preferably, at least one of the supply / discharge passages opens at least on a surface of the shoe facing the vane.

  Therefore, it is possible to reduce the weight.

It is a disassembled perspective view of a valve timing control device. It is a fragmentary sectional view which passes along the rotating shaft of a valve timing control apparatus (AA sectional view of FIG. 3). It is the front view which looked at the valve timing control device from the direction of a rotation axis (most retarded angle position). It is the front view which looked at the valve timing control apparatus from the rotating shaft direction (the most advanced angle position). It is sectional drawing which passes along the axial center of a locking mechanism (BB cross section of FIG. 3).

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for realizing a valve timing control device for an internal combustion engine of the present invention will be described with reference to the drawings.

[Configuration of Example 1]
The valve timing control device (hereinafter referred to as “device 1”) for an internal combustion engine according to the first embodiment is applied to the intake side of an internal combustion engine (hereinafter referred to as “engine”) of an automobile. The present invention may be applied to a device on the exhaust side of the engine.
First, the structure of the apparatus 1 is demonstrated based on FIGS. For the sake of explanation, the X-axis is provided in the direction in which the rotation axis O of the apparatus 1 extends, and the intake camshaft (hereinafter referred to as camshaft 3) side is the negative direction. FIG. 1 is an exploded view of the constituent members of the device 1 arranged on the same axis and viewed obliquely. FIG. 2 shows a partial section through the axis of rotation O of the device 1. 3 and 4 are front views of the apparatus 1 (with the vane member 6 assembled to the housing body 10) with the front plate 8 and the like removed, as viewed from the X axis positive direction side. FIG. 2 substantially corresponds to the AA cross section of FIG. 3 and 4, grooves or holes formed in the vane member 6 and the rear plate 9 are indicated by broken lines.

The camshaft 3 is made of an iron-based metal material, and is rotatably supported on the inner side of the upper end portion of the cylinder head via a bearing. A drive cam (intake cam) is provided on the outer peripheral surface of the camshaft 3 at a position corresponding to the intake valve of the engine. When the camshaft 3 rotates, the intake cam opens and closes the intake valve via a valve lifter or a rocker arm. The device 1 is attached to the end 30 on the X axis positive direction side of the camshaft 3 by one cam bolt 31.
The cam bolt 31 is a hexagon bolt and has a regular hexagonal columnar head 310 and a shaft portion 311 having a male screw formed on the outer periphery. The head 310 is integrally formed with a washer (a plain washer) 312 for protecting the seat surface. Note that the number of cam bolts is not limited to one, and a suitable one is not limited to a hexagon bolt. In addition to the bolt, an appropriate fastening and fixing means may be employed.
Inside the end portion 30, there are formed one bolt hole 32 through which the cam bolt 31 (shaft portion 311) is inserted, axial passages 502, 512 as a part of the retard passage 50 and the advance passage 51 described later, and the like. ing.
The bolt hole 32 is formed on the rotation axis O from the end surface 300 on the X axis positive direction side of the end portion 30 to a predetermined depth in the X axis direction, and has a small diameter portion 320 and a large diameter portion 321. The large diameter part 321 is provided from the end surface 300 to a predetermined depth in the X-axis direction, and the diameter of the large diameter part 321 is slightly larger than the shaft part 311 of the cam bolt 31. The small-diameter portion 320 has a step with respect to the large-diameter portion 321 and is provided to a predetermined depth in the negative X-axis direction. The diameter of the small-diameter portion 320 is substantially the same as the shaft portion 311 of the cam bolt 31. is there. A female screw corresponding to the male screw of the cam bolt 31 is formed on the inner periphery of the small diameter portion 320 to form a female screw hole.
On the end surface 300 of the end portion 30, a convex portion for positioning the vane member 6 and the camshaft 3 in the circumferential direction is provided. The convex portion can be configured by inserting and installing a pin in a concave portion provided on the end surface 300, for example. As a method of providing the convex portion, the convex portion may be formed directly by processing or the like instead of using a pin. In the case of using a pin as in the first embodiment, it is simpler than directly forming a convex portion, and it is advantageous that a pin (such as a dowel pin) suitable for positioning can be selected as appropriate.

The device 1 is an actuator that variably controls the valve timing of the intake valve by continuously changing the rotational phase of the camshaft 3 relative to the crankshaft using the pressure of the supplied working fluid. In the first embodiment, a working fluid, specifically, working oil (oil) is used as the working fluid. That is, the device 1 is a hydraulic drive type phase conversion device. Note that a fluid other than oil (working oil) may be used as the working fluid. The device 1 is disposed so as to be rotatable relative to the camshaft 3 and is rotationally driven by the crankshaft via a timing chain, and is disposed between the sprocket 2 and the camshaft 3. A phase change mechanism 4 for changing the relative rotational position (phase) of the crankshaft) and the camshaft 3, and a hydraulic supply / discharge mechanism 5 for operating the phase change mechanism 4. The unit of the apparatus 1 includes a housing HSG that is a housing member and a vane member 6 accommodated in the housing HSG. The phase changing mechanism 4 has a plurality of working chambers (working oil chambers or working hydraulic chambers) partitioned (defined) by the housing HSG and the vane member 6.
The housing HSG is disposed at the end 30 of the camshaft 3. The housing HSG is provided with a sprocket 2, and the rotational force from the crankshaft is transmitted through the sprocket 2. The vane member 6 is fixed to the end 30 by the cam bolt 31 from the X-axis direction, and is housed inside the housing HSG so as to be rotatable relative to the housing HSG (sprocket 2). The plurality of working chambers are retarded chambers (retarded working chambers) R1 to R5 and advanced chambers (divided by shoes 11 to 15 provided on the inner periphery of the housing HSG and vanes 61 to 65 of the vane member 6). Advance angle working chambers) A1 to A5. The phase changing mechanism 4 receives supply of hydraulic oil from the hydraulic supply / discharge mechanism 5 or discharges the hydraulic oil to the hydraulic supply / discharge mechanism 5, whereby the vane member 6 (camshaft 3) with respect to the housing HSG (crankshaft). Change the rotation phase. The hydraulic supply / discharge mechanism 5 has a hydraulic circuit, and the pressure of the hydraulic oil supplied from the hydraulic circuit to the working chamber acts on the vanes 61 to 65, whereby the vane member 6 rotates with respect to the housing HSG. The rotation angle (phase conversion angle) of the camshaft 3 with respect to the crankshaft is changed. The supply / discharge of hydraulic oil by the hydraulic supply / discharge mechanism 5 is controlled by a controller CU as a control means.

The housing HSG has a front plate 8, a rear plate 9, and a housing body 10. The housing body 10 is a housing member (sintered alloy body) made into a hollow cylindrical shape by sintering an iron-based metal material, and both ends in the X-axis direction are open. A front plate 8 and a rear plate 9 as sealing members are respectively fixed to both ends of the housing main body 10 in the X-axis direction, and seal the openings of the housing main body 10. The shape of the housing body 10 is not particularly limited. For example, the housing body 10 has a bottomed cylindrical shape opened only at one end in the axial direction, in other words, a bowl shape in which one of the sealing members 8 and 9 and the housing body 10 are integrally formed. There may be.
A sprocket 2 is integrally provided on the outer periphery of the housing body 10 at a substantially central position in the X-axis direction of the housing body 10. The sprocket 2 is a gear having a plurality of convex portions (teeth) extending in the X-axis direction at substantially equal intervals in the circumferential direction, and is formed by rolling after sintering the housing body 10. The sprocket 2 is heat-treated integrally with the housing body 10 and has high strength and high hardness. A chain is wound around the sprocket 2 and is driven to rotate by a crankshaft through the chain and rotates clockwise together with the housing body 10. Note that the sprocket 2 is not necessarily provided as a member integral with the housing body 10, and may be provided on a housing member (such as the rear plate 9) other than the housing body 10. Further, the power may be transmitted not only by the sprocket and the chain but also by a pulley and a belt. For example, a pulley may be provided on the outer periphery of the housing body, and the belt may be wound. When a chain and a sprocket are used as in the first embodiment, there are advantages such as easy downsizing of the apparatus in the axial direction.
On the inner periphery of the housing body 10, a plurality of (in this embodiment, five) shoes 11 to 15 are integrated with the housing body 10 so as to protrude toward the inner periphery side (the rotation axis O side). Molded. The shoes 11 to 15 are provided so as to slide with the vane member 6 (rotor 60) in the housing HSG, and constitute inner walls (partition walls) that define a plurality of (five in the first embodiment) storage chambers. ing. The shoes 11 to 15 may be provided separately from the housing body 10. Specifically, the first to fifth shoes 11 to 15 are arranged in an inner diameter direction (rotation) from the inner peripheral surface of the housing body 10 at substantially equal intervals in a direction around the rotation axis O (hereinafter referred to as a circumferential direction). Projecting toward the axis O). As shown in FIG. 3, the first to fifth shoes 11 to 15 are arranged in the clockwise direction in this order as viewed from the X axis positive direction side (hereinafter referred to as “clockwise” and “counterclockwise without notice”). "Refers to the case viewed from the positive side of the X axis.) Each of the shoes 11 to 15 is formed to extend in the X-axis direction, and a cross section cut in a direction perpendicular to the X-axis has a substantially trapezoidal shape (a side surface is substantially U-shaped) whose width decreases toward the inner diameter direction. Is provided. Holes 110 to 150 are formed in the X axis direction in the outer diameter side (the direction away from the rotation axis O) of the shoes 11 to 15, respectively. The holes 110 to 150 are bolt holes through which the bolts b1 to b5 are respectively inserted. A front plate 8 is fixedly installed on the end surface of each shoe 11-15 on the X-axis positive direction side, and a rear plate 9 is fixedly installed on the end surface of the X-axis negative direction side.
Except between the first shoe 11 and the second shoe 12, the circumferential width of the gap between the adjacent shoes 11 to 15 is set to be approximately the same. The gap between the first shoe 11 and the second shoe 12 is provided with a wider width in the circumferential direction than the gap between the other shoes because a wide first vane 61 described later is accommodated. The circumferential widths passing through the centers of the bolt holes 110 to 150 of the shoes are such that the second to fifth shoes 12 to 15 are provided with substantially the same size, and the width of the first shoe 11 is the same as that of the other shoes 12 to 15. It is larger than 15 (wider).
The circumferential side surfaces (clockwise and counterclockwise surfaces) of the shoes 11 to 15 are provided so as to extend in the radial direction of the housing body 10. For example, the flat surface portion 113 formed on the clockwise side of the first shoe 11 and the flat surface portion 121 formed on the counterclockwise direction side of the second shoe 12 have a housing radial direction ( It is a straight line that is substantially coincident with the radial straight line passing through the rotation axis O.
On the inner diameter side (tip portion) of each shoe 11-15, a tip surface that continues to the circumferential side surface of each shoe 11-15 via a slight radius is provided facing the rotation axis O. Is formed in a shape along an outer peripheral surface 600 of the rotor 60 of the vane member 6 described later (an arc shape slightly depressed in the outer diameter direction when viewed from the X-axis direction). The circumferential width of the tip surface of the first shoe 11 is wider than the tip surfaces of the other shoes 12-15.
The outer diameter side (base part or base part) of each shoe 11-15 continues to the inner peripheral surface of the housing body 10 through a slight radius. A built-up portion 114 is integrally formed at the root portion of the first shoe 11 in the clockwise direction (the housing outer diameter side of the flat portion 113). The build-up portion 114 has a gently curved shape (curved shape) that protrudes toward the outer periphery of the housing. When viewed from the X-axis direction, the side surface of the built-up portion 114 (facing the inside of the housing) extends to the housing inner diameter side with a predetermined curvature with respect to the inner peripheral surface of the housing body 10, and the housing diameter of the first shoe 11 It continues to the plane portion 113 at a substantially intermediate position in the direction.
On the outer peripheral side of the first shoe 11 (in the outer peripheral surface of the housing main body 10), a recess 116 is provided on the clockwise direction side so as to be sandwiched between the build-up portion 114 and the bolt hole 110. The recess 116 is a recess for positioning the housing body 10 and the rear plate 9 in the circumferential direction, and is formed over the entire range of the first shoe 11 in the X-axis direction, and is recessed toward the inner diameter side when viewed from the X-axis direction. It is provided in the shape.
Concave grooves 117 to 157 are provided in the inner peripheral portions (tip portions) of the first to fifth shoes 11 to 15, respectively. The concave grooves 117 to 157 are seal grooves that are formed in a substantially rectangular shape toward the outer diameter side when viewed from the X-axis direction, and are substantially at the center in the circumferential direction of the inner peripheral surfaces (tip surfaces) of the shoes 11 to 15. It is provided at the position over the entire range in the X-axis direction so as to extend in the direction of the rotation axis O. Seal members S1 to S5 are fitted and held in the seal grooves 117 to 157, respectively.
As shown in FIG. 2, the seal member S3 includes a seal body 138 and an urging means 139. The seal body 138 is substantially U-shaped when viewed from the circumferential direction, and has a seal surface portion that extends by the length of the shoe 13 approximately in the X-axis direction. 60 is provided in the seal groove 137 so as to face the outer peripheral surface 600 side). The urging means 139 is composed of a leaf spring as a seal spring, and is installed in the seal groove 137 so as to urge the seal body 138 (seal surface portion) toward the rotor outer peripheral surface 600 side. . The seal surface portion is in elastic contact with the outer peripheral surface 600 (in the entire range in the X-axis direction) of the rotor 60, and is in sliding contact with the rotor outer peripheral surface 600 when the rotor 60 rotates relative to the housing HSG. The other seal members S1, S2, S4, and S5 are similarly configured, and have seal bodies 118, 128, 148, and 158 and biasing means 119, 129, 149, and 159, respectively.
As shown in FIGS. 3 and 5, a groove 111 is formed on the first shoe 11 in the clockwise direction side (plane portion 113) from the X-axis negative direction side to a predetermined depth in the X-axis direction. The corners of the first shoe 11 on the clockwise direction side and the X-axis negative direction side are notched by the grooves 111, and the grooves 111 are formed on the surfaces of the first shoes 11 on the clockwise direction side (planar portions 113). ) And the X-axis negative direction side surface. The groove 111 is molded at the same time when the housing body 10 is molded in a coarse material state. The groove 111 linearly extends from the inner peripheral side end (tip portion) of the first shoe 11 to the outer peripheral side of the housing body 10 to a substantially intermediate position in the radial direction of the first shoe 11. The cross section of the groove 111 cut along a plane perpendicular to the direction in which the groove 111 extends is substantially rectangular. When viewed from the positive side of the X axis, the edge of the groove 111 in the clockwise direction coincides with the surface of the first shoe 11 in the clockwise direction (the plane portion 113), and the edge of the groove 111 in the counterclockwise direction is It is substantially parallel to the plane part 113. When viewed from the circumferential direction (clockwise direction side), the edge of the groove 111 on the X axis negative direction side coincides with the surface of the first shoe 11 on the X axis negative direction side, and the edge of the groove 111 on the X axis positive direction side is It is substantially parallel to the X-axis direction side surface of the first shoe 11. The widths of the grooves 111 are substantially equal in the groove length direction. Note that the groove widths need not be uniform.
Further, the groove 111 is disposed so as not to overlap the seal groove 117 when viewed from the X-axis direction. Specifically, the edge on the counterclockwise direction side of the groove 111 is disposed on the distal end surface of the first shoe 11 slightly more clockwise than the edge on the clockwise direction side of the seal groove 117, and Since the distance from the edge of the seal groove 117 is increased toward the radial side, communication between the groove 111 and the seal groove 117 is suppressed.

The front plate 8 is formed into a disk (disk) shape by pressing a ferrous metal material, specifically a steel material, and is an opening end on the X axis positive direction side of the housing body 10, in other words, an advance angle. The ends on the X axis positive direction side of the chamber A and the retarded chamber R are closed and sealed.
The diameter of the front plate 8 is substantially the same as the diameter of the outer peripheral surface of the housing body 10 excluding the sprocket 2. A hole 80 is formed in the center of the inner diameter side of the front plate 8 so as to penetrate in the X-axis direction. The hole 80 is an insertion hole through which the cam bolt 31 is inserted (when the device 1 is assembled to the camshaft 3), and is a large-diameter hole whose diameter is slightly larger than that of the washer 312.
A hole 800 is formed through the front plate 8 in the X-axis direction. The hole 800 is formed continuously to the hole 80 in a substantially rectangular shape when viewed from the X-axis direction, and extends from the inner peripheral surface of the hole 800 by a predetermined distance in the plate outer diameter direction. In a state where the vane member 6 is installed in the housing HSG, the hole 800 is disposed so as to substantially overlap with a radial groove 605 of the vane member 6 to be described later in the X-axis direction. 6 within a total relative rotation range of 6 and a dimension that substantially overlaps the radial groove 605 in the X-axis direction. The hole 800 is an air vent hole and, together with the radial groove 605, constitutes a back pressure relief portion of the back pressure chamber 72 of the lock piston 71 described later.
On the outer diameter side of the front plate 8, five holes 81 to 85 are formed to penetrate in the X-axis direction at substantially equal intervals in the circumferential direction. The holes 81 to 85 are bolt holes through which the bolts b1 to b5 are respectively inserted, and are provided at respective locations facing the bolt holes 110 to 150 of the shoes 11 to 15 of the housing body 10 in the X-axis direction. The front plate 8 is formed as thin as possible in the X-axis direction to such an extent that rigidity against the fastening force of the bolts b1 to b5 (strength of the surface on which the bolt head is seated) can be ensured.

The rear plate 9 is formed into a disk (disk) shape by sintering a ferrous metal material, like the housing body 10, and is the opening end of the housing body 10 on the X axis negative direction side, in other words, an advance angle. The ends of the chamber A and the retarded chamber R on the X axis negative direction side are closed and sealed so that the camshaft 3 can be inserted. Unlike the housing body 10, the rear plate 9 is not heat-treated after the sintering, and therefore has a lower hardness than the housing body 10.
As shown in FIG. 2, the thickness of the rear plate 9 in the X-axis direction is thicker than the width of the front plate 8 in the X-axis direction, and is substantially the same as the width of the sprocket 2 in the X-axis direction. The diameter of the rear plate 9 is approximately the same as the diameter of the outer peripheral surface of the housing body 10 excluding the sprocket 2.
A hole 90 is formed at substantially the center on the inner diameter side of the rear plate 9 so as to pass through the rear plate 9 in the X-axis direction (rotational axis direction) substantially coaxially with the rotational axis O. The hole 90 is an insertion hole through which the camshaft end 30 is inserted and rotatably supported, and is also a support hole that rotatably supports the housing HSG with respect to the camshaft 3. The insertion hole 90 is molded at the same time when the rear plate 9 is molded in a coarse material state, and is processed so that the diameter thereof is substantially the same as the large-diameter hole 80 of the front plate 8.
On the outer diameter side of the rear plate 9, five female screw portions 91 to 95 are provided at substantially equal intervals in the circumferential direction. The female thread portions 91 to 95 are provided at locations facing the bolt holes 110 to 150 of the shoes 11 to 15 and the bolt holes 81 to 85 of the front plate 8 in the X-axis direction, respectively. The female thread portions 91 to 95 each have bolt holes formed so as to penetrate the rear plate 9 in the X-axis direction, and female threads are formed on the inner periphery of these bolt holes. The male threads at the front ends of the bolts b1 to b5 on the negative side of the X-axis are respectively screwed onto the female threads.
That is, the front plate 8, the housing body 10, and the rear plate 9 are integrally coupled together by bolts b1 to b5 from the X-axis direction. Bolts b1 to b5 are respectively inserted into bolt holes 81 to 85 of front plate 8 and bolt holes 110 to 150 of housing body 10 from the X axis positive direction side, and are screwed into female thread portions 91 to 95 of rear plate 9. As a result, the front plate 8 and the rear plate 9 are fastened and fixed to the housing body 10. The bolt holes 81 to 85 of the front plate 8 and the bolt holes 110 to 150 of the housing body 10 are provided slightly larger than the shaft diameters of the bolts b1 to b5.
As shown in FIGS. 2 and 4, the rear plate 9 is formed with a hole 96 penetrating in the X-axis direction. The hole 96 is a fitting hole for constituting an engaging recess 730 described later, and is biased toward the advance chamber A1 side in the accommodation chamber sandwiched between the first shoe 11 and the second shoe 12 (first shoe). 11 (adjacent to the clockwise direction side).
On the surface on the X axis positive direction side of the rear plate 9, a convex portion for positioning the housing body 10 and the rear plate 9 in the circumferential direction is between the hole 96 and the female screw portion 91 and slightly outside of them. 97 is provided so as to extend in the positive direction of the X-axis. The convex portion 97 is formed in a columnar shape with a diameter substantially the same as the circumferential width of the concave portion 116 at a position substantially corresponding to the concave portion 116 of the housing body 10 in the plate radial direction. The convex portion 97 can be provided, for example, by fitting a pin into a hole formed in the rear plate 9. The circumferential position of the convex portion 97 on the rear plate 9 is such that when the convex portion 97 is fitted into the concave portion 116, the bolt hole 110 of the first shoe 11 and the female thread portion 91 of the rear plate 9 are positioned substantially coaxially. In addition, in a state where a first vane 61 (planar portion 614), which will be described later, is in contact with the first shoe 11 (planar portion 113) (see FIG. 3), a sliding hole 70 and a rear plate, which will be described later, of the first vane 61. 9 fitting holes 96 are provided so as to be positioned substantially coaxially.

A groove 900 and radially extending grooves 515, 516, 517, 518, and 519 are provided on the end surface of the rear plate 9 in the X-axis positive direction. These grooves are simultaneously molded when the rear plate 9 is molded in a coarse material state. The groove 900 is an annular groove provided at the X axis positive direction end of the inner peripheral surface of the camshaft insertion hole 90, and the diameter of the inner peripheral surface is slightly larger than the diameter of the insertion hole 90. The groove 900 is provided from the end surface of the rear plate 9 in the X-axis positive direction to a predetermined depth on the X-axis negative direction side (a little less than half the dimension of the rear plate 9 in the X-axis direction).
The grooves 515 to 519 are formed on the end surface of the rear plate 9 in the positive X-axis direction up to substantially the same depth in the X-axis direction as the groove 900. Each of the grooves 515 to 519 linearly extends from the inner peripheral side of the rear plate 9 to the outer peripheral side, and specifically from the inner peripheral surface of the camshaft insertion hole 90 (groove 900) to a predetermined position in the plate radial direction. Each extends to a substantially intermediate position in the radial direction of each shoe 11-15. In addition, you may provide the groove | channels 515-519 so that it may extend curvilinearly. When viewed from the X-axis direction, the tips (outer diameter side) of the grooves 515 to 519 are provided in a semicircular shape. The cross sections of the grooves 515 to 519 cut along a plane perpendicular to the extending direction of the grooves 515 to 519 are substantially rectangular.
As shown in FIGS. 3 and 4, the grooves 515 to 519 are inclined with respect to the plate radial direction (radial straight line passing through the rotation axis O) when viewed from the X-axis direction side, and the inner circumferential side As it goes from the (inner diameter side) to the outer peripheral side (outer diameter side), it moves away from the nearest shoes 11-15. For example, regarding the groove 516, the outer peripheral side end (the center in the width direction) of the groove 516 is (groove 516 with respect to the straight line connecting the rotation axis O and the inner peripheral side end (the center in the width direction) of the groove 516. B) It is provided so as to be biased (offset) to the side away from the circumferential center of the nearest shoe 12. The same applies to the other grooves 515, 517 to 519.
The widths of the grooves 516 to 519 excluding the groove 515 are substantially evenly provided in the groove length direction. Note that the groove widths need not be uniform. The grooves 516 to 519 are respectively provided adjacent to the second to fifth shoes 12 to 15 in the circumferential direction, and open to the clockwise direction side of the shoes 12 to 15 (tip portions) on the outer peripheral side of the rotor 60. And communicate with the advance chambers A2 to A5, respectively. When viewed from the X-axis direction, the inner diameter side (base end portion) of each of the grooves 516 to 519 is hidden by overlapping the rotor 60, while the outer diameter side (tip end portion) of each of the grooves 516 to 519 is partially part of each shoe. 12 to 15 are overlapped with the inner diameter side (tip portion), and the other portion is opened on the end surface of the rear plate 9 in the X-axis positive direction. In other words, grooves 516 to 519 are provided on the surface of the rear plate 9 facing the shoes 12 to 15 (the portion facing the shoes 12 to 15 in the X-axis direction on the end surface of the rear plate 9 in the X-axis positive direction). The surfaces on the clockwise direction side of the shoes 12 to 15 (tip portions) are arranged at substantially the center positions in the circumferential direction of the grooves 516 to 519, respectively. In other words, in the rear plate 9, each of the grooves 516 to 519 opened on the outer peripheral side of the rotor 60 is closed approximately half by the shoes 12 to 15, and the other approximately half is respectively advanced to the advance chambers A2 to A5. It is provided so that it can be opened.
On the other hand, the groove 515 is provided at a position overlapping the first shoe 11 in the circumferential direction. The width of the groove 515 is narrower on the outer peripheral side than on the inner peripheral side of the rear plate 9. The groove width of the groove 515 from the inner peripheral side, that is, the inner peripheral surface of the insertion hole 90 to the rotor outer peripheral surface 600 is the same as that of the other grooves 516 to 519. It is provided in about half. Specifically, the edge of the groove 515 on the clockwise direction side gradually deviates counterclockwise as it goes from the rotor outer peripheral surface 600 to the outer peripheral side, and the distal end round portion of the first shoe 11 on the clockwise direction side. In the vicinity of the boundary between the flat portion 113 and the flat portion 113, the flat portion 113 substantially coincides with the flat portion 113, and the portion extending from the vicinity of the boundary toward the outer peripheral side has a substantially straight line shape. On the other hand, the edge on the counterclockwise direction side of the groove 515 extends linearly from the inner peripheral surface of the insertion hole 90 toward the outer peripheral side, like the other grooves 516 to 519. Therefore, the groove 515 is closed by overlapping with the rotor 60 on the inner peripheral side (base end portion) when viewed from the X-axis direction, while from the rotor outer peripheral surface 600 to the vicinity of the boundary on the outer peripheral side (tip end portion). (The triangular area adjacent to the tip rounded portion of the first shoe 11 in the clockwise direction, see FIG. 4), the rear plate 9 opens at the end surface in the positive direction of the X axis, and the remaining portion is the first portion. It overlaps the clockwise direction side of one shoe 11.
When viewed from the positive X-axis side, the counterclockwise edge of the groove 515 is substantially parallel to the clockwise surface of the first shoe 11 (plane portion 113) and the groove 111, and the groove It is located slightly deviated counterclockwise with respect to the counterclockwise direction edge of 111. In addition, the (outer diameter side) tip of the groove 515 and the (outer diameter side) tip of the groove 111 are provided at substantially the same radial position. In other words, the groove 111 is provided on the surface of the first shoe 11 that faces the groove 515 in the X-axis direction (end surface in the negative X-axis direction), and in the X-axis direction (that is, viewed from the X-axis direction) It is formed to be included in the range.
Further, when viewed from the X-axis direction, the grooves 515 to 519 are arranged so as not to overlap the seal grooves 117 to 157 of the shoes 11 to 15. Specifically, the counterclockwise edges of the grooves 515 to 519 substantially coincide with the clockwise edges of the seal grooves 117 to 157 at the tip surfaces of the shoes 11 to 15, respectively. However, since the seal grooves 117 to 157 are separated from the edge as they go to the outer diameter side, the communication between the grooves 515 to 519 and the seal grooves 117 to 157 is suppressed. .
As shown in FIG. 2, the groove 900 and the grooves 515 to 519 are provided to a depth overlapping with an annular groove 514 (described later) of the camshaft end 30 in the X-axis direction. Specifically, the groove 900 and the grooves 515 to 519 have a slightly smaller dimension in the X-axis direction than the annular groove 514, and are positioned approximately at the center of the annular groove 514 in the X-axis direction. Therefore, the inner diameter side ends of the grooves 515 to 519 communicate with the annular groove 514 through the groove 900. The grooves 515 to 519 supply hydraulic oil from the supply / discharge oil passage (annular groove 514 and the like) on the camshaft 3 side to the advance chambers A1 to A5, respectively, or supply hydraulic oil from the advance chambers A1 to A5. Advancing-side supply / discharge passages are respectively discharged to the supply / discharge oil passages on the camshaft 3 side (hereinafter, grooves 515 to 519 are referred to as first grooves 515 to 519). Note that the groove 900 may be omitted.

  The vane member 6 is a driven rotating body (driven member) that rotates integrally with the camshaft 3 in the clockwise direction. Like the housing body 10, the vane member 6 is formed by sintering an iron-based metal material. The vane member 6 is provided on the inner diameter side (rotation center side) of the first to fifth vanes 61 to 65, which are five blades that receive the hydraulic pressure, and to the camshaft 3 by the cam bolt 31. It is a vane rotor which has the rotor 60 which is a rotating shaft part fixed substantially coaxially.

The rotor 60 has a cylindrical shape, and is supported rotatably with respect to the housing HSG while sliding with respect to the seal members S1 to S5 fitted to the tip portions of the shoes 11 to 15.
The length of the rotor 60 in the X-axis direction is slightly smaller than the length of the housing body 10 in the X-axis direction. The rotor 60 has a bottomed hole 601 that is substantially coaxial with the rotor 60 from the surface on the negative side of the X-axis toward the positive direction of the X-axis to a depth slightly less than half of the rotor 60 (on the rotation axis O) ) Is formed. The hole 601 is a camshaft insertion hole into which the insertion portion 301 of the camshaft end 30 is inserted and installed, and the diameter of the hole 601 is slightly larger than the diameter of the camshaft 3 (insertion portion 301).
In the rotor 60, a hole 602 is formed through the rotation axis O at the bottom of the hole 601 on the X axis positive direction side. The hole 602 is a bolt hole through which the shaft portion 311 of the cam bolt 31 is inserted from the X axis positive direction side, and the diameter of the hole 602 is slightly larger than the shaft portion 311. In the rotor 60, a hole 603 is formed in the bottom of the hole 601 on the X axis positive direction side so as to penetrate the hole 602 in the X axis direction. The hole 603 is a positioning hole that fits with a convex portion provided on the camshaft end surface 300 and is used for circumferential positioning of the vane member 6 with respect to the camshaft 3, and is formed to extend from the hole 602 in the rotor outer diameter direction. ing. The hole 603 has a semi-oval shape when viewed from the X-axis direction, and includes two linear portions extending in the radial direction and facing each other in the circumferential direction, and one curved portion formed in a semi-arc shape. ing. The convex portion is inserted and fitted into the hole 603 from the X-axis negative direction side. The circumferential dimension of the hole 603 (distance between the linear portions) is slightly larger than the circumferential dimension of the convex portion, and the vane member 6 and the camshaft are fitted with the convex portion fitted into the hole 603. 3 is set to a dimension that does not generate play in the circumferential direction.

On the outer periphery of the rotor 60, first to fifth vanes 61 to 65 are provided radially at substantially equal intervals in the circumferential direction so as to protrude toward the outer diameter direction. The first to fifth vanes 61 to 65 are provided in this order in the clockwise direction, and are formed integrally with the rotor 60.
The cross section of each vane 61 to 65 in the direction perpendicular to the X-axis is formed in a substantially trapezoidal shape with the circumferential width becoming wider toward the outer diameter direction. The cross-sectional shapes of the vanes 61 to 65 can be changed as appropriate. The length of each vane 61 to 65 in the X-axis direction is substantially the same as the length of the rotor 60 in the X-axis direction. The widths of the second to fifth vanes 62 to 65 in the circumferential direction are substantially the same. The circumferential width of the first vane 61 is wider than the second to fifth vanes 62 to 65 and has the maximum width, and it is possible to accommodate the lock piston 71 by forming a sliding hole 70 described later. . The intervals in the circumferential direction of the vanes 61 to 65 are adjusted so that the center of gravity of the vane member 6 is close to the rotation axis O. In a state where the vane member 6 is installed in the housing HSG, the surfaces on the X axis positive direction side of the vanes 61 to 65 are opposed to the surfaces on the X axis negative direction side of the front plate 8 with a slight gap. The surfaces on the X-axis negative direction side of the vanes 61 to 65 are opposed to the surface on the X-axis positive direction side of the rear plate 9 with a slight gap. The first vane 61 is between the first shoe 11 and the second shoe 12, the second vane 62 is between the second shoe 12 and the third shoe 13, and the third vane 63 is between the third shoe 13 and the fourth shoe 14. The fourth vane 64 is disposed between the fourth shoe 14 and the fifth shoe 15, and the fifth vane 65 is disposed in the accommodating chamber between the fifth shoe 15 and the first shoe 11.
Grooves 611 to 651 are formed along the X-axis direction at the outer diameter end portions of the first to fifth vanes 61 to 65, respectively. Seal members 612 to 652 are installed in the grooves 611 to 651, respectively. The seal members 612 to 652 have the same structure as the seal members S1 to S5 of the respective shoes 11 to 15, and the seal body that is in fluid-tight sliding contact with the inner peripheral surface of the housing body 10 and the seal body in the above-described manner. It has a seal spring (plate spring) as urging means for pressing toward the peripheral surface, and is fitted and held in seal grooves 611 to 651, respectively.

The vane member 6 forms an advance chamber A and a retard chamber R through which hydraulic oil is supplied and discharged with the housing HSG. That is, when viewed from the X-axis direction, five storage chambers are defined between adjacent shoes 11 to 15, and these storage chambers are formed into an advance chamber A and a retard chamber R by vanes 61 to 65, respectively. It is defined. In other words, the vane 61 and the like form a plurality of working chambers A and R with the shoe 11 and the like. The working oil supplied from the oil pump P is introduced into these working chambers A and R, and rotation is transmitted between the vane member 6 and the housing HSG via the working oil. Specifically, the X-axis negative direction surface of the front plate 8, the X-axis positive direction surface of the rear plate 9, the outer peripheral surface 600 of the rotor 60, and both sides of the vanes 61 to 65 in the circumferential direction. Five sets of hydraulic working chambers, that is, five advance chambers A1 to A5 and five retard chambers R1 to R5 are defined between the surface and both side surfaces of the shoes 11 to 15 in the circumferential direction. Yes. The first advance chamber A1 is formed between the clockwise side surface of the first shoe 11 and the counterclockwise side surface of the first vane 61, and the second vane 61 side surface and the second vane 61 side surface. A first retardation chamber R1 is defined between the shoe 12 and the surface on the counterclockwise direction side. Similarly, the second to fifth advance chambers A2 to A5 and the second to fifth retardation chambers are defined. Corner chambers R2 to R5 are respectively defined.
The advance chamber A and the retard chamber R are kept in a liquid-tight state by the seal member S1 or the like, respectively, between the working chambers A and R at the shoe tip (rotor outer peripheral surface) and vane tip (housing main body inner peripheral surface). The leakage of hydraulic oil is suppressed. Note that these seal members S1 and the like may be omitted. As the seal member S1 and the like, types other than those used in the first embodiment can be adopted. An elastic member other than a leaf spring may be used as the urging means 119, or the urging means may be omitted by elastically deforming the seal body 118 itself. Further, a seal groove may be provided in the outer peripheral portion of the vane member 6 and the seal member may be installed in the seal groove so as to be in sliding contact with the tip portions of the shoes 11 to 15. In the first embodiment, since the seal member is installed at the tip of the shoes 11 to 15, the hydraulic oil supply / discharge passage (holes 505 to 509, first grooves 515 to 519 described later) is connected to the rotor outer peripheral surface 600. When it is arranged on the inner peripheral side, the layout freedom of these passages can be improved.
A flat portion 614 is formed on the first vane 61 on the counterclockwise direction side. The plane portion 614 is formed to extend in the rotor radial direction, and has a plane extending in a straight line substantially coincident with the radial line passing through the rotation axis O when viewed from the X-axis direction, and the first shoe in the circumferential direction. 11 plane portions 113. The flat surface portion 614 has a rotor outer peripheral surface 600 at a base portion of the first vane 61 via a slight radius (a curvature radius that is substantially the same as or slightly smaller than the radius of the tip portion of the first shoe 11). It is continuous. On the outer diameter side (front end portion) of the first vane 61 on the counterclockwise direction side, a cutout portion is provided at a position that is continuous with the flat surface portion 614 and faces the build-up portion 114 of the first shoe 11 in the circumferential direction. 615 is provided. The notch 615 is substantially arc-shaped convex outward as viewed from the X-axis direction, has substantially the same curvature (curved surface shape) as the arc-shaped outer peripheral surface of the built-up portion 114, and surrounds a hole 70 described later. As described above, it is provided along the hole 70 over an angle range of about 90 degrees.
A flat surface portion 617 is formed on the first vane 61 in the clockwise direction. Similarly to the flat portion 614, the flat portion 617 has a flat surface that extends linearly in the rotor radial direction, and faces the flat portion 121 of the second shoe 12 in the circumferential direction. A cutout portion 618 is provided adjacent to the flat surface portion 617 on the inner diameter side (base portion) of the first vane 61 in the clockwise direction. The notch 618 is a concave groove formed in a shape obtained by scraping the base portion of the first vane 61 from the flat surface portion 617 toward the center in the circumferential direction of the vane 61, and is counterclockwise when viewed from the positive direction of the X axis. It has a substantially triangular shape convex in the turning direction. The notch 618 is formed at the same time as the vane member 6 is molded.
A hole 70 is formed through the first vane 61 in the X-axis direction. As shown in FIG. 5, the hole 70 includes a small diameter portion 701 provided on the X axis negative direction side and a large diameter portion 702 provided on the X axis positive direction side. The diameter of the inner peripheral surface of the small diameter portion 701 is set smaller than the diameter of the inner peripheral surface of the large diameter portion 702.
The thickness (circumferential dimension) of the portion (plane portion 614) adjacent to the counterclockwise direction side of the hole 70 in the first vane 61 is small enough to ensure the minimum strength around the hole 70 (thin wall). ) Is provided. In the first vane 61, the tip portion (notch portion 615) adjacent to the hole 70 on the outer diameter side is also provided with a similar thin wall. On the other hand, in the first vane 61, the circumferential dimension of the portion (planar portion 617) adjacent to the clockwise direction side of the hole 70 is larger (thick) than the counterclockwise direction side of the hole 70, Thereby, it is possible to provide the seal groove 611 on the clockwise direction side of the tip portion of the first vane 61. That is, the space around the hole 70 and the seal groove 611 is secured while securing a space for providing the seal groove 611.
A hole 75 is formed inside the first vane 61 in a substantially intermediate portion in the X-axis direction so as to extend linearly in the circumferential direction of the rotor. The hole 75 opens on the inner peripheral surface of the hole 70 at the connection portion between the small diameter portion 701 and the large diameter portion 702 at the end in the counterclockwise direction, and rotates clockwise in the clockwise direction at the first vane 61. Open to the direction side surface (plane portion 617).
On the other hand, a groove 76 is formed on the surface of the first vane 61 on the X axis negative direction side so as to extend linearly in the circumferential direction. The groove 76 opens to the inner peripheral surface of the hole 70 at the X axis negative direction end of the small diameter portion 701 at the end in the clockwise direction, and counterclockwise in the counterclockwise direction at the end of the first vane 61. Open to the side surface (planar portion 614).
A groove 605 is provided on the surface of the vane member 6 on the X axis positive direction side to a predetermined depth in the X axis direction. The groove 605 extends in the inner diameter direction from the large diameter portion 702 through the root portion of the first vane 61 and continues to the hole 800 of the front plate 8, and the X axis positive direction end of the hole 70 (large diameter portion 702). The hole 800 is a rectangular notch groove (radial groove) that connects the hole 800 in the rotor radial direction and communicates these holes.
The groove 111 opened in the clockwise direction surface (plane portion 113) of the first shoe 11 is opposed to the first vane 61 (the counterclockwise direction surface thereof) in the circumferential direction, and the first advance chamber. Communicate with A1. The groove 111 constitutes an advance side supply / discharge passage for supplying hydraulic oil to the first advance chamber A1 or discharging the hydraulic oil from the first advance chamber A1 (hereinafter, the groove 111 is referred to as the first advance chamber A1). 2 groove 111).
In addition, it is good also as a structure which has only one of an advance chamber and a retard chamber as a working chamber in which hydraulic fluid is supplied / discharged. Further, the number of advance chambers and retard chambers is not limited to 5, respectively. In other words, the number of shoes and vanes is not limited to 5 and may be other numbers.

Inside the vane member 6, holes 505, 506, 507, 508, and 509 are provided. The holes 505 to 509 are through holes formed so as to penetrate from the inner peripheral surface of the camshaft insertion hole 601 to the outer peripheral surface 600 of the rotor 60, and are formed to extend linearly from the inner peripheral side of the rotor 60 to the outer peripheral side. ing. The holes 505 to 509 are provided at positions slightly closer to the X axis negative direction side from the approximate center of the rotor 60 in the X axis direction. The holes 505 to 509 are provided adjacent to the first to fifth vanes 61 to 65 in the circumferential direction, respectively. When viewed from the X axis positive direction side, the holes 505 to 509 are provided to be inclined with respect to the rotor radial direction (radial straight line passing through the rotation axis O). Specifically, the holes 505 to 509 are positioned on the circumferential center line of the vanes 61 to 65, respectively, and the holes 505 to 509 are clockwise from the center line toward the outer circumferential side. Separate. The rotor outer peripheral side ends of the holes 505 to 509 open to the outer peripheral surface 600 of the rotor 60 at the root portions of the vanes 61 to 65 on the clockwise direction side, and communicate with the retarding chambers R1 to R5, respectively. The openings of the holes 505 to 509 are arranged as close to the vanes 61 to 65 as possible, and the holes 506 to 509 are not only the outer peripheral surface 600 of the rotor 60 but also partially. It opens also to the circumferential direction side surface of each vane 62-65. The hole 505 opens in the notch 618 of the first vane 61.
The holes 505 to 509 are provided at positions that overlap an annular groove 504 (described later) of the camshaft end 30 in the X-axis direction. Specifically, the holes 505 to 509 have a slightly smaller dimension in the X-axis direction than the annular groove 504, and are positioned approximately at the center of the annular groove 504 in the X-axis direction. Therefore, the inner diameter side ends of the holes 505 to 509 communicate with the annular groove 504. The holes 505 to 509 supply hydraulic oil from the supply / discharge oil passage (annular groove 504 or the like) on the camshaft 3 side to the retard chambers R1 to R5, respectively, or supply hydraulic fluid from the retard chambers R1 to R5. A retarded-side supply / discharge passage that discharges to the supply / discharge oil passage on the camshaft 3 side is configured (hereinafter, the holes 505 to 509 are referred to as retarded oil holes 505 to 509).

The flat portion 113 of the first shoe 11 and the flat portion 614 of the first vane 61 constitute a first stopper portion that restricts relative rotation of the vane member 6 in the counterclockwise direction (retard direction) with respect to the housing HSG. . In other words, the counterclockwise side surface (planar portion 614) of the first vane 61 and the clockwise side surface (planar portion 113) of the first shoe 11 are provided so as to be in contact with each other. When the vane member 6 tries to rotate more than a predetermined angle in the counterclockwise direction with respect to the housing HSG, as shown in FIG. 3, the flat surface portion 614 contacts the flat surface portion 113 in contact with each other, and this relative rotation is caused. Be regulated.
At this time, the other second to fifth vanes 62 to 65 are opposed to the adjacent shoes on the counterclockwise direction side through a slight gap and do not contact each other (maintain a non-contact state). ). That is, it is avoided that the volume of the second to fifth advance chambers A2 to A5 becomes zero in the rotation restricted state by the first stopper portion. Further, the second to fifth vanes 62 to 65 (inner peripheral side base end portions) respectively overlap with the clockwise side portions of the first grooves 516 to 519 in the circumferential direction, but the second to fifth advance chambers. The openings of the first grooves 516 to 519 in A2 to A5 are not completely closed by the second to fifth vanes 62 to 65, respectively, and the opening area is ensured by the slight gap. The edges on the clockwise direction side of the first grooves 516 to 519 are located slightly counterclockwise from the circumferential center of the second to fifth vanes 62 to 65, respectively, and the counterclockwise rotation of the vanes 62 to 65 is performed. The first grooves 516 to 519 overlap with 20 to 30% of the direction side.
On the other hand, in this rotation restricted state, the opening of the first groove 515 in the first advance chamber A1 is mostly blocked by the inner diameter side base end portion of the first vane 61. That is, the root portion of the first vane 61 largely closes even a slight opening (at the tip portion of the first shoe 11) of the first groove 515 in the advance chamber A1. Only a very small gap remains between the base portion, and the first groove 515 and the second groove 111 are opened in this gap. Further, the contact range (surface contact range) between the flat portion 614 and the flat portion 113 is provided from the outer peripheral side end of the first groove 515 and the second groove 111 to the outer peripheral side. The opening of the second groove 111 is closed by the flat portion 614. In the first embodiment, the vane 61 and the shoe 11 including the inner diameter side proximal end portion of the vane 61 are brought into surface contact with each other, thereby increasing the contact area of the first stopper portion and acting on the vane 61 by the contact. The surface pressure is suppressed and the strength of the first stopper portion is increased. On the other hand, there is a slight gap between the build-up portion 114 of the first shoe 11 and the cutout portion 615 of the first vane 61. It should be noted that the shape of the build-up portion 114 may be formed in a planar shape.
Further, the flat portion 121 of the second shoe 12 and the flat portion 617 of the first vane 61 constitute a second stopper portion that restricts the relative rotation of the vane member 6 in the clockwise direction (advance direction). That is, the side surface in the clockwise direction (plane portion 617) of the first vane 61 and the side surface in the counterclockwise direction (plane portion 121) of the second shoe 12 are provided so as to be in contact with each other. When the vane member 6 tries to rotate more than a predetermined angle in the clockwise direction with respect to the housing HSG, as shown in FIG. 4, the flat surface portion 617 contacts and contacts the flat surface portion 121 and the relative rotation is restricted. Is done. At this time, the other vanes 62 to 65 are opposed to the adjacent shoes on the clockwise direction side through a slight gap and do not contact each other (maintain a non-contact state). That is, it is avoided that the volume of the second to fifth retarding chambers R2 to R5 becomes zero in the rotation restricted state by the second stopper portion. Further, the openings of the retard oil holes 506 to 509 to the retard chambers R2 to R5 are not completely blocked by the tip surfaces of the shoes 13 to 15 and 11 (slidably contacting the rotor outer peripheral surface 600), respectively. The opening area is secured. For example, the counterclockwise direction side portion of the opening of the retarded oil hole 506 is partially provided on the surface on the clockwise direction side of the second vane 62, so that the third shoe 13, the second vane 62, Open in the slight gap between. Further, the clockwise side portion of the opening of the retarded oil hole 506 is in a position overlapping the tip surface of the third shoe 13 in the circumferential direction, but is provided on the counterclockwise direction side of the tip portion of the third shoe 13. Due to the rounded shape, a slight gap is formed in the radial direction in the overlapping portion in the circumferential direction between the two. Therefore, the opening of the retard oil hole 506 to the retard chamber R2 is prevented from being blocked by the tip of the shoe 13. The same applies to the other retarded angle oil holes 507 to 509.
Further, in this rotation restricted state, a gap exists between the root portion of the first vane 61 and the tip portion of the second shoe 12 due to a notch 618 provided in the first vane 61, and this gap The retard oil hole 505 is opened. Therefore, the opening of the retard oil hole 505 to the first retard chamber R1 is not blocked.
Further, in this rotation restricted state, the opening on the rotor outer peripheral side of each retarded oil hole 505 to 509 has the edge in the clockwise direction on the seal groove 117 to which the edge of each shoe 11 to 15 is provided. It is substantially coincident with the counterclockwise edge of 157 or is located on the counterclockwise direction side, and the openings of the retard oil holes 505 to 509 are respectively connected to the seal members S1 to S5. It is provided so as not to overlap in the direction (not opposed in the radial direction). In this rotation-restricted state, the first grooves 515 to 519 and the retarded oil holes 505 to 509 adjacent to each other with the seal grooves 117 to 157 sandwiched therebetween as seen from the X-axis direction extend substantially parallel to each other. Has been placed.

The hydraulic supply / discharge mechanism 5 selectively supplies the hydraulic oil to the advance chambers A1 to A5 or the retard chambers R1 to R5, or discharges the hydraulic oil from these hydraulic chambers, thereby allowing the vane member 6 to the housing HSG. Rotate forward and reverse by a predetermined angle. That is, by adjusting the supply and discharge of hydraulic oil and changing the oil chamber volume, the vane member 6 is rotated by a predetermined angle with respect to the housing HSG, and in this state, the rotational force is transmitted between the two. The rotation phase of the camshaft 3 with respect to the rotation of the crankshaft is changed. As shown in FIG. 2, the hydraulic supply / discharge mechanism 5 includes a pump P that is a hydraulic supply source, a hydraulic circuit, and a flow path switching valve 54 that is a hydraulic control actuator.
The hydraulic circuit has two passages, that is, a retard passage 50 that supplies and discharges hydraulic oil to and from each retard chamber R1 to R5, and an advance angle that supplies and discharges hydraulic oil to each advance chamber A1 to A5. A passage 51 is provided. A supply passage 52 and a drain passage 53 are connected to both passages 50 and 51 via a passage switching valve 54. The supply passage 52 is provided with a pump P that pumps oil in the oil pan 55 to the flow path switching valve 54. The pump P is rotationally driven by the crankshaft of the engine, and for example, a unidirectional variable displacement vane pump can be used. The downstream end of the drain passage 53 communicates with the oil pan 55.
The camshaft 3, the vane member 6, and the housing HSG (rear plate 9) are formed with a part of the retard passage 50 and the advance passage 51.
The camshaft end 30 is provided with grooves 500, 504, 510, 514, holes 502, 512 and holes 501, 503, 511, 513. The grooves 500 to 514 are annular grooves formed to a predetermined depth over the entire circumferential range of the outer peripheral surface of the end portion 30, and include retardation passage grooves 500 and 504 and advance passage grooves 510 and 514. The widths in the X-axis direction of the grooves 500 to 514 are substantially the same. The grooves 500 and 510 are provided on the negative X-axis side of the end portion 30 and are disposed in the cylinder head, and are arranged in this order in the negative X-axis direction. The grooves 504 and 514 are provided on the X axis positive direction side of the end 30 and are arranged in this order in the X axis negative direction. The groove 504 is disposed in the camshaft insertion hole 601 of the vane member 6, and the groove 514 is disposed in the camshaft insertion hole 90 (X-axis positive direction side) of the rear plate 9.
The holes 502 and 512 are axial passages formed in the end portion 30 so as to extend in the X-axis direction, and include a retard passage 502 and an advance passage 512. The passages 502 and 512 have a predetermined diameter (smaller than the bolt hole 32) and open to the camshaft end surface 300, respectively. With the end 30 inserted and installed in the camshaft insertion hole 601, the opening in the end surface 300 of the passages 502 and 512 is blocked by the bottom surface of the camshaft insertion hole 601 on the X axis positive direction side.
The holes 501 to 513 are radial passages formed in the end portion 30 so as to extend in a direction substantially perpendicular to the X axis, and have retardation passages 501 and 503 and advance passages 511 and 513. . The passage 501 is between the groove 500 and the axial passage 502, the passage 503 is between the groove 504 and the axial passage 502, the passage 511 is between the groove 510 and the axial passage 512, and the passage 513 is the groove 514. And the axial passage 512 are respectively formed through and connecting them.
The retarding passage 50 from the flow path switching valve 54 first communicates with the annular groove 500 when connecting to the oil passage in the camshaft 3 (end 30), which is a rotating body. The annular groove 500 communicates with the axial passage 502 via the radial passage 501, and the axial passage 502 communicates with the annular groove 504 via the radial passage 503. Similarly, the advance passage 51 from the flow path switching valve 54 communicates with the annular groove 510 at the end 30, and the annular groove 510 is annular through the radial passage 511, the axial passage 512, and the radial passage 513. It communicates with the groove 514.
Further, the holes 505 to 509 are provided in the vane member 6 as a retard side passage, and the first grooves 515 to 519 and the second groove 111 are provided in the rear plate 9 as an advance side passage.
With the end 30 inserted and installed in the camshaft insertion hole 601, the retard side passages 501 to 503 in the end 30 are connected to the holes 505 to 509 of the vane member 6 through the annular groove 504, The retard chambers R1 to R5 communicate with each other through the holes 505 to 509. Further, the advance side passages 511 to 513 in the end portion 30 communicate with the first grooves 515 to 519 of the rear plate 9 via the annular groove 514 (and the annular groove 900), and the first groove 515 and the second groove. The first advance angle chamber A1 communicates with the first advance angle chamber 111 via the 111 and communicates with the second to fifth advance angle chambers A2 to A5 via the first grooves 515 to 519. By providing the annular groove 504, the degree of freedom in layout of the holes 505 to 509 in the vane member 6 in the circumferential direction of the rotor is improved. By providing the annular groove 514, the plate periphery of the first grooves 515 to 519 in the rear plate 9 is improved. Layout flexibility in the direction has been improved.
The camshaft insertion hole 601 may not be provided. In the first embodiment, the camshaft insertion hole 601 is provided, so that the radial positioning of the vane member 6 with respect to the camshaft 3 is easy. Connection with the path (holes 505 to 509) is easy.
The flow path switching valve 54 is a 4-port 3-position direction control valve (two-way valve) that controls the hydraulic pressure supplied to and discharged from the advance chambers A1 to A5 or the retard chambers R1 to R5. Solenoid valve. The flow path switching valve 54 has a valve body fixed to the engine side (cylinder head), a solenoid SOL fixed to the valve body, and a spool valve body slidably provided inside the valve body. ing. The valve body includes a supply port 540 that communicates with the supply passage 52, a first port 541 that communicates with the retard passage 50, a second port 542 that communicates with the advance passage 51, and a drain port 543 that communicates with the drain passage 53. Is formed. The solenoid SOL pushes and moves the spool valve body by energizing the electromagnetic coil. The electromagnetic coil is connected to the controller CU via a harness. As the spool valve element moves, the first port 541 and the second port 542 are opened and closed. When the solenoid SOL is not energized, the spool valve body communicates the supply port 540 (supply passage 52) and the second port 542 (advance passage 51) with the spring force of the return spring RS, and the first port 541. It is biased to a position where the (retard passage 50) and the drain port 543 (drain passage 53) communicate with each other. On the other hand, in a state where the solenoid SOL is energized, the spool valve body is opposed to the spring force of the return spring RS by the control current from the controller CU, and the supply port 540 (supply passage 52) and the first port 541 (slow). The angular passage 50) is communicated and the second port 542 (advanced passage 51) and the drain port 543 (drain passage 53) communicate with each other, or the movement is controlled to a predetermined intermediate position. .
The controller CU is an electronic control unit, and signals from various sensors such as a crank angle sensor that detects the engine speed, an air flow meter that detects the intake air amount, a throttle valve opening sensor, and a water temperature sensor that detects the engine water temperature. To detect the current engine operating state. Further, the controller CU outputs a pulse control current to the solenoid SOL of the flow path switching valve 54 in accordance with the detected engine operating state, and performs flow path switching control, so that the advance chambers A1 to A5 or the retard angle are controlled. The hydraulic oil is selectively supplied to and discharged from the chambers R1 to R5.

  Between the vane member 6 (first vane 61) and the rear plate 9, there is provided a lock mechanism 7 that restrains the free rotation of the vane member 6 with respect to the rear plate 9 (housing HSG) and releases the restraint. ing. The device 1 is configured such that the operation (relative rotation) is locked by the lock mechanism 7 at a predetermined initial rotation phase, specifically, at the most retarded angle position where rotation is restricted by the first stopper portion. . The lock mechanism 7 has a lock piston 71, an engagement recess 730 provided in the rear plate 9, and the lock piston 71 is advanced and engaged with the engagement recess 730 according to the state of the engine. And an engagement / disengagement mechanism that releases the engagement by retreating. FIG. 5 is a partial cross-sectional view substantially corresponding to the BB cross section of FIG. 3 and shows the operating state of the lock mechanism 7 when the engine is stopped (when the engine is started).

The lock piston 71 is an engaging member (stopper piston), and is formed in a bottomed cylindrical pin shape from an iron-based metal material. The lock piston 71 is installed inside the hole 70 of the first vane 61 so as to reciprocate in the X-axis direction (which is the direction of the rotation axis O), and moves forward and backward toward the rear plate 9 according to the state of the engine ( The first vane 61 is provided so as to be able to appear and disappear in the negative direction of the X axis. That is, the hole 70 is a sliding hole that slidably accommodates the lock piston 71 and is a hollow cylindrical cylinder.
The lock piston 71 includes a sliding portion 710 that slides with respect to the sliding hole 70 and an engaging portion 714 that is a tip portion of the lock piston 71 that is provided inside and outside the sliding hole 70. The sliding portion 710 has a bottomed cylindrical shape that opens toward the positive x-axis direction, and includes a small diameter portion 711 and a large diameter portion 712. The large-diameter portion 712 is an annular flange portion formed at the base end portion of the lock piston 71, that is, the end on the X axis positive direction side. The large-diameter portion 712 is installed inside the large-diameter portion 702 so that the outer periphery thereof is slidable with respect to the inner periphery of the large-diameter portion 702 of the sliding hole 70. The small diameter portion 711 is installed inside the small diameter portion 701 so that the outer periphery thereof is slidable with respect to the inner periphery of the small diameter portion 701 of the sliding hole 70. On the X axis negative direction side of the bottom portion 713 of the small-diameter portion 711, an engaging portion 714 is provided in a substantially truncated cone shape through a step with the bottom portion 713. The engaging portion 714 has a substantially trapezoidal cross section in the axial direction, and has a tapered surface (inclined surface) with a small diameter toward the tip on the X axis negative direction side on the outer periphery.

On the other hand, a bottomed engagement recess 730 that does not penetrate the rear plate 9 is formed on the surface of the rear plate 9 on the X axis positive direction side. The engagement recess 730 is a lock hole (stopper hole) that opens to the surface of the rear plate 9 on the X axis positive direction side and can be engaged with the engagement portion 714. The engaging recess 730 is formed by fitting a bottomed cup-shaped sleeve 73 formed of an iron-based metal material into the fitting hole 96 of the rear plate by press fitting.
The depth of the engaging recess 730 in the X-axis direction is substantially the same as the length of the engaging portion 714 in the X-axis direction, and the diameter of the engaging recess 730 is slightly larger than the diameter of the engaging portion 714. Yes. The engagement recess 730 has a substantially trapezoidal cross section cut by a plane passing through the axis of the sleeve 73, and gradually increases in diameter toward the opening on the X axis positive direction side. In other words, the engagement recess 730 has an inclined surface and is provided with a tapered surface having a smaller diameter toward the bottom on the X-axis negative direction side. The inclination of the inner peripheral surface (inclined surface) of the engaging recess 730 with respect to the X axis is substantially equal to the inclination of the outer peripheral surface (inclined surface) of the engaging portion 714 with respect to the X axis.
The position of the engaging recess 730 is provided such that the relative rotation angle between the housing HSG and the vane member 6 is in an optimum phase for engine starting when the engaging portion 714 is engaged with the engaging recess 730. Specifically, the engagement recess 730 is provided at a position that is substantially coincident with the distal end (engagement portion 714) of the lock piston 71 when viewed from the X-axis direction at the most retarded position in FIG. . In other words, when the vane member 6 rotates relative to the most retarded angle and the rotation is restricted by the first stopper portion, the position of the lock piston 71 (engagement portion 714) and the engagement recess when viewed from the X-axis direction. 730 positions overlap. At this time, as shown in FIG. 5, the position of the shaft center of the engaging recess 730 in the circumferential direction of the rotor is slightly in the counterclockwise direction (on the first shoe 11 side) with respect to the shaft center of the engaging portion 714. It is provided so as to be offset.

The engagement / disengagement mechanism includes a coil spring 74 that is an urging means for engagement, and first and second pressure receiving chambers 77 and 78 (communication hole 75 and communication groove 76) that are urging means for release. Yes. The coil spring 74 is an elastic member that constantly urges the lock piston 71 toward the X-axis negative direction side, that is, the engagement recess 730 side. The coil spring 74 is elastically mounted (installed in a compressed state) in the hole 70 (large diameter portion 702), and the end on the X axis positive direction side is the surface of the front plate 8 on the X axis negative direction side. The X-axis negative direction end is in contact with the rear end portion (bottom portion 713) of the lock piston 71.
The sliding hole 70 is provided with a pressure receiving chamber for generating an oil pressure acting on the lock piston 71. Specifically, the inner peripheral surface of the large diameter portion 702 (including the X axis positive direction end surface of the small diameter portion 701) in the sliding hole 70 and the X piston negative direction end surface of the large diameter portion 712 in the lock piston 71 are included. A first pressure receiving chamber 77 is defined between the outer peripheral surface of the small diameter portion 711. In the locked state where the surface of the engaging portion 714 (the tip surface and the inclined surface on the negative side of the X axis) and the surface of the rear plate 9 on the positive side of the X axis (the engaging portion 714 is fitted in the engaging recess 730). The second pressure receiving chamber 78 is defined between the inner peripheral surface and the bottom surface of the sleeve 73. The first vane 61 is provided with the hole 75 and the groove 76 as a communication path for guiding the hydraulic pressure of the working chamber to the first and second pressure receiving chambers 77 and 78. The retarding chamber R 1 and the first pressure receiving chamber 77 are connected via the communication hole 75 and are always in communication, and the hydraulic pressure in the retarding chamber R 1 is guided to the first pressure receiving chamber 77. Via the communication groove 76, the advance chamber A1 and the X-axis negative direction end of the sliding hole 70 are connected and always communicated, and the hydraulic pressure in the advance chamber A1 is guided to the second pressure receiving chamber 78. (In the locked state of FIG. 5, the hydraulic pressure in the second groove 111 is directly introduced to the second pressure receiving chamber 78 through the communication groove 76.) Thus, the retard chamber R1 and the advance chamber A1 are selectively used. The supplied hydraulic oil is guided to the first pressure receiving chamber 77 and the second pressure receiving chamber 78 through the communication hole 75 and the communication groove 76, respectively, and both urge the lock piston 71 in the backward direction on the X axis positive direction side. Generate oil pressure.
When the vane member 6 rotates relative to the most retarded angle and the rotation is restricted by the first stopper portion, the position of the lock piston 71 and the position of the engagement recess 730 overlap when viewed from the X-axis direction. Can move in the negative direction of the X-axis. At this time, the spring force of the coil spring 74 acts to assist the engaging portion 714 to advance from the first vane 61 (sliding hole 70) and fit into the engaging recess 730. When the lock piston 71 engages with the engagement recess 730, the relative rotation between the rear plate 9 and the vane member 6, that is, the relative rotation between the housing HSG and the camshaft 3 is restricted (locked). On the other hand, the lock piston 71 receives an oil pressure on the X axis positive direction side in the large diameter portion 712 by the hydraulic pressure supplied from the retard chamber R1 into the first pressure receiving chamber 77 through the communication hole 75. Further, the lock piston 71 is hydraulically moved in the positive direction of the X-axis at the engaging portion 714 by the hydraulic pressure supplied into the second pressure receiving chamber 78 from the advance chamber A1 or the second groove 111 via the communication groove 76. Receive. In any of the above oil pressures, the lock piston 71 moves in the positive direction of the X axis against the spring force of the coil spring 74, and the engaging portion 714 retreats from the engaging recess 730 to enter the sliding hole 70. Acts to assist in fitting. As a result, the engagement between the lock piston 71 and the engagement recess 730 is released. Thus, while the coil spring 74 functions as a lock state maintaining mechanism, the communication hole 75 and the communication groove 76 function as a release hydraulic circuit.
A back pressure chamber 72 of the lock piston 71 is provided inside the sliding hole 70. The back pressure chamber 72 is a low pressure chamber provided on the X axis positive direction side of the sliding hole 70, the surface on the X axis negative direction side of the front plate 8, the inner peripheral surface of the sliding hole 70, and the lock piston. 71 (sliding portion 710). The back pressure chamber 72 communicates with the hole 800 of the front plate 8 via the radial groove 605, and communicates with the outside (outside air) of the apparatus via the hole 800, thereby releasing to atmospheric pressure (low pressure space). (See FIG. 2). In other words, the radial groove 605 is a breathing groove formed on the end surface of the vane member 6 on the X axis positive direction side, functions as an air vent hole, and releases the pressure of the back pressure chamber 72 to maintain a low pressure. The back pressure relief part for doing is comprised.

[Operation of Example 1]
Hereinafter, the operation of the device 1 will be described.
(Phase conversion action)
First, the phase conversion action of the device 1 will be described. In addition, the following control content can be changed variously. FIG. 3 shows a state when the engine is stopped (when the engine is started), and FIG. 4 shows a state when the engine is operating.
When the engine is started, the lock mechanism 7 preliminarily constrains the vane member 6 to the initial position on the retard side, specifically, the most retarded angle position so that the optimum relative conversion angle is obtained when the engine is started (FIG. 3). ). For this reason, when the engine is started by turning on the ignition switch, good startability can be obtained by smooth cranking.
In a predetermined low rotation and low load region after engine startup, no control current is output from the controller CU to the flow path switching valve 54. The spool valve body remains in a position where the supply port 540 and the second port 542 communicate with each other and the first port 541 and the drain port 543 communicate with each other by the spring force of the return spring RS. Therefore, the hydraulic oil discharged from the pump P and flowing into the valve body from the supply passage 52 via the supply port 540 flows into the advance passage 51 from the second port 542, and from here the axial direction of the camshaft 3 Through the passage 512, the radial passage 511 and the like and the first grooves 515 to 519 of the rear plate 9, they are supplied to the advance chambers A1 to A5. When hydraulic oil is supplied to the first groove 515, the lock state by the lock mechanism 7 is released, the vane member 6 is allowed to freely rotate, and the valve timing can be arbitrarily changed. After unlocking, the vane member 6 rotates from the position shown in FIG. 3 in the rotation direction of the housing HSG (the arrow direction in FIG. 3) with respect to the housing HSG by the hydraulic pressure supplied to the advance chambers A1 to A5. The rotational phase of the camshaft 3 relative to the crankshaft is changed to the advance side. As a result, the opening / closing timing of the intake valve is advanced, the valve overlap during which both the intake valve and the exhaust valve are opened increases, and the combustion efficiency due to the use of inertial intake at such low rotation and low load is increased. As a result, engine rotation is stabilized and fuel consumption is improved. As shown in FIG. 4, when the vane member 6 rotates relative to the most advanced position where the volumes of the advance chambers A1 to A5 are maximized and the volumes of the retard chambers R1 to R5 are minimized, the valve overlap occurs. Maximum.
When the operating state of the engine shifts to, for example, a high rotation / high load region, a control current is output from the controller CU to the flow path switching valve 54. The spool valve body moves to a position where the supply port 540 communicates with the first port 541 and the second port 542 communicates with the drain port 543 against the spring force of the return spring RS. Therefore, the hydraulic oil discharged from the pump P flows into the retarded passage 50 from the first port 541 of the flow path switching valve 54, and the vane member 6 and the axial passage 502 and the radial passage 501 of the camshaft 3. Since the oil is supplied to the retard chambers R1 to R5 through the retard oil holes 505 to 509, the internal pressure of the retard chambers R1 to R5 increases. On the other hand, the hydraulic oil in each advance chamber A1 to A5 is discharged to the oil pan 55 via the advance passage 51 and the drain passage 53, and the internal pressure in each advance chamber A1 to A5 is reduced. When the internal pressures of the retard chambers R1 to R5 are larger than the internal pressures of the advance chambers A1 to A5, the vane member 6 is counterclockwise in the direction opposite to the rotation direction of the housing HSG (the arrow direction in FIG. 3). Then, it rotates relative to the housing HSG and changes the rotational phase of the camshaft 3 relative to the crankshaft to the retard side. As a result, the opening / closing timing of the intake valve is controlled to the retard side, the valve overlap is reduced, and the output of the engine at the time of such high rotation and high load can be improved. As shown in FIG. 3, when the vane member 6 rotates relative to the most retarded position where the volumes of the retard chambers R1 to R5 are maximized and the volumes of the advance chambers A1 to A5 are minimized, the valve overlap occurs. Minimal.
Furthermore, for example, when the engine shifts to the middle rotation load region, the controller CU controls the flow path switching valve 54 to hold the spool valve body at the intermediate movement position. As a result, the internal pressures of the retard chambers R1 to R5 and the advance chambers A1 to A5 are kept substantially constant, and the vane member 6 is controlled to the intermediate rotation position. Therefore, optimal valve timing control in the middle rotation / middle load range is possible, and both fuel consumption and engine output can be satisfied.
During engine operation, specifically, during rotation of the camshaft 3, the camshaft 3 is caused by friction due to the rotational reaction force transmitted to the cam of the camshaft 3 from the valve spring that biases the intake valve in the closing direction. An alternating torque (reverse torque) is generated. That is, due to the cam shape, a negative torque (counterclockwise) that prevents the camshaft 3 from rotating (clockwise) and a positive torque that assists the rotation of the camshaft 3 (clockwise) are: It acts on the camshaft 3 alternately. The alternating torque is offset to the negative torque side as a whole. That is, when the positive torque and the negative torque generated at each rotation cycle of the camshaft 3 are integrated over time, the camshaft 3 becomes negative, and the negative torque acts on the camshaft 3 on average.
When the engine stops, the operation of the pump P is stopped. Further, the energization from the controller CU to the flow path switching valve 54 is interrupted. Accordingly, the supply of hydraulic pressure to the advance chambers A1 to A5 and the retard chambers R1 to R5 is stopped. For this reason, immediately after the engine is stopped, the vane member 6 is rotated relative to the housing HSG by the friction generated in the camshaft 3 (alternating torque offset to the negative torque side) (the direction of the arrow in FIG. 3). ) Tries to rotate in the opposite direction, that is, the retard side. Therefore, after the engine is stopped, the vane member 6 is moved to a predetermined initial position suitable for starting the engine (re) in advance by the friction (alternating torque) of the camshaft 3, that is, the most retarded position shown in FIG. To do. In other words, the valve timing is a phase suitable for engine (re) starting. At this time, the lock mechanism 7 operates to restrain the rotation of the vane member 6 relative to the housing HSG.
As described above, in the apparatus 1, when the engine stops, the vane member 6 is rotated to the initial position on the retard side with respect to the housing HSG by the alternating torque, so that the apparatus 1 is initialized even when the engine is restarted. It can be controlled from the position.

(Operation of locking mechanism)
As described above, by operating the lock mechanism 7, the device 1 can be controlled from the initial position (FIG. 3) regardless of the presence or absence of the hydraulic pressure. Therefore, the fluttering of the vane member 6 that can be generated by the alternating torque acting on the camshaft 3 when the engine is started is suppressed, and abnormal noise (sounding sound) is generated due to the collision between the vanes 61 to 65 and the housing HSG (shoes 11 to 15). Can be suppressed. Further, the engine or device 1 can be stably operated while knocking or the like is suppressed. This is the same not only when the engine is started but also when the engine is idling when hydraulic pressure is not generated so much. In the first embodiment, the lock position is set as the rotation retarding position on the most retarded angle side. However, the present invention is not limited to this. It is good.
Specifically, when the vane member 6 rotates relative to the housing HSG relative to the most retarded angle side, the position of the lock piston 71 and the position of the engagement recess 730 overlap. For this reason, when the engine is stopped, the engaging portion 714 is advanced by the spring force of the coil spring 74 and is engaged with the engaging recess 730. Thereby, the lock piston 71 restricts free relative rotation of the vane member 6.
In this locked state, the second groove 111 and the communication groove 76 face each other in the circumferential direction and communicate with each other. That is, even when the volume of the advance chamber A1 is minimum, the first groove 515 is connected to the communication groove 76 via the second groove 111 and communicates with the second pressure receiving chamber 78. Therefore, when the hydraulic oil is supplied to the advance passage 51, the pressure in the second pressure receiving chamber 78 is increased by the hydraulic oil supplied from the first groove 515, and accordingly, the lock piston 71 (the engaging portion 714). ) Receives hydraulic pressure acting on the positive side of the X axis. When the oil pressure becomes larger than the spring force of the coil spring 74, the lock piston 71 moves (retreats) in the X-axis positive direction. When the engaging portion 714 is completely removed from the engaging recess 730, the locked state is released.
If the hydraulic oil continues to be supplied to the advance passage 51 after the lock is released, the hydraulic pressure is supplied from the advance chamber A1 to the second pressure receiving chamber 78 through the communication groove 76, so that the unlocked state is maintained. When the device 1 is in operation, the hydraulic oil is discharged from the advance passage 51 and supplied to the retard passage 50. Then, the hydraulic oil is supplied from the advance chamber A1 to the second pressure receiving chamber 78 through the communication groove 76. The hydraulic pressure decreases. On the other hand, as the hydraulic pressure of the retarding chamber R1 increases, this hydraulic pressure is supplied to the first pressure receiving chamber 77 via the communication hole 75 and acts as an oil pressure on the pressure receiving surface of the large diameter portion 712 of the lock piston 71. As a result, the release state in which the lock piston 71 has come out of the engagement recess 730 against the spring force of the coil spring 74 is maintained.
As described above, in the first embodiment, the vane member 6 (vane 61) is provided with the lock piston 71 that can be moved in and out with respect to the housing HSG (rear plate 9), and the housing HSG (rear plate 9) includes An engagement recess 730 (lock hole) with which the lock piston 71 can be engaged is formed, and the lock piston 71 is engaged with or released from the engagement recess 730 depending on the state of the engine. Therefore, the mechanism is simpler than the case where a clutch mechanism or a lever mechanism is used as a lock means for restricting the relative rotation of the vane member 6 and operating the device 1 from the initial position, and the lock operation can be performed while reducing the cost. Reliability can be secured. The lock mechanism 7 (lock piston 71) may be installed on the housing HSG side and locked with the vane member 6. In the first embodiment, by installing the lock piston 71 on the vane member 6, it is possible to suppress an increase in the size of the housing HSG (device 1) as compared with the case where the lock piston 71 is provided on the housing HSG.
In the vane member 6, the lock piston 71 may be provided not on the vane 61 but on the rotor 60. In the first embodiment, by providing the lock piston 71 on the vane 61, the radial enlargement of the rotor 60 can be suppressed, thereby suppressing the radial enlargement of the device 1 while securing the pressure receiving area of the vanes 61 to 65. Is possible.
The lock piston 71 may be provided on the vanes 62 to 65 other than the vane 61 that contacts the shoe 11.
Further, the lock piston 71 may advance or retreat in a direction other than the rotation axis O, for example, in the radial direction of the housing HSG. In other words, the cylinder that houses the lock piston 71 may be formed in the housing radial direction, for example, other than the rotation axis direction. In the first embodiment, the lock piston 71 is provided so as to be able to appear and retract with respect to the sealing member (rear plate 9). In other words, the sliding hole 70 of the lock piston 71 is formed to extend in the direction of the rotation axis O (X-axis direction), and the tip (engagement portion 714) of the lock piston 71 protrudes and retracts in the direction of the rotation axis O. By configuring the lock piston 71 to operate in the rotation axis direction in this way, it is possible to suppress an increase in the radial direction of the device 1. Further, it is possible to suppress the centrifugal force due to the rotation of the vane member 6 from affecting the operation of the lock mechanism 7.
The lock piston 71 may be provided so as to be able to appear and retract with respect to the front plate 8. In the first embodiment, since the lock piston 71 is provided so as to be able to appear and retract with respect to the rear plate 9, the apparatus 1 can be reduced in the axial direction. That is, the sealing member on the side where the engagement concave portion into which the lock piston 51 protruding and retracting in the axial direction from the vane member 6 is inserted is formed thick in order to form the engagement concave portion (install the sleeve). It is necessary to configure. On the other hand, in order to fasten the sealing members 8 and 9 and the housing body 10 with the bolts b1 to b5, it is necessary to form a female screw hole in either of the sealing members 8 and 9. Since the female screw hole needs to have a certain length, the sealing member on the side where the female screw hole is formed needs to be thick. In the first embodiment, the rear plate 9 is provided with female thread portions 91 to 95. Therefore, since it is not necessary to form a female screw hole or the like in the front plate 8, the front plate 8 may be thin. On the other hand, the engagement recess 730 is provided in the rear plate 9 which must be thick to form the female screw portions 91 to 95. In other words, in order to form the engagement recess 730 (install the sleeve 73), the internal thread portions 91 to 95 are provided on the rear plate 9 that must be thick. Thus, since both the engagement recess 730 and the female thread portions 91 to 95 are formed in the rear plate 9, the axial dimension of the device 1 can be reduced.
The lock mechanism 7 includes an elastic member (coil spring 74) as an urging unit for the lock piston 71, and the lock piston 71 is caused to protrude and retract with respect to the vane member 6 using the urging force of the elastic member. For example, when the engine is stopped, when the vane member 6 is rotated to a predetermined initial position by the alternating torque, the lock piston 71 is automatically engaged with the engagement recess 730 by the urging force of the coil spring 74. Therefore, since a special actuator for the locking operation is not required, the mechanism can be simplified. Note that an elastic member other than the coil spring, such as a leaf spring, may be used as the biasing member of the lock piston 71.
The distal end (engagement portion 714) of the lock piston 71 has a substantially truncated cone shape and is provided so as to have a smaller diameter toward the negative X-axis direction (engagement recess 730). Easy to engage with. Since the engagement recess 730 is also provided with a larger diameter toward the opening on the X axis positive direction side, the engagement portion 714 is easily engaged. Therefore, the lock is performed smoothly.
Further, both the engaging portion 714 and the engaging recess 730 have a tapered surface (inclined surface). Then, at the relative rotation restriction position by the first stopper portion in FIG. 3, the shaft center of the engagement recess 730 rotates in the counterclockwise direction (the first shoe 11 side) with respect to the shaft center of the engagement portion 714. There is a slight offset in the direction. For this reason, when the lock piston 71 is inserted into the engagement recess 730 at the time of locking, the inclined surfaces of the two come into contact with each other in the clockwise direction, and at this time, the first vane 61 is moved counterclockwise (the first shoe). 11), a component force is generated (hereinafter referred to as a wedge effect). Therefore, when the lock piston 71 is engaged with the engagement recess 730, the first vane 61 is pressed against the first shoe 11, so that the vane member 6 is more reliably moved to the relative rotation restriction position (the most retarded position that is the initial position). ) Can be fixed. In addition, as a configuration for contacting both the inclined surfaces, the shapes of the engaging portion 714 and the engaging recess 730 may be changed as appropriate in addition to offsetting the axis. When the axis is offset as in the first embodiment, the configuration is simple. In addition, an inclined surface that generates the above-described component force during engagement may be provided only in one of the engagement portion 714 and the engagement recess 730. Also in this case, the wedge effect can be obtained. When the inclined surfaces are provided on both sides as in the first embodiment, wear can be reduced while effectively obtaining the pressing force.
In the first embodiment, fluid pressure is applied to the lock piston 71 so that the lock piston 71 is withdrawn from the engagement recess 730 and the lock is released. May be. When the lock is released by the pressure of the hydraulic oil supplied to the working chamber as in the first embodiment, the lock is released using the hydraulic pressure of the device 1 as it is. A special actuator is not required and the mechanism can be simplified.
Further, the back pressure relief portion allows the lock piston 71 to move smoothly without being affected by the pressure in the back pressure chamber 72 when the device 1 is operated. That is, when the engagement portion 714 is disengaged from the engagement recess 730 and the lock piston 71 moves in the positive direction of the X axis and the volume of the back pressure chamber 72 is to be reduced, the air in the back pressure chamber 72 It is transmitted to the low-pressure space outside the device via the pressure relief part. Therefore, the inside of the back pressure chamber 72 is maintained at a low pressure. In the back pressure chamber 72, hydraulic oil that has leaked from the gap around the back pressure chamber 72 is accumulated. This oil is also discharged out of the apparatus through the back pressure relief. Therefore, when the volume of the back pressure chamber 72 is to be reduced, the back pressure is released without being hindered by air or oil. Therefore, good operation of the lock piston 71 (sliding in the sliding hole 70) is ensured in all relative rotation ranges of the vane member 6, and unlocking is smoothly performed.
In addition, it is good also as a structure which cancels | releases a lock | rock with the hydraulic_pressure | hydraulic of only one of the advance side and the retard side. For example, the communication hole 75 may be omitted, and the lock piston 71 may be released only when the hydraulic pressure in the advance chamber A1 (first groove 515) is supplied to the second pressure receiving chamber 78. In the first embodiment, when the device 1 is operated, the lock piston 71 is always held in the released state when the hydraulic pressure is guided to either the advance side or the retard side. That is, according to the state of the engine, the retarded hydraulic pressure is guided to the first pressure receiving chamber 77 and the advanced hydraulic pressure is guided to the second pressure receiving chamber 78, respectively. Against this, the lock piston 71 operates in the release direction. Therefore, since it is suppressed that engagement / release is repeated each time the vane member 6 rotates in the advance direction or the retard direction, not only can the operation of the device 1 be made smooth, but also the number of operations of the lock piston 71. This can reduce the durability of the apparatus 1.
Specifically, the sliding hole 70 is a cylinder having a different diameter (stepped), and the lock piston 71 is provided with a large diameter portion 712 and a small diameter portion 711 corresponding thereto, and the lock piston 71 has a different diameter (step). (With) pin. A small-diameter portion 711 and a large-diameter portion 712 are slidably provided on the inner periphery of the small-diameter portion 701 of the sliding hole 70 and on the inner periphery of the large-diameter portion 702, respectively. Thus, a first pressure receiving chamber 77 is defined in the sliding hole 70. In this way, by using different diameter (stepped) cylinders and pins, it is possible to easily provide the first pressure receiving chamber 77 and the second pressure receiving chamber 78 separately in a liquid-tight manner. On the other hand, it is possible to easily realize a configuration in which the oil pressures from the advance chamber A1 and the retard chamber R1 are separately applied. Note that the first and second pressure receiving chambers 77 and 78 can be arbitrarily formed or arbitrarily positioned by appropriately adjusting the shape of the cylinder (sliding hole 70) and the lock piston 71 and the configuration of the oil passage 75 and the groove 76. Or may be provided. Further, the hydraulic pressure of the advance chamber A1 may be guided to the first pressure receiving chamber 77, and the hydraulic pressure of the retard chamber R1 may be guided to the second pressure receiving chamber 78. In other words, the communication groove 76 may be constituted by a hole (similar to the communication hole 75), and the communication hole 75 may be constituted by a groove (similar to the communication groove 76). In the first embodiment, since the second groove 111 is opposed to the communication groove 76 in the circumferential direction and communicated with the second pressure receiving chamber 78 via the communication groove 76, the dimension of the second groove 111 in the X-axis direction is set. Only the opening of the communication groove 76 is suppressed, thereby suppressing a decrease in strength around the seal groove 117 as described later.

(Operation of positioning means)
When assembling the constituent members of the apparatus 1, the positioning means rotates the rear plate 9 relative to the housing body 10, that is, positions the housing body 10 and the rear plate 9 in the circumferential direction. By fitting the convex portion 97 of the rear plate 9 into the concave portion 116 of the housing main body 10, the rotational position of the housing main body 10 with respect to the rear plate 9 is adjusted, and the circumferential positioning of both is performed. The dimensions of the convex portion 97 and the concave portion 116 are set to dimensions that do not cause backlash in the circumferential direction of the housing body 10 and the rear plate 9 in a state where the convex portion 97 is fitted in the concave portion 116. By this positioning, the internal thread portions (bolt holes) 91 to 95 of the rear plate 9 are substantially coaxial with the bolt holes 110 to 150 of the housing body 10. Further, the engagement recess 730 is slightly offset (slightly offset) from the sliding hole 70 (lock piston 71) in a state where the first vane 61 (plane portion 614) is in contact with the first shoe 11 (plane portion 113). While being substantially coaxial. In other words, the concave portion 116 and the convex portion 97 constitute positioning means for adjusting and determining the circumferential relative position between the lock piston 71 and the engaging concave portion 730. As a result, the lock piston 71 and the engagement recess 730 are accurately positioned, so that a smooth engagement action of the lock piston 71 including the wedge effect is obtained.
Specifically, the lock piston 71 is provided on the vane 61 that comes into contact with the shoe 11 provided with positioning means (recess 116). Therefore, the engaging recess 730 is provided in the vicinity of the shoe 11, and the positioning means (the recess 116 and the protrusion 97 on the rear plate 9 fitted to the engaging portion 730) is located at a position close to the engaging recess 730. Will be provided. For this reason, it is possible to more accurately position the shoe 11 (the lock piston 71 in the vane 61 contacting the shoe) with respect to the engagement recess 730 than in the case where the positioning means is provided in the other shoes 12-15. Therefore, a smoother engaging action of the lock piston 71 is obtained. For example, the wedge effect can be obtained more reliably.
As positioning means, the housing body 10 (shoe 11) may be provided with a convex portion and the rear plate 9 may be provided with a concave portion. Further, as in the first embodiment, a pin may be inserted and installed in the hole to form a positioning convex portion, or a jig may be used. In this case, the positioning convex portion (pin) is omitted and the apparatus is used. It is possible to further reduce the weight. For example, the rear plate 9 may be provided with a concave portion (or hole) instead of the convex portion 97, and positioning may be performed by fitting a jig into the concave portion (or hole) of the rear plate and the concave portion 116 of the housing body. Good.
Further, when the device 1 is attached to the engine, the unit assembled integrally is attached to the camshaft 3. First, the end portion 30 (insertion portion 301) of the camshaft 3 is inserted from the X-axis negative direction side into the insertion hole 90 formed in the housing HSG of the unit and the vane member 6 accommodated in the housing HSG. Is inserted and installed in the camshaft insertion hole 601. At this time, the positioning means is used to position the vane member 6 in the circumferential direction with respect to the camshaft 3. That is, a hole 603 is provided on the bottom surface of the camshaft insertion hole 601. The camshaft end surface 300 is provided with one convex portion. When inserting and installing the end portion 30 in the camshaft insertion hole 601, the end portion 30 is inserted until the end surface 300 abuts against the bottom surface of the camshaft insertion hole 601 while fitting the convex portion into the hole 603. To do. The opening in the camshaft end surface 300 of the passage 502 or the passage 512 is closed when the end surface 300 abuts against the bottom surface of the camshaft insertion hole 601. At this time, the relative rotation of the vane member 6 and the camshaft 3 is restricted by the fitting of the convex portions, and relative positioning in the rotational direction (circumferential direction) is performed. That is, the convex portion and the positioning hole 603 constitute positioning means for adjusting and determining the rotational position of the vane member 6 relative to the camshaft 3 when the device 1 is attached to the camshaft 3. Thereby, the initial phase of the camshaft 3 (vane member 6) with respect to the crankshaft (housing HSG) is set.
The convex portion on the camshaft side may be provided by inserting and installing a pin or the like in one of the openings of the axial passages 502 and 512 provided on the end surface 300. The positioning hole 603 may have any shape as long as it can fit a convex portion therein to restrain relative rotation in the circumferential direction, and is not limited to a semi-oval shape continuous with the hole 602. Moreover, it is good also as providing a convex part in the vane member 6 side and providing the recessed part fitted to this in the camshaft end part 30 side.
In addition, in the apparatus 1, since the large diameter hole 80 is provided in the front plate 8, the fastening of the cam bolt 31 is easy. That is, if the unit of the assembled apparatus 1 is attached to the camshaft 3, an opening is formed by the large-diameter hole 80 on the X axis positive direction side (front plate 8 side) of the housing HSG. The vane member 6 can be fastened and fixed to the camshaft 3 simply by inserting and rotating the cam bolt 31 from the opening. Therefore, attachment of the device 1 to the camshaft 3 can be facilitated.

(Operation by the stopper configuration)
The first vane 61 (the root portion) constituting the first stopper portion is wider and thicker in the circumferential direction than the other vanes 62 to 65 (the root portion). As described above, at least one of the plurality of vanes 61 to 65 is the wide vane 61, so that the lock mechanism 7 can be easily provided on the vane member 6 (vane 61), and the wide and rigid. The high vane 61 is brought into contact with the shoe 11 to restrict the relative rotation of the vane member 6 in one direction. Therefore, the first stopper portion can be simply provided while securing the fixing strength of the vane 61 with respect to the contact. Further, the second stopper portion that restricts the relative rotation in the other direction is also constituted by the wide first vane 61. Therefore, by sharing the wide vane used as the stopper portion in both directions of the relative rotation, the wide members can be reduced and the space can be omitted. Moreover, about the other vanes 62-65 which are not provided in the circumferential direction wide like the 1st vane 61, there exists a high possibility that the fixing strength of the vanes 61-65 with respect to the rotor 60 may be insufficient. In the first embodiment, the other vanes 62 to 65 are configured not to come into contact with the shoes 11 to 15 at the time of restricting the rotation in the two directions, thereby avoiding the action of force due to the contact, and the thin vanes 62. The fixing strength (durability) of ˜65 can also be improved.
Therefore, the durability of the vane member 6 can be improved while sufficiently obtaining strength for restricting relative rotation.
As a configuration for restricting the relative rotation, any one set or a plurality of sets of the other vanes 62 to 65 and the shoes 11 to 15 are brought into contact with each other, and the first and second stopper portions are configured by the contact portions. It is good as well. Further, the vane constituting the abutting portion may be formed to be wide like the first vane 61 to increase the rigidity.
Unlike the case where the vane 61 itself is provided in contact with the shoe 11 as in the first embodiment, a protruding portion is provided on the circumferential side surface of the vane 61 and this is brought into contact with the shoe 11. It is possible to ensure a larger relative rotation angle range of the member 6.

(Operation by material and molding method)
In the first embodiment, since the constituent members 6, 8 to 10 are formed of a ferrous metal material having a relatively high hardness, it is possible to provide the members 6, 8 to 10 with a relatively small thickness. is there. Thereby, compared with the case where each member 6,8-10 is shape | molded with the material (for example, aluminum type metal material) with comparatively low hardness, the X-axis direction dimension and radial direction dimension of the apparatus 1 are ensured, ensuring required intensity | strength. Can be reduced.
The sealing members (front plate 8 and rear plate 9) are formed of an iron-based metal material that is a material having high hardness. Therefore, the strength of the front plate 8 that functions as a seating surface of the bolts b1 to b5 is secured, and the strength of the bolt holes (internal threads 91 to 95) provided in the rear plate 9 is secured, thereby improving the durability of the device 1. Can be improved. Moreover, the sealing members 8 and 9 are shape | molded with the iron-type metal material which is a material with high abrasion resistance. Therefore, durability of the sliding part with the vane member 6 in the sealing members 8 and 9 (the axial end surface thereof) can be ensured. In addition, it is possible to suppress wear due to the sliding of the coil spring 74 of the lock mechanism 7 on the surface of the front plate 8 on the X axis negative direction side. As a material having high wear resistance and hardness, a metal material other than the iron-based metal material, such as magnesium, may be used, or a material other than the metal material, such as ceramic, may be used.
In the first embodiment, the front plate 8 having a relatively simple structure is formed by pressing a steel material. However, the front plate 8 may be formed by another material (for example, an aluminum-based metal material) or a method. For example, in addition to the powder metallurgy method (sintering method) similar to the rear plate 9 or the like, the front plate 8 may be formed by forging or casting. The material and processing method of the housing body 10 and the rear plate 9 are not particularly limited, and may be formed by casting or forging of another metal material, for example, extrusion molding of an aluminum-based metal material.
The housing body 10 and the vane member 6 are formed of a ferrous metal material that is a high-hardness material. The housing body 10 is hardened by heat treatment. Therefore, the durability of the device 1 can be further improved by increasing the rigidity of the vane 61 and the shoes 11 and 12 that function as the stopper portion.
The material of the vane member 6 is not particularly limited, and an aluminum metal material can be used in addition to the iron metal material. The forming method of the vane member 6 is not limited to the powder metallurgy method. For example, the vane member 6 may be integrally formed by extrusion molding, or may be integrally formed by casting or forging. Further, the rotor 60 and the vanes 61 to 65 may be formed as separate members without being integrally formed. In the first embodiment, since the rotor 60 and the vanes 61 to 65 are integrally formed, the number of parts can be reduced, and the cost of processing and assembly can be reduced. Specifically, since these are molded integrally, processing is easier. In the first embodiment, since the vane member 6 is formed of an iron-based metal material, it is possible to suppress wear of the sliding hole 70 resulting from the sliding of the lock piston 71. Further, since it is formed by sintering, the lubricating oil stays in the countless fine holes in the sliding hole 70 for a long time. Therefore, when the engine is not operated for a long time (for example, several days to several months) and the apparatus 1 is not used during that time, when the engine is restarted, the apparatus 1 is activated and the lock piston 71 has a large diameter. Even when the rear end corner of the portion 712 and the inner peripheral surface of the sliding hole 70 are in contact with each other, since the lubricating oil is held in the sliding hole 70, wear can be suppressed. That is, in the apparatus 1, the wear reduction effect is further improved by utilizing the shape characteristics of the sintered metal and imparting a lubricating oil retaining function thereto.
The lock piston 71 and the sleeve 73 are made of a highly wear-resistant material, specifically, an iron-based metal material. Therefore, the hardness of the lock piston 71 and the engagement recess 730 (the inclined surface that is in sliding contact with the engagement portion 714) can be secured, and wear can be particularly effectively reduced. Therefore, the deterioration of the operation of the lock piston 71 can be more effectively suppressed. The engaging recess 730 may be provided directly on the rear plate 9 without being formed by the sleeve 73. In this case, the engaging recess 730 may be formed in the rear plate 9 by cutting or the like. In the first embodiment, since the sleeve 73 is formed of a member different from the rear plate 9, the shape and material of the engagement recess 730 are suitable for engagement / disengagement (engagement and release) of the lock piston 71. It is easy to make adjustments, and it is possible to prevent the rear plate 9 from being worn or twisted during the engagement / disengagement. That is, there is an advantage that a material particularly suitable for wear resistance can be selected and the processing accuracy of the inclined surface can be improved.

(Operation due to the structure of the retard side supply / discharge passage)
The retard oil holes 505 to 509 are provided adjacent to the vanes 61 to 65 in the circumferential direction, open at the roots of the vanes 61 to 65 on the clockwise direction side, and communicate with the retard chambers R1 to R5. Therefore, the vane member 6 relatively rotates in the direction in which the volume of the working chamber (retarding chamber R) in which the retarding oil holes 505 to 509 are opened becomes smaller (advanced side), and the vanes 61 to 65 are the shoes 12 to 15 respectively. , 11, the openings of the retarded oil holes 505 to 509 are not easily blocked by the tip portions of the shoes 12 to 15 and 11, and it is easy to keep the open state.
Specifically, the openings of the holes 505 to 509 are arranged as close to the vanes 61 to 65 as possible, and the holes 506 to 509 are not only the outer peripheral surface 600 of the rotor 60, It opens partially also in the circumferential direction side surface of each vane 62-65. In the first embodiment, since the vanes 61 to 65 and the rotor 60 are integrally formed, it is easy to open in this way. The hole 505 opens in the notch 618 of the first vane 61. Therefore, even if the vane member 6 is relatively rotated in the advance direction, it is possible to suppress the range in which the openings of the holes 505 to 509 to the retarded chamber R are blocked by the shoe tip (increase the opening area). Is possible. Accordingly, a hydraulic oil supply / discharge passage to each retardation chamber R via the holes 505 to 509 is secured in the entire relative rotation range of the vane member 6, and the hydraulic oil is easily introduced into the plurality of retardation chambers R. The controllability of the device 1 can be ensured. In particular, it is possible to smoothly supply the hydraulic oil necessary for starting the relative rotation of the vane member 6 (to the retard angle side) at the maximum relative rotation position (most advanced angle position). In other words, it is easy to expand the relative rotation range of the vane member 6 while ensuring controllability.
The holes 505 to 509 may be inclined to the opposite side of the first embodiment when viewed from the X axis positive direction side, or may be provided on a radial straight line passing through the rotation axis O. The shape of the holes 505 to 509 is not limited to a linear shape, and may be bent, for example. In the first embodiment, since the holes 505 to 509 are linear, molding is relatively easy. Further, instead of the holes 505 to 509, a retarded-side supply / discharge passage may be formed by providing a groove on the end face of the vane member.

(Operation due to the configuration of the advance side supply / discharge path)
Instead of forming a through hole in the vane member 6, a groove (first groove 515 to 519) is provided on the axial end surface of the housing HSG (rear plate 9), and the shaft of the vane member 6 facing this is provided. Covering the concave grooves (first grooves 515 to 519) with the direction end surfaces (end surfaces of the rotor 60 in the X-axis negative direction) constitute a supply / exhaust passage to one of the working chambers (advance chambers A1 to A5) did. Therefore, it is advantageous for shortening the axial dimension of the vane member 6, and the apparatus 1 can be miniaturized in the axial direction.
In addition, since a plurality of supply / discharge passages of hydraulic oil to each of the advance chambers A1 to A5 are formed as concave grooves (first grooves 515 to 519) in the housing HSG, for example, a plurality of holes are individually formed in the vane member 6. Unlike the case of forming a through-hole and using this as a supply / discharge passage, it is possible to reduce labor and man-hours for drilling and shorten the machining time. That is, when providing the supply / discharge passage, it is only necessary to form the first grooves 515 to 519 on the end face of the housing HSG (rear plate 9), so that the forming is easy and the manufacturing cost can be reduced.
Here, the housing HSG has a housing body 10 having an opening at least on the camshaft 3 side (X-axis negative direction side) in the axial direction, and a through hole that seals the opening and through which the camshaft 3 is inserted. And the rear plate 9 provided with the (insertion hole 90), and the first grooves 515 to 519 are provided on the rear plate 9 (the end face in the positive direction of the X axis). Therefore, for example, it is easier to mold the first grooves 515 to 519 with a mold than when the first grooves 515 to 519 are provided on the inner bottom surface of the bottomed cylindrical housing member. In addition, the range in which the first grooves 515 to 519 are formed in the rear plate 9 is reduced by the amount of the insertion holes 90, and when forming the first grooves 515 to 519 together with the insertion holes 90 in a rough material state, the molding is performed. (Molding) is easy. The first grooves 515 to 519 may be formed by cutting or the like after the rear plate 9 is molded. As in the first embodiment, when the rear plate 9 is molded by the sintering method, the first grooves 515 to 519 are formed at the same time, thereby reducing the labor and man-hour for individually cutting the grooves 515 to 519. In addition, the processing time can be shortened.
In addition, since the first grooves 515 to 519 are provided in the rear plate 9 that must be thick in order to form the female screw portions 91 to 95 and the engaging recess 730 (install the sleeve 73), The axial dimension can be reduced more effectively.
The rear plate 9 is formed of sintered metal, and the first grooves 515 to 519 are formed at the same time as the rear plate 9 is molded. Therefore, the first grooves 515 to 519 can be easily formed as compared with cutting and the like.
The first grooves 515 to 519 may be inclined to the opposite side of the first embodiment when viewed from the X axis positive direction side, or may be provided on a radial straight line passing through the rotation axis O. Further, the shape of the first grooves 515 to 519 is not limited to a linear shape, and may be, for example, bent or curved. In the first embodiment, since the first grooves 515 to 519 are linear, molding is relatively easy.
Here, the X-axis direction dimension of the rear plate 9 provided with the first grooves 515 to 519 is set larger than the X-axis direction dimension of the front plate 8 (is formed thicker in the X-axis direction). Therefore, the strength can be improved by increasing the thickness of the portion (the periphery of the groove) where the first grooves 515 to 519 are formed.
Further, between the front end surfaces of the vanes 61 to 65 of the vane member 6 and the inner peripheral surface of the housing main body 10, and the outer peripheral surface 600 of the rotor 60 of the vane member 6 and the front end surfaces of the shoes 11 to 15 of the housing main body 10. A slight radial gap is provided between the two. The radial gap is filled with seal members S1 to S5, 612 to 652, and biasing means (plate springs) 119 to 159 for pressing the seal bodies 118 to 158 and the like are elastically deformed, thereby causing the vane member. 6 is provided so as to be slightly displaceable in the radial direction within the gap with respect to the housing HSG. On the other hand, the gap between the inner circumference of the insertion hole 90 of the rear plate 9 and the outer circumference of the camshaft 3 is provided smaller than the dimension of the vane member 6 that can be displaced in the radial direction (the radial gap). . Therefore, the insertion hole 90 functions to position the camshaft 3 (vane member 6) in the radial direction with respect to the rear plate 9 (housing HSG), and also functions as a bearing of the device 1 with respect to the camshaft 3. Here, as described above, the rear plate 9 in which the first grooves 515 to 519 are provided is larger in thickness (dimension in the X-axis direction) than the front plate 8. As a result, the X-axis direction width of the bearing (around the insertion hole 90) can be made relatively large, and the bearing function can be improved.

(Operation by the arrangement of the first groove)
Conventionally, rotation is transmitted from the crankshaft, and a housing member in which a plurality of storage chambers are defined by a plurality of shoes (partition members) protruding to the inner peripheral side, and fixed to the camshaft, can be relatively rotated in the housing member And a vane member for defining each storage chamber into an advance working chamber and a retard working chamber by a plurality of vanes protruding to the outer peripheral side, and supplying and discharging hydraulic oil to and from these working chambers In a valve timing control device for a so-called vane type internal combustion engine that converts the rotation angle of the vane member relative to the housing member, that is, the relative rotation phase of the crankshaft and the camshaft, a groove for supplying and discharging the working fluid to and from the working chamber Is provided on the end surface in the axial direction of the inner periphery of the housing member (hereinafter referred to as a conventional device).
If the opening of the groove to the working chamber is blocked and the supply / discharge amount of the working fluid is reduced, it becomes difficult to rapidly rotate the vane member, and the valve timing cannot be controlled with good responsiveness. For this reason, the groove needs to be opened to the working chamber without being blocked by the vane even when the vane is closest to the shoe. (For example, increasing the number of vanes and shoes is advantageous because the pressure receiving area of the vane can be increased while suppressing an increase in the size of the apparatus, but in this case, the groove may be blocked by the vane. Therefore, in the conventional apparatus, in order to secure the supply / discharge amount of the working fluid while improving the relative conversion angle of the vane member, the groove is arranged in the vicinity of the shoe. Further, in order to restrict the maximum relative rotational position of the vane member, one vane is brought into contact with the shoe, and the opening of the groove to the working chamber defined between the vane and the shoe is provided. In order not to be blocked by the vane, the outer peripheral side of the vane is protruded and brought into contact with the shoe, and the inner peripheral side of the vane is separated from the shoe, thereby opening the groove into the working chamber. Secured.
However, in the conventional apparatus, since the outer peripheral side of the vane contacting the shoe needs to protrude in the circumferential direction with respect to the inner peripheral side, the weight cannot be reduced by that amount, and the apparatus cannot be reduced in size. Moreover, the range of the relative rotation angle of the vane member, that is, the conversion angle of the device cannot be increased by the amount of protrusion.
On the other hand, the apparatus 1 of the first embodiment includes a housing main body 10 including a plurality of shoes 11 to 15 as a housing HSG (housing member), and at least the X-axis negative direction end (one axial end) of the housing main body 10. The rear plate 9 includes first plates 515 to 519 for supplying and discharging hydraulic oil (working fluid) to the advance chambers A1 to A5 (working chambers). The rear plate 9 is provided on the housing body 10 so that the first grooves 515 to 519 partially overlap the shoes 11 to 15 in the circumferential direction. . In other words, the first grooves 515 to 519 are provided on the surface of the rear plate 9 facing the shoes 11 to 15 (the portion facing the shoes 11 to 15 in the axial direction on the one end surface in the axial direction).
Therefore, the circumferential distance from the vanes 61 to 65 defining the advance chambers A1 to A5 together with the shoes 11 to 15 to the first grooves 515 to 519, specifically, the vanes 61 to 61 facing the advance chambers A1 to A5. The circumferential distance between the circumferential side surface of 65 and the (clockwise direction) edge of the first groove 515 to 519 closest in the circumferential direction from the circumferential side surface of the vanes 61 to 65 is expanded, Even when the vanes 61 to 65 are closest to the shoes 11 to 15, the first grooves 515 to 519 are not blocked by the vanes 61 to 65 and are easily opened to the working chamber. That is, when the first grooves 515 to 519 are not disposed so as to overlap the shoes 11 to 15, there is a circumferential clearance between the first grooves 515 to 519 (its counterclockwise edge) and the shoes 11 to 15. it can. If the vanes 61 to 65 (counterclockwise edges thereof) rotate until they overlap with the circumferential gap, the first grooves 515 to 519 may be completely covered with the vanes 61 to 65, and the openings may be blocked. There is. On the other hand, if the first grooves 515 to 519 are arranged so as to overlap the shoes 11 to 15, the circumferential gap is not generated between the two, so even if the vanes 61 to 65 are closest to the shoes 11 to 15 ( The first grooves 515 to 519 are not completely covered by the vanes 61 to 65 (unless the vanes 61 to 65 and the shoes 11 to 15 are in contact with each other), and the advance chambers A1 to A5 of the first grooves 515 to 519 are not covered. It is possible to ensure an opening to the. In other words, it is possible to increase the conversion angle while securing the opening of the first grooves 515 to 519 to the working chamber. If one or more of the plurality of first grooves 515 to 519 are arranged so as to overlap with the shoes 11 to 15, the opening of at least the first groove overlapped with the shoes is completely blocked by the vanes 61 to 65. It can be made difficult. For this reason, the other first groove is not arranged so as to overlap the shoes 11 to 15, and when the conversion angle is expanded, the opening of the other first groove is completely blocked by the vanes 61 to 65 at the maximum relative rotation position. Even if configured, the total amount of hydraulic oil supplied to the working chamber is reduced, but the hydraulic oil is supplied to the extent that the controllability of the apparatus 1 can be kept at a minimum by the opening of the first groove overlapped with the shoe. If the amount (working hydraulic pressure) can be secured, the conversion angle can be expanded without excessively impairing controllability. In the first embodiment, the first grooves 515 to 519 are provided on the rear plate 9 on the facing surfaces of all the shoes 11 to 15, respectively. In other words, all of the plurality of first grooves 515 to 519 have portions that face the shoes 11 to 15 in the X-axis direction, respectively, and are provided so as to partially overlap the shoes 11 to 15 in the circumferential direction. Therefore, it is easier to expand the conversion angle while preventing the openings of all the first grooves 515 to 519 from being blocked by the vanes 61 to 65 and suppressing the responsiveness of the valve timing control.
Further, the first grooves 515 to 519 are arranged so as not to overlap the seal grooves 117 to 157 in the circumferential direction. Therefore, since communication between the first grooves 515 to 519 and the seal grooves 117 to 157 is suppressed, the hydraulic pressure in the first grooves 515 to 519 acts on the seal members S1 to S5 and functions of the seal members S1 to S5. Can be suppressed, and the supply and discharge of hydraulic oil to and from the working chamber via the first grooves 515 to 519 can be performed more smoothly. By arranging the first grooves 515 to 519 so as to overlap with the shoes 11 to 15 as much as possible in a range that does not overlap with the seal grooves 117 to 157 in the circumferential direction, as described above, the first grooves 515 to 515 to the working chamber are provided. While making it easy to secure 519 openings, the conversion angle can be expanded.

(Operation by the second groove)
A second groove 111 is provided on a surface of the first shoe 11 facing the first groove 515 in the X-axis direction, and the second groove 111 is communicated with the first advance chamber A1 (working chamber). Specifically, the second groove 111 was opened on the surface of the shoe 11 facing the vane 61 in the circumferential direction.
Therefore, a passage for supplying hydraulic oil from the first groove 515 to the first advance chamber A1 via the second groove 111 is formed. Therefore, when the vane 61 comes closest to the shoe 11, there is almost no circumferential clearance between the vane 61 and the shoe 11, and the opening of the first groove 515 to the first advance chamber A <b> 1 is almost completely blocked by the vane 61. Even in the case where the oil is released (for example, when the two surfaces are brought into contact with each other), the hydraulic oil is supplied to and discharged from the first advance chamber A1 through the second groove 111, and the supply / discharge amount is reduced. It is suppressed. In other words, there is an effect that the second groove 111 functions as (a part of) the first advance chamber A1, and the area where the hydraulic oil pressure acts on the vane 61 is defined as the first advance chamber A1. At least the opening area of the second groove 111 can be secured. For this reason, the responsiveness fall of valve timing control can be controlled. That is, for example, the outer circumferential side of the vane 61 protrudes in the circumferential direction relative to the inner circumferential side, and the circumferential clearance is not provided between the vane 61 and the shoe 11 at the maximum relative rotational position. At the relative rotation position, a hydraulic oil supply / discharge passage (the hydraulic oil pressure receiving area in the vane 61) to the first advance chamber A1 defined by the shoe 11 and the vane 61 can be secured. Therefore, in order to supply and discharge the hydraulic oil to and from the first advance chamber A1, it is not necessary to separately provide a circumferential gap between the shoe 11 and the vane 61 and to open the first groove 515 in the circumferential gap. For this reason, the said circumferential clearance is abbreviate | omitted and it becomes possible to enlarge the range of the relative rotation angle of the vane member 6 with respect to the housing HSG to the maximum. That is, it is possible to achieve both expansion of the conversion angle and supply of hydraulic oil to the working chamber. Further, in order to provide the circumferential clearance between the shoe 11 and the vane 61, it is not necessary to provide a protrusion for contact with the shoe 11 or the vane 61. Therefore, the weight of the housing HSG or the vane member 6 can be reduced by the amount that the protruding portion can be omitted, and the device 1 can be reduced in weight and size. In addition, it is good also as omitting partially (it reduces the protrusion amount of the circumferential direction) instead of omitting all the protrusion parts. In the first embodiment, since all the protrusions are omitted and the vane 61 and the shoe 11 are in contact with each other, the above effect can be maximized.
In this manner, the supply / discharge passage can be enlarged and the control response can be improved without hindering the downsizing and widening of the device 1.
The first groove 515 is provided so as to extend from the inner peripheral side of the rear plate 9 (sealing member) to the outer peripheral side, and the second groove 111 also extends from the inner peripheral side end of the shoe 11 to the housing body 10. It is provided so as to extend to the outer peripheral side. Therefore, at the maximum relative rotation position, there is almost no circumferential clearance between the vane 61 and the shoe 11, and the opening of the first groove 515 to the first advance chamber A1 and the second groove to the first advance chamber A1. When the opening of 111 is almost completely blocked by the vane 61, the hydraulic oil supplied from the inner peripheral side (camshaft 3 side) of the rear plate 9 in the first groove 515 is the inner peripheral side of the shoe 11. It tends to flow into the second groove 111 from the end. Accordingly, since the hydraulic oil is smoothly supplied from the first groove 515 to the second groove 111, the hydraulic oil pressure in the second groove 111 is promptly supplied to the vane 61 after the supply of the hydraulic oil to the advance passage 51 is started. The above effect can be improved by acting. The second groove 111 is not provided so as to extend from the inner peripheral side end of the shoe 11, and the second groove 111 is provided at an appropriate portion between the inner peripheral end and the outer peripheral end of the shoe 11. The first groove 515 may be communicated with. Further, for example, a hole is formed in the shoe 11 so that one end of the through hole opens on the side surface of the shoe 11 (facing the first advance chamber A1) and communicates with the advance chamber A1, and the other end is formed. You may comprise so that it may open to the side surface of the shoe 11 (facing the rear plate 9), and may communicate with the 1st groove | channel 515. In the first embodiment, only a part of the shoe 11 in the X-axis direction is cut out to form the second groove 111. However, the second groove 111 may be formed by cutting out the entire shoe 11 in the X-axis direction. Good.
The housing body 10 is formed of sintered metal, and the second groove 111 is formed at the same time as the housing body 10 is molded. Therefore, it is easier to form the second groove 111 as compared with cutting or the like.
Here, since the second groove 111 is provided so as to extend from the inner peripheral side end (tip portion) of the shoe 11 to the outer peripheral side of the housing body 10, the seal groove 117 and the second groove 111 are formed at the shoe tip portion. There is a risk of overlapping and communicating with each other. On the other hand, in the first embodiment, the second groove 111 is disposed so as not to communicate with the seal groove 117. Therefore, the hydraulic oil in the second groove 111 can be prevented from acting on the seal members S1 to S5 and the function of the seal members S1 to S5 can be suppressed, and the hydraulic oil for the advance chamber A1 can be suppressed via the second groove 111. It is possible to more smoothly perform the supply / discharge. As in the first embodiment, the seal members S1 to S5 have seal surface portions extending in the axial direction (only the lengths of the shoes 11 to 15 and the rotor 60 in the axial direction), and are formed on the tip surfaces of the shoes 11 to 15. The seal bodies 118 to 158 installed in the provided seal grooves 117 to 157 and the seal bodies 118 to 158 (the seal surface portions thereof) are biased toward the rotor outer peripheral surface 600 so as to protrude from the seal grooves 117 to 157. In the case of using one constituted by the biasing means 119 to 159, it is possible to reduce the possibility of the function of the seal member being lowered due to the communication between the seal groove 117 and the second groove 111. Because even if the second groove 111 communicates with the seal groove 117, if hydraulic oil from the second groove 111 passes through the side surface of the seal body and is supplied to the bottom of the seal groove 117 (the back side of the seal body), This is because a hydraulic pressure that urges the seal body toward the rotor outer peripheral surface is generated, so that a significant decrease in the sealing function is suppressed. Note that types other than those used in the first embodiment may be employed as the seal members S1 to S5. As the urging means 119 to 159, an elastic member other than the leaf spring may be used, or the seal bodies 118 to 158 themselves may be elastically deformed and the urging means may be omitted.
Specifically, the second groove 111 is formed so as to be included in the range of the first groove 515 in the rotation axis direction (that is, viewed from the X-axis direction). Accordingly, the second groove 111 has a predetermined circumferential distance between the second groove 111 and the seal groove 117 while overlapping the shoe 11 in the circumferential direction. Therefore, not only the seal groove 117 and the second groove 111 are not communicated but also the strength and formability of the seal groove 117 and the second groove 111 at the shoe tip can be improved. That is, the first groove 515 can be provided in a maximum range that does not overlap with the seal groove 117 in the circumferential direction, while the second groove 111 is the maximum that does not overlap with the seal groove 117 in the circumferential direction, like the first groove 515. If it is provided in the range, the thickness between the second groove 111 and the seal groove 117 is not ensured, the strength may be insufficient, and it is disadvantageous in terms of formability. In particular, in the first embodiment, since the housing body 10 (shoe 11) is molded by a mold, if the size of the portion between the second groove 111 and the seal groove 117 is small, molding failure may occur. For example, when a green compact before sintering is formed, there is a risk that this portion may be lost because the powder does not sufficiently reach the above portion in the mold. In the first embodiment, the second groove 111 is formed so as to be included in the range of the first groove 515 in the rotation axis direction, thereby ensuring a thickness between the second groove 111 and the seal groove 117. And the strength and formability can be improved. In addition, as long as the thickness between the second groove 111 and the seal groove 117 can be secured to the extent that there is no inconvenience in terms of strength and formability, the second groove 111 is arranged in the rotational axis direction (as viewed from the axial direction). It may be formed in substantially the same shape as the first groove 515. In this case, since the communication between the first groove 515 and the second groove 111 can be maximized, the efficiency is high.
In the first embodiment, not the entire axial direction (X-axis direction) of the shoe 11 but only a part in the axial direction is notched as the second groove 111. For this reason, the periphery of the seal groove 117 of the shoe 11 in the range where the second groove 111 is not provided in the axial direction can be made thick to further suppress the strength reduction. As long as the strength can be ensured, the second groove 111 may be formed in the entire range of the shoe 11 in the X-axis direction. In this case, the opening area of the second groove 111 on the circumferential side surface of the shoe 11 can be increased.

(Operation by the relationship between the second groove and the positioning means)
In the first embodiment, a recess 116 (positioning means) that determines the circumferential position of the shoe 11 (housing main body 10) with respect to the rear plate 9 (sealing member) is provided. It is provided on the outer peripheral side of the shoe 11 in which the two grooves 111 are formed. Therefore, it is possible to reduce the size of the apparatus 1 while easily achieving positioning. In other words, it is advantageous to provide the shoe 11 in which the second groove 111 is formed as wide in the circumferential direction as much as the strength around the second groove 111 can be secured. By providing the recess 116 in the wide shoe 11 in this manner, space can be saved compared with the case where the other shoe 12-15 is provided with positioning means (recess) to make the other shoe 12-15 wider. This makes it possible to reduce the size of the device 1.

(Operation by the relationship between the second groove and the lock mechanism)
As in the first embodiment, when the lock piston 71 is installed on the vane 61 and the engagement recess 730 (lock hole) is provided at a position adjacent to the shoe 11 in the circumferential direction on the rear plate 9 (sealing member), In the rear plate 9, the circumferential distance (thickness) between the engaging recess 730 and the first groove 515 (in the vicinity of the shoe 11) is reduced, and the formability of the engaging recess 730 in the rear plate 9 and the surrounding strength are reduced. May decrease. In particular, in the first embodiment, since the sleeve 73 is fitted into the fitting hole 96 by press fitting, there is a high risk of deformation around the fitting hole 96 due to press fitting. Even when the engaging recess 730 is formed directly on the rear plate 9 by cutting or the like, the formability and strength may be lowered due to the positional relationship with the first groove 515. On the other hand, in the first embodiment, since the second groove 111 is provided in the shoe 11, the hydraulic oil is not passed from the first groove 515 to the advance chamber A <b> 1 (not directly supplied / discharged) via the second groove 111. It is possible to supply and discharge. Therefore, it is possible to reduce the opening area of the first groove 515 to the advance chamber A1 while securing the supply / discharge passage to the advance chamber A1 by the second groove 111, and the opening of the first groove 515. By reducing the area, the thickness around the engaging recess 730 (fitting hole 96) is increased. In other words, a predetermined thickness (circumferential dimension) is ensured between the first groove 515 and the engaging recess 730 (fitting hole 96) from the viewpoint of the strength and formability of these grooves or recesses. However, in the first embodiment, the engagement groove 730 side portion of the first groove 515 is reduced, and the distance between the first groove 515 and the engagement recess 730 (fitting hole 96) is increased. . Therefore, it is easy to avoid interference between the first groove 515 and the engagement recess 730 (the fitting hole 96) and to secure a predetermined thickness between them. Therefore, for example, even if the sleeve 73 is press-fitted into the fitting hole 96, it is possible to ensure the strength sufficient to withstand the press-fitting, thereby improving the durability of the device 1 and engaging the lock piston 71. And the operation of the lock mechanism 7 can be made more reliable. Further, the engaging recess 730 (the initial position of the vane member 6) can be provided at a circumferential position as close as possible to the shoe 11, and the range for setting the initial position can be maximized.
Specifically, the opening area of the first groove 515 to the advance chamber A1 is set to substantially zero. In other words, when viewed from the X-axis direction, the first groove 515 is provided only at a position overlapping the shoe 11 and not provided at a position overlapping the advance chamber A1. This maximizes the distance between the engaging recess 730 (fitting hole 96) and the first groove 515, in other words, the thickness around the engaging recess 730 (fitting hole 96). The first groove 515 only needs to have a portion formed on the rear plate 9 on the surface facing the shoe 11, and may be formed on a surface other than the facing surface (for example, facing the advance chamber A1). Good. That is, the first groove 515 may be partially opened to the advance chamber A1 within a range in which the strength and formability can be ensured.

(Operation by the relationship between the second groove and the first stopper)
In the first embodiment, the relative rotation position is regulated by the vane 61 being in contact with the shoe 11 provided with at least the second groove 111 at the portion where the second groove 111 is provided. That is, the vane 61 comes into contact with the side surface in the circumferential direction facing the vane 61 (with the opening of the second groove 111) in the shoe 11 provided with the second groove 111. The relative rotational position, that is, the most retarded angle position is regulated.
Thus, when the vane 61 and the shoe 11 are in contact with each other to form the first stopper portion, the vane 61 and the shoe 11 (which constitute the first stopper portion) face each other at the rotation restricting position by the first stopper portion. And the circumferential gap between them is eliminated, and the opening of the first groove 515 to the working chamber (advance chamber A1) formed between them may be blocked by the vane 61.
In the first embodiment, hydraulic oil is supplied to the advance chamber A1 via the second groove 111 even at the rotation restriction position. In other words, at least the opening area of the second groove 111 is ensured for the operating range of the hydraulic pressure applied to the vane 61 (the pressure receiving area of the vane 61). Therefore, after the start of the supply of hydraulic oil, the hydraulic pressure for relative rotation of the vane member 6 is promptly generated also in the advance chamber A1, thereby improving the control responsiveness from the maximum relative rotation position.
Specifically, the first groove 515 is formed in the rear plate 9 so as to extend from the inner peripheral side to the outer peripheral side, and the second groove 111 is formed in the shoe 11 so as to face the first groove 515, The shoe 11 opens on the surface facing the vane 61. Therefore, when the relative rotation between the housing HSG and the vane member 6 is restricted, when the vane 61 and the shoe 11 abut on the inner peripheral side, the opening of the second groove 111 facing the vane 61 (in the circumferential direction) The vane 61 is closed by the contact. That is, at this rotation restricting position, the vane 61 and the shoe 11 are in contact with each other and the volume on the inner peripheral side of the advance chamber A1 is substantially zero, while the pressure of the hydraulic oil in the second groove 111 is It acts on the side surface of the vane 61 in the circumferential direction from the opening. This operating hydraulic pressure generates a force for separating the vane 61 from the shoe 11.
A plurality of pairs of vanes and shoes that contact each other in the same relative rotational direction may be provided to form a plurality of stopper portions in the same direction. In this case, if the second groove is formed in the shoe with which the vane abuts, the above action can be obtained. In the first embodiment, only one vane 61 of the plurality of vanes 61 to 65 is configured to contact the shoe 11, and the second groove 111 is formed only in the shoe 11 to which the vane 61 contacts. The first grooves 516 to 519 in the advance chambers A2 to A5 defined between the other shoes 12 to 15 and the vanes 62 to 65 at the time of the contact are formed by the vanes 62 to 65 and the shoes 12 to 15 is configured to open in a gap between the two. Therefore, in order to ensure the supply / discharge passage (the pressure receiving area of the vane) of the hydraulic oil to the advance chamber A, the second groove 111 may be formed only in one shoe 11 with which the vane 61 abuts. Since it is not necessary to form the second groove in the other shoes 12 to 15 to which 65 does not abut, it is easier to manufacture the device 1 (housing body 10).

(Operation by the relationship between the second groove, lock mechanism and stopper)
In the first embodiment, the lock piston 71 is provided on the vane 61 that contacts the shoe 11. For this reason, compared with the case where the vane which installs the lock piston 71, and the vane which contact | abuts with the shoe 11, it is possible to achieve size reduction, improving the intensity | strength of the apparatus 1. FIG. In other words, the vane 61 provided with the lock piston 71 is advantageously provided wider (thickness) in the circumferential direction than the other vanes 62 to 65 in order to accommodate the lock piston 71. By making the wide vane 61 contact the shoe 11, a stopper function can be realized while ensuring the strength of the vane 61. In other words, the vane 61 to be brought into contact with the shoe 11 is preferably provided with a wide width (thickness) in the circumferential direction in order to ensure strength, but by accommodating the lock piston 71 in the wide vane 61, the other The vanes 62 to 65 are not required to be wide (for installing the lock piston), and the enlargement of the vane member 6 is suppressed.
Further, the engagement recess 730 is provided at a position where the lock piston 71 can be engaged when the vane 61 provided with the lock piston 71 contacts the shoe 11. That is, the rotation restricting position of the vane member 6 and the initial operation position are provided in the same manner. Therefore, in order to hold the vane member 6 at the initial position by the lock mechanism 7, it is sufficient to restrict the relative rotation by the first stopper portion, and it is not necessary to control the relative rotation position of the vane member 6 to the initial position. Therefore, the apparatus 1 can be simplified.
Further, the vane 61 in which the lock piston 71 is installed is provided with a communication groove 76 as a release circuit for supplying hydraulic pressure for releasing the engagement of the lock piston 71. It opens in the position which opposes the 2nd groove | channel 111 in the circumferential direction on the circumferential side surface. Therefore, the hydraulic oil supplied to the second groove 111 via the first groove 515 in the state where the vane 61 and the shoe 11 are in contact with each other at the initial stage of the operation acts on the vane 61 as the hydraulic pressure, and at the same time, 76 is also supplied to generate hydraulic pressure for releasing the engagement of the lock piston 71. For this reason, after the supply of the hydraulic oil to the advance passage 51 is started, the engagement of the lock piston 71 can be released early to improve the startability (control responsiveness) of the device 1.
The opening position of the communication groove 76 on the side surface in the circumferential direction of the vane 61 may be a position that faces the second groove 111 in the circumferential direction and communicates with each other when the vane 61 and the shoe 11 contact each other. It may be biased toward the tip end portion (the root portion of the vane 61).

(Operation by the relationship between the second groove, the positioning means and the stopper)
In the housing main body 10 (with the second groove 111 formed), on the outer peripheral side of the shoe 11 with which the vane 61 abuts, a positioning that determines the circumferential position of the housing main body 10 with respect to the rear plate 9 (sealing member). As a means, a recess 116 is provided. Therefore, it is possible to reduce the size of the apparatus 1 while easily achieving positioning. That is, as described above, the shoe 11 in which the second groove 111 is formed is advantageously provided wide so that strength can be ensured even if it abuts against the vane 61. By providing the recess 116 in the wide shoe 11 in this way, it is not necessary to make the other shoes 12 to 15 wide (in order to provide positioning means), thereby saving space and reducing the housing body 10. The increase in size is suppressed.
Further, the second groove 111 is formed in the widened shoe 11 while allowing the shoe 11 to be widened to some extent in order to secure a space for providing the concave portion 116 (filled portion 114). That is, by forming the second groove 111 using a space that must be wide to provide the recess 116, the strength around the second groove 111 is improved, and the seal groove 117 and the second groove Interference with the groove 111 is suppressed.
In other words, in the first embodiment, the notch portion 615 is provided by notching the tip end portion of the first vane 61 along the shape of the outer periphery of the lock piston 71 (inner periphery of the sliding hole 70). The weight of one vane 61 is reduced. Further, the notch 615 makes it possible to provide a built-up portion 114 at a portion of the housing body 10 (shoe 11) facing the notch 615. In other words, the notch 615 suppresses the interference between the tip end portion of the first vane 61 and the build-up portion 114, and the plane portion 614 of the first vane 61 and the plane portion 113 of the first shoe 11 are face to face. It is possible to contact.
The build-up portion 114 improves the fixing strength of the first shoe 11 against the force acting when the first vane 61 comes into contact with the first shoe 11. That is, the rigidity in the circumferential direction at the root portion of the first shoe 11 is increased so that there is no problem in strength even if the first vane 61 contacts the first shoe 11.
And the build-up part 114 provides the wall thickness for providing the recessed part 116 in the outer peripheral side of the 1st shoe 11 (clockwise direction side). Since the recess 116 is provided by using the space (thickness) formed on the outer peripheral side of the build-up portion 114 as described above, the first portion is compared with the case where the recess 116 is provided in a portion other than the build-up portion 114. It is not necessary to make the shoe 11 wider in the circumferential direction than necessary (to ensure strength), which is efficient.

  In addition, the structure for obtaining each of the above-described actions is not limited to that of the first embodiment. For example, holes 505 to 509 are opened in the advance chambers A1 to A5, and the first grooves 515 to 519 are the retard chambers R1 to R5. It is good also as opening to. Further, the holes 505 to 509 may be omitted, and the supply / exhaust passage to the working chamber may be only one system by the first grooves 515 to 519. In this case, the vane member 6 is provided by supplying / discharging the hydraulic oil to only one of the advance chamber A or the retard chamber R through the first grooves 515 to 519 from the hydraulic oil supply / discharge portion of the camshaft 3. Rotate the relative position. If an urging member (for example, a coil spring) is installed in the working chamber on the side where hydraulic oil is not supplied or discharged, the vane member 6 can be urged and returned to the initial position. When the hydraulic oil is supplied / discharged only to the advance chamber A, the vane member 6 returns to the initial position on the retard side (driven side) due to friction (alternating torque). It is also possible not to install the member.

[Effect of Example 1]
Hereinafter, effects obtained by the valve timing control device for the internal combustion engine of the first embodiment will be listed.
(1) The device 1 seals a housing body 10 that forms a plurality of storage chambers with a plurality of shoes 11 to 15 projecting to the inner peripheral side, and at least one end in the rotational axis direction (X-axis negative direction end) of the housing body 10 A housing member (housing HSG) having a sealing member (rear plate 9) to be stopped, and a plurality of vanes 61 to 65 provided in the housing main body 10 and projecting to the outer peripheral side in the respective housing chambers. The working chambers (advance chambers A1 to A5) are separated from each other and the vane member 6 whose valve timing is changed by rotating relative to the housing member, and the working fluid (hydraulic oil) is supplied in communication with the respective working chambers. A discharge / discharge passage (advanced-side supply / discharge passage made up of the first grooves 515 to 519 and the second groove 111), and at least one of the supply / discharge passages (passage made up of the first groove 515 and the second groove 111). ) Less Also opened to the surface facing the vane 61 in the shoe 11.
Therefore, it is possible to increase the conversion angle while suppressing a decrease in control responsiveness, and to reduce the weight and size of the device 1.
The above-mentioned “separation” is synonymous with “definition (partition formation)”, and in addition to the state in which leakage of the working fluid in the working chamber is suppressed by the sealing member, the sealing member is defined between the defined working chambers. Including a state in which the working fluid can leak to some extent from the working chamber.
Specifically, the working chamber includes an advance working chamber (advance chambers A1 to A5) and a retard working chamber (retard chambers R1 to R5). In other words, the plurality of working chambers (accommodating chambers) formed by the shoes 11 to 15 are defined by the vane 61 to 65 as an advance working chamber and a retard working chamber, respectively. The supply / discharge passages (advanced-side supply / discharge passages 515 to 519, 111, retard-angle supply / discharge passages 505 to 509) communicate with the advance working chamber or the retard working chamber, respectively, to supply and discharge the working fluid. The working fluid may be supplied / discharged only from the supply / discharge passage to only one of the working chambers (advanced working chamber or retarded working chamber).

(2) In other words, a housing body 10 in which a plurality of storage chambers are defined by a plurality of shoes 11 to 15 projecting toward the inner peripheral side, and a sealing member that seals at least one end in the rotational axis direction of the housing body 10 ( A rear plate 9), a housing member (housing HSG) to which rotation is transmitted from the crankshaft, and a camshaft 3, which is provided in the housing main body 10 so as to be relatively rotatable, and protrudes to the outer peripheral side. A plurality of vanes 61 to 65 define the respective storage chambers as working chambers (advance chambers A1 to A5), and a plurality of supply and discharge passages that communicate with the working chambers to supply and discharge the working fluid. (Advanced side supply / exhaust passage comprising the first grooves 515 to 519 and the second groove 111), and at least one of the supply / exhaust passages (passage comprising the first groove 515 and the second groove 111), A first supply / discharge portion (first groove 515) provided on at least a surface (X-axis positive direction end surface) that faces the shoe 11 in the stop member (rear plate 9), and a first supply / discharge portion that faces the shoe 11 It is comprised by the 2nd supply / discharge part (2nd groove | channel 111) which connects a surface (X-axis negative direction end surface) and the surface (clockwise direction end surface) which opposes the vane 61. As shown in FIG.
Therefore, the same effect as the above (1) can be obtained. The first supply / exhaust part is not limited to a groove, and may be a hole.

(3) In other words, at least one of the supply / discharge passages is formed in the shoe 11 so as to face the first groove 515 and the first groove 515 formed in the sealing member (rear plate 9). The second groove 111 communicates with the advance chamber A1).
Specifically, at least one of the supply / discharge passages is provided on at least a surface (X-axis positive direction end surface) facing the shoe 11 in the sealing member (rear plate 9) and the working fluid on the camshaft 3 side. A first groove 515 communicating with the supply / discharge portion (annular groove 514, etc.) and a surface of the shoe 11 facing the first groove 515 (X-axis negative direction end surface) and communicating with the working chamber (advance angle chamber A1) And the second groove 111.
Therefore, by forming the supply / exhaust passage with a groove, molding is easier and the manufacturing cost can be reduced.
More specifically, the first groove 515 is formed to extend in the radial direction. The “radial direction” is synonymous with “from the inner peripheral side (to the sealing member) to the outer peripheral side”, and is not limited to the direction of the radial line passing through the rotation axis O, but with respect to the radial line. It also includes a direction extending at an angle.

(4) The sealing member (rear plate 9) is formed of sintered metal, and the first grooves 515 to 519 are simultaneously formed when the sealing member (rear plate 9) is molded.
Therefore, the first grooves 515 to 519 can be easily formed as compared with cutting and the like.

(5) The housing body 10 is formed of sintered metal, and the second groove 111 is formed at the same time as the housing body 10 is molded.
Therefore, it is easier to form the second groove 111 as compared with cutting or the like.

(6) The 1st groove | channels 515-519 are each provided in the opposing surface with all the shoes 11-15.
Therefore, it is easier to expand the conversion angle while suppressing a decrease in control responsiveness.

(7) The first groove 515 is formed so as to extend from the inner peripheral side to the outer peripheral side. The second groove 111 extends from the inner peripheral end of the shoe 11.
Therefore, the working fluid can be smoothly circulated between the first groove 515 and the second groove 111.

(8) A seal groove 117 formed in the inner peripheral portion of the shoe 11 so as to extend in the rotation axis direction, and a seal member that is disposed in the seal groove 117 and slides on the vane member 6 (rotor outer peripheral surface 600). S1 is provided, and the second supply / discharge portion (second groove 111) and the seal groove 117 are not in communication.
Therefore, it is possible to suppress the functional deterioration of the seal member S1, and to smoothly supply and discharge the working fluid via the second supply / discharge portion (second groove 111).

(9) The second groove 111 is formed to have the same shape as the first groove 515 in the rotation axis direction, or included in the range of the first groove 515 in the rotation axis direction.
Therefore, it is possible to ensure the thickness between the second groove 111 and the seal groove 117, and the strength and formability can be improved.

(10) Positioning means for determining the circumferential position with respect to the sealing member (rear plate 9) on the outer peripheral side of the shoe 11 where the second supply / discharge portion (second groove 111) in the housing body 10 is formed. A recess 116) is provided.
Therefore, the apparatus 1 can be reduced in size.
Specifically, the positioning means includes a positioning concave portion 116 provided in one of the sealing member (rear plate 9) or the housing main body 10 (housing main body 10), and a positioning convex portion provided in the other (rear plate 9). 97.

(11) The vane member 6 is provided with a lock piston 71 that can be projected and retracted with respect to the sealing member (rear plate 9), and the lock piston 71 can be engaged with the sealing member (rear plate 9). A lock hole (engagement recess 730) is formed, and the lock piston 71 is engaged with or released from the lock hole depending on the state of the internal combustion engine.
Therefore, it is possible to simply provide the lock mechanism 7 for operating the device 1 from the initial position while suppressing the enlargement of the device 1.

(12) In the above (11), the vane 61 is provided with the lock piston 71, and the sealing member (rear plate 9) is adjacent to the shoe 11 provided with the second supply / discharge portion (second groove 111) in the circumferential direction. The lock hole (engagement recessed part 730) was provided in the position to do.
Therefore, it is possible to improve the strength of the portion between the first groove 515 and the lock hole (engagement recess 730) in the sealing member (rear plate 9) and the moldability of the lock hole.

(13) In (12) above, the engagement hole constituting member (sleeve 73) is press-fitted into the lock hole.
Therefore, it is possible to secure the thickness around the lock hole and suppress the strength shortage against press-fitting.

(14) At least one of the supply / discharge passages (passage formed by the first groove 515 and the second groove 111) is opened at least on the surface of the shoe 11 facing the vane 61, and the opening is in contact with the vane 61. Closed by.
In other words, the vane 61 comes into contact with the shoe 11 provided with at least the second supply / discharge portion (second groove 111) at the portion where the second supply / discharge portion (second groove 111) is provided. The advance angle position or the most retarded angle position is regulated.
Therefore, the control responsiveness from the maximum relative rotational position can be improved while obtaining the same effect as the above (1).

(15) Specifically, at least one of the supply / discharge passages (passage formed by the first groove 515 and the second groove 111) extends from the inner peripheral side to the outer peripheral side of the sealing member (rear plate 9). The formed first groove 515 is formed on the shoe 11 so as to oppose the first groove 515 (in the X-axis direction), and the vane 61 and the shoe 11 abut on the inner peripheral side so that the housing member (housing HSG) and the vane When the relative rotation of the member 6 is restricted, the vane 61 and the second groove 111 facing (in the circumferential direction) are configured.
Therefore, the same effect as the above (1) and (3) can be obtained.

(16) Of the plurality of vanes 61 to 65, only one vane 61 is configured to contact the shoe 11, and the second groove 111 is formed only in the shoe 11 to which the vane 61 contacts, and the first groove 516 to 519 are configured to open in a gap between the other vanes 62 to 65 and the shoes 12 to 15 when one vane 61 contacts the shoe 11.
Therefore, the manufacture of the device 1 can be facilitated.

(17) In the above (12), the lock piston 71 is provided on the vane 61 that contacts the shoe 11.
Therefore, it is possible to reduce the size of the device 1 while obtaining the same effect as the above (12).

In the apparatus of Example 2, the second groove 111 of the first shoe 11 constituting the stopper portion was omitted, and the second grooves (similar to the second groove 111) were provided in the other shoes 12 to 15. Moreover, the opening area to the working chamber of the 1st groove | channels 516-519 facing this 2nd groove | channel was reduced. Since the second groove and other configurations are the same as those in the first embodiment, description thereof is omitted. The first shoe 11 may also be provided with a second groove.
That is, in order to reduce the weight and size of the apparatus 1, it is preferable to reduce the circumferential width of each of the vanes 62 to 65. However, in this case, the sealing performance between the working chambers A and R adjacent to each other with the vanes 62 to 65 is lowered, thereby reducing the amount of hydraulic oil supplied to the working chambers A and R, and the valve timing control. Responsiveness may decrease. In other words, a slight gap in the X-axis direction is provided between the vane member 6 and the sealing members 8 and 9 in order to enable relative rotation between the two. When the circumferential width of the vanes 62 to 65 is small, the circumferential distance (seal length) between the adjacent working chambers A and R across the vanes 62 to 65 is small, so that the hydraulic oil passes through the gap. The risk of leakage increases. In particular, the vane member 6 is in a direction in which the volume of the working chamber (retarding chamber R2 to R5) where the first grooves 516 to 519 are not opened increases (the direction in which the vanes 62 to 65 approach the first grooves 516 to 519). When the vanes 62 to 65 and the first grooves 516 to 519 overlap with each other in the circumferential direction, the circumferential distance between the working chamber (retarding chambers R2 to R5) and the first grooves 516 to 519 (seal) Length) is smaller than the circumferential width of the vanes 62 to 65. When the hydraulic oil is supplied to the first grooves 516 to 519 in this state, the hydraulic oil in the first grooves 516 to 519 is displaced in the axial gap between the vanes 62 to 65 and the sealing member (rear plate 9). There is a high risk of leakage through the (low pressure) working chamber (retarding chambers R2 to R5). In particular, at the maximum relative rotation position (maximum retardation position) where the overlapping range of the vanes 62 to 65 and the first grooves 516 to 519 is maximum, the seal length is minimum, and thus the risk is maximum. Further, when the conversion angle is increased, the gap between the vanes 62 to 65 and the shoes 12 to 15 is reduced, and the working chamber (retarding angle) adjacent to the first grooves 516 to 519 with the vanes 62 to 65 interposed therebetween. Since the circumferential distance (seal length) between the chambers R2 to R5) and the first grooves 516 to 519 is small, the sealing performance between the two may be reduced.
In contrast, in the second embodiment, since the second grooves are provided in the shoes 12 to 15, the hydraulic oil is directly supplied to and discharged from the first grooves 516 to 519 (the working chambers (advance chambers A2 to A5)). It is possible to supply and discharge via the second groove. Therefore, it is possible to reduce the opening area of the first grooves 516 to 519 to the working chamber (advanced chambers A2 to A5) while securing a supply / discharge passage to the working chamber (advanced chambers A2 to A5). In addition, the seal length is increased by reducing the opening area of the first grooves 516 to 519.
In other words, when the vanes 62 to 65 and the first grooves 516 to 519 overlap with each other in the circumferential direction, the first groove 516 to 519 and the working chamber (slow) that is adjacent to the first groove 516 to 519 with the vanes 62 to 65 interposed therebetween. It is necessary to ensure a predetermined circumferential distance (seal length) between the corner chambers R2 to R5) from the viewpoint of sealing performance. In the second embodiment, even if the opening area of the first grooves 516 to 519 to the working chamber (advance chambers A2 to A5) is reduced, the second groove supplies the working chamber (advance chambers A2 to A5). Focusing on the fact that an exhaust passage can be secured, by reducing the opening area of the first grooves 516 to 519, a working chamber (retarding chamber) adjacent to the first grooves 516 to 519 with the vanes 62 to 65 interposed therebetween. The circumferential distance between R2-R5) and the first grooves 516-519 was increased. Therefore, the said seal length in each vane 62-65 can be increased, and leakage of hydraulic fluid can be suppressed to such an extent that the operation responsiveness of the device 1 can be ensured, for example, even at the maximum relative rotational position (most retarded position). In other words, even if the circumferential width of the vanes 62 to 65 is reduced and the apparatus 1 is downsized, the conversion angle can be expanded while ensuring the operation responsiveness by increasing the seal length in each of the vanes 62 to 65. It becomes possible.
Specifically, the opening area of the first grooves 516 to 519 to the working chambers (advance chambers A2 to A5) was set to substantially zero. In other words, when viewed from the X-axis direction, the first grooves 516 to 519 are provided only at positions overlapping the shoes 12 to 15 and are not provided at positions overlapping the working chambers (advance chambers A2 to A5). This maximizes the distance (seal length) between the working chambers (retarding chambers R2 to R5) adjacent to the first grooves 516 to 519 and the first grooves 516 to 519 across the vanes 62 to 65. .
The first grooves 516 to 519 may be opened to the working chambers (advance chambers A2 to A5) within a range in which sealing performance can be secured. Further, if a second groove is provided in at least one of the second to fifth shoes 12 to 15, the vanes 62 to 65 (first grooves 516) that face the shoes 12 to 15 not provided with the second groove in the circumferential direction. Even if the seal length in the vanes 62 to 65 defining the working chamber in which ˜519 is opened becomes small, the above in the vanes 62 to 65 facing the shoes 12 to 15 provided with the second groove in the circumferential direction at least. The seal length can be increased as described above. For this reason, in the maximum relative rotation position (most retarded angle position), the amount of hydraulic oil leakage is suppressed in the vanes 62 to 65 facing the shoes 12 to 15 provided with the second groove in the circumferential direction, and the controllability of the device 1 If the supply amount of hydraulic oil (working hydraulic pressure) that can guarantee the minimum is secured, the conversion angle can be expanded without excessively degrading the controllability. In this case, manufacturing can be facilitated. Here, the controllability of the apparatus 1 can be improved by increasing the total amount of hydraulic oil supplied as the number of shoes 12 to 15 provided with the second groove is increased. In the second embodiment, since the second grooves are provided in all the shoes 12 to 15, the above-mentioned operational effects can be maximized.
Further, the hydraulic pressure supplied to the working chamber to relatively rotate the vane member 6 is higher at the most retarded position than at the most advanced position. That is, an alternating torque acts on the vane member 6 in addition to the torque caused by the hydraulic pressure in the working chamber. The direction in which this alternating torque (average) acts is the retard direction as described above. Therefore, in the most retarded angle position, in order to relatively rotate the vane member 6 against the alternating torque, the hydraulic pressure higher than the most advanced angle position is applied to the working chamber (first groove 516 to 519) via the supply / discharge passage (first grooves 516 to 519). To advance chambers A2 to A5). Therefore, in order to suppress the leakage amount between the working chambers A and R adjacent to each other with the vanes 62 to 65 interposed therebetween, the seal length needs to be provided larger at the most retarded angle position than at the most advanced angle position. . On the other hand, in the second embodiment, the opening area of the first grooves 516 to 519 for supplying the hydraulic oil to the advance chambers A2 to A5 is reduced, and the seal length at the most retarded position is increased. Thus, leakage of hydraulic oil can be suppressed and the above effect can be improved.
Other functions and effects are the same as those of the first embodiment.

[Other embodiments]
As mentioned above, although the form for implement | achieving this invention has been demonstrated based on Example 1, 2, the concrete structure of this invention is not limited to Example 1, 2, The summary of invention is shown. Design changes and the like within a range that does not deviate are included in the present invention.

1 valve timing control device 3 camshaft 6 vane member (vane rotor)
61-65 Vane 9 Rear plate (sealing member)
10 Housing body 11 to 15 Shoes 515 to 519 First groove (supply / discharge passage)
111 Second groove (supply / discharge passage)
HSG housing (housing member)
A1 to A5 Advance chamber (advance chamber)
R1-R5 Retarded room (retarded working room)

Claims (3)

A housing body that forms a plurality of working chambers by a plurality of shoes projecting to the inner peripheral side, a sealing member that seals at least one end of the housing body in the direction of the rotation axis, and rotation is transmitted from the crankshaft. A housing member;
The working chamber is fixed to the camshaft, is provided in the housing body so as to be relatively rotatable, and the working chamber is separated into an advance working chamber and a retard working chamber by a plurality of vanes protruding outward in each working chamber. Vane rotor to do,
A supply / discharge passage for supplying and discharging hydraulic fluid in communication with each of the advance working chamber and the retard working chamber;
At least one of the supply / discharge passages is provided on a surface of the sealing member that is formed to extend in a radial direction on at least a surface of the shoe facing the shoe, and on a surface of the shoe facing the first groove. And a second groove formed,
The most advanced angle position or the most retarded angle position is regulated by abutting at least the shoe provided with the second groove and the vane at a portion provided with the second groove. Engine valve timing control device. A housing member comprising a housing body that forms a plurality of working chambers by a plurality of shoes projecting to the inner peripheral side; and a sealing member that seals at least one end in the rotational axis direction of the housing body;
By separating the working chamber into an advance working chamber and a retard working chamber by a plurality of vanes provided in the housing body and projecting to the outer peripheral side in each working chamber, and by rotating relative to the housing member, A vane rotor whose valve timing is changed,
A supply / discharge passage for supplying and discharging hydraulic fluid in communication with each of the advance working chamber and the retard working chamber;
At least one of the supply / discharge passages opens at least on a surface of the shoe facing the vane, and the opening is closed when the vane comes into contact with the valve timing control device for an internal combustion engine. . A housing member comprising a housing body that forms a plurality of working chambers by a plurality of shoes projecting to the inner peripheral side; and a sealing member that seals at least one end in the rotational axis direction of the housing body;
By separating the working chamber into an advance working chamber and a retard working chamber by a plurality of vanes provided in the housing body and projecting to the outer peripheral side in each working chamber, and by rotating relative to the housing member, A vane rotor whose valve timing is changed,
A supply / discharge passage for supplying and discharging hydraulic fluid in communication with each of the advance working chamber and the retard working chamber;
At least one of the supply and discharge passages is formed in the shoe so as to extend in the radial direction in the sealing member, the shoe facing the first groove, and the vane and the shoe A valve timing control for an internal combustion engine, comprising: a second groove provided so as to face the vane when the housing member and the vane rotor are restricted from rotating relative to each other on the circumferential side. apparatus.

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