JP5179405B2 - Valve timing control device for internal combustion engine - Google Patents

Description

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

  2. Description of the Related Art Conventionally, a valve timing control device for an internal combustion engine that changes valve timing (rotation phase of a camshaft with respect to a crankshaft) by relatively rotating a driven member housed in a housing member so as to be relatively rotatable by supplying and discharging fluid. Are known. For example, in the apparatus described in Patent Document 1, a pulley is formed on the outer periphery of a cylindrical housing member, and a timing belt is stretched over the pulley to transmit the rotation of the crankshaft. Rotate in sync with

Japanese Patent Laid-Open No. 5-113112

In the apparatus described in Patent Document 1, both axial ends of the housing main body, which is a cylindrical portion of the housing member, are directly butted against both axial end faces of the housing main body with both the first plate and the second plate. The first plate and the second plate are used for sealing.
By the way, recently, there is a tendency that the demand for downsizing of the apparatus is increased. For example, in the configuration described in Patent Document 1, both end surfaces of the first plate and the second plate are brought into contact with the axial end surface of the housing body as it is. Since it is fixed, the shortening of the axial dimension of the apparatus is not considered.
An object of the present invention is to provide a valve timing control device for an internal combustion engine that can be reduced in size by reducing the axial dimension of the device.

In order to achieve the above object, a valve timing control device for an internal combustion engine according to the present invention is preferably a housing body in which a toothed pulley is integrally formed on the outer periphery in the entire axial range, and a sealing recess is formed at least at one axial end. And a plate that is inserted or fixed in the sealing recess in the entire axial direction or partially and seals one end of the housing body in the axial direction.

  Therefore, the apparatus can be reduced in size in the axial direction by inserting and fixing a plate that seals one end of the housing body in the axial direction in the sealing concave portion of the housing body in whole or in part.

It is the front view which looked at the valve timing control apparatus of the intake side and exhaust side which were installed in the internal combustion engine from one side of the axial direction. It is a disassembled perspective view of the valve timing control device on the intake side. It is a fragmentary sectional view which passes along the rotating shaft of the valve timing control apparatus by the side of intake. It is the front view which looked at the valve timing control apparatus of the intake side from one side of the rotating shaft direction (most retarded angle position). It is the front view which looked at the valve timing control apparatus of the intake side from one side of the rotating shaft direction (most advanced position). (A) is the front view which looked at the housing main body by the side of an intake air from one side of the rotating shaft direction. (B) is CC sectional view taken on the line of (a). (C) is the front view which looked at the housing main body by the side of an intake air from the other in the rotating shaft direction. It is a perspective view of the primary processed product of the housing body of an intake side and an exhaust side. It is a perspective view of the tertiary processed product of the housing body of an intake side and an exhaust side. (A) is the front view which looked at the vane rotor of the intake side from one side of the rotating shaft direction. (B) is DD sectional view taken on the line of (a). It is a perspective view of the primary processed product of the vane rotor of an intake side and an exhaust side. It is a perspective view of the secondary work product of the vane rotor of an intake side and an exhaust side. It is a perspective view of a front plate on the intake side. It is a fragmentary sectional view which passes along the axial center of the pin hole to which the positioning pin was fixed. It is sectional drawing which passes along the axial center of a locking mechanism. It is a fragmentary sectional view which passes along the rotating shaft of the valve timing control apparatus by the side of exhaust. It is the front view which looked at the valve | bulb timing control apparatus by the side of an exhaust gas from one side of the rotating shaft direction (most advanced angle position). It is the front view which looked at the valve | bulb timing control apparatus by the side of an exhaust gas from one side of the rotating shaft direction (most retarded angle position). (A) is the front view which looked at the housing body by the side of an exhaust from the one side of the rotating shaft direction. (B) is EE view sectional drawing of (a). (C) is the front view which looked at the housing body by the side of an exhaust side from the other of the rotating shaft direction. (A) is the front view which looked at the vane rotor of the exhaust side from one side of the rotating shaft direction. (B) is the FF sectional view taken on the line of (a).

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

(Configuration of valve timing control device)
FIG. 1 is a partial front view of a valve timing control device (hereinafter referred to as device 1) in which a cylinder block of an internal combustion engine (hereinafter referred to as engine) is viewed from the axial direction of a crankshaft (or camshaft). The engine to which the apparatus 1 of the first embodiment is applied is a V-type engine in which two cylinder rows (banks) are arranged in a V shape starting from a crankshaft, and is used for an intake valve for one cylinder. This is a DOHC system in which two camshafts (hereinafter referred to as intake camshaft 3a) and two camshafts for exhaust valves (hereinafter referred to as exhaust camshaft 3b) are installed. A set of one intake camshaft and one exhaust camshaft is provided for each cylinder row. The intake camshaft 3a is installed inside the cylinder block in the width direction, and drives the intake valve. The exhaust camshaft 3b is installed outside the cylinder block in the width direction, and drives the exhaust valve.

  A device 1 is installed at one axial end of each camshaft 3. The intake side device 1a is fixedly installed on the intake camshaft 3a, and the exhaust side device 1b is fixedly installed on the exhaust camshaft 3b. Each apparatus 1 is provided with a pulley 100, and each pulley 100 is stretched over one timing belt (hereinafter referred to as belt B) (two-dot chain line in FIG. 1). Belt B is a rubber toothed belt. The rotational force of the crankshaft is transmitted to each pulley 100 via the belt B. Each device 1 is rotationally driven by a pulley 100 and optimally variably controls the opening / closing timing of each valve (intake valve / exhaust valve) according to operating conditions.

  Hereinafter, for convenience of explanation, the X axis is provided in the axial direction of the intake camshaft 3a and the exhaust camshaft 3b, and the side on which the devices 1a and 1b are installed is defined as the positive direction.

(System configuration on the intake side)
First, the configuration of the device 1a applied to the intake side of the engine will be described with reference to FIGS. FIG. 2 is a diagram of the members constituting the device 1a disassembled and arranged on the same axis as viewed obliquely. FIG. 3 shows a partial cross section through the camshaft rotation axis O (see FIG. 4) of the device 1a. 4 and 5 are front views of the apparatus 1a (with the vane rotor 4 assembled to the housing body 10) with the front plate 8 and the like removed, as viewed from the X axis positive direction side. The retarded oil passage 408 and the advanced oil passage 409 are shown together (broken line in FIG. 3). Note that FIG. 3 corresponds to a cross section (dotted line) in FIG.

  The device 1a is a hydraulic actuator (hydraulic drive type phase conversion mechanism) that operates when hydraulic oil is supplied from the hydraulic supply / discharge mechanism 2 or is discharged to the hydraulic supply / discharge mechanism 2. The supply / discharge of hydraulic oil to / from the apparatus 1a by the hydraulic supply / discharge mechanism 2 is controlled by a control means (controller CU). The apparatus 1a variably controls the valve timing of the intake valve by continuously changing the rotational phase of the intake camshaft 3a (hereinafter referred to as the camshaft 3a) with respect to the crankshaft using the supplied hydraulic pressure.

  The apparatus 1a includes a pulley 100, a housing HSG, and a vane rotor 4. The rotational force of the crankshaft is transmitted to the housing HSG via the pulley 100. The vane rotor 4 accommodated in the housing HSG is provided so as to be rotatable relative to the housing HSG, and a rotational force is transmitted from the housing HSG via the hydraulic oil, and this rotational force is transmitted to the camshaft 3a. To communicate.

  The housing HSG is a housing member having a front plate 8, a rear plate 9, and a housing body 10. The housing body 10 is a hollow cylindrical housing member that is open at both ends in the X-axis direction. The front plate 8 is a disk-shaped housing member that seals and closes the opening end of the housing body 10 on the positive side of the X axis. The rear plate 9 is a disk-shaped housing member that seals and closes the opening end of the housing main body 10 on the X axis negative direction side. Since the housing body 10 of the first embodiment is made by extrusion molding as will be described later, the housing body 10 has a hollow cylindrical shape and is open at both ends. Therefore, both opening ends are sealed by the front plate 8 and the rear plate 9.

  FIG. 6 shows the housing body 10. (A) is the front view which looked at the housing main body 10 from the X-axis positive direction side, (b) shows CC sectional view of (a), (c) is the X-axis negative direction side. It is the front view seen from. 7 and 8 show an intermediate state (material) in the manufacturing process of the housing body 10.

  The housing body 10 is formed from an aluminum extruded material as shown in FIG. First, an aluminum-based metal material (aluminum or an aluminum alloy such as A6000 or A7000) is extruded from a mold, and has the shape of each shoe 11-13 on the inner periphery as shown in FIG. It is extrusion-molded into a continuous body having a shape (this is called a primary processed product P1). Thereafter, the entire outer peripheral surface and inner peripheral surface of the primary processed product P1 are subjected to anodizing treatment (alumite processing) to increase the surface hardness (this is referred to as a secondary processed product P2). Then, as shown in FIG. 8, the secondary processed product P2 is cut in a radial direction at a constant axial interval to form a plurality of members having the same shape (these members are referred to as a tertiary processed product P3). Then, the tertiary processed product P3 is cut to provide the sealing recess 101, the bolt hole 110, and the like, thereby obtaining the housing body 10 having the final shape shown in FIG.

  As shown in FIGS. 6B and 6C, at the opening end of the housing body 10 on the X axis negative direction side, a sealing recess 101 which is a recess (stepped portion) drilled toward the X axis positive direction side. Is provided. The sealing recess 101 is formed by drilling (thinning) the tertiary processed product P3 into a cylindrical shape having a predetermined radius R around the rotation axis O to a predetermined depth in the positive direction of the X axis. ing. The sealing recess 101 has a bottom surface 102 whose outer periphery is circular, and a wall surface 103 that surrounds the bottom surface 102 and is the inner peripheral surface of the sealing recess 101. The wall surface 103 has a radius R around the rotation axis O.

  If the radius of the inner peripheral surface of the housing body 10 around the rotation axis O is Ri and the maximum radius to the tooth tip of the pulley 100 is Ro, then Ro> R> Ri and Ro: Ri≈100: 82. . Further, (Ro + Ri) / 2≈R. In other words, when viewed in the housing radial direction, the sealing recess 101 is provided over a substantially half range between the inner peripheral surface and the outer peripheral surface of the housing body 10. On the other hand, in the X-axis direction, the distance L2 between the end surface 104 of the housing body 10 on the negative side of the X-axis and the bottom surface 102 of the sealing recess 101 is approximately 20% of the length L of the housing body 10 in the X-axis direction. It is. In other words, the sealing recess 101 is provided over a range of about 20% of the housing body 10 in the X-axis direction.

  A pulley 100 is formed integrally with the housing body 10 in the entire outer periphery of the housing body 10 in the X-axis direction. The X-axis direction length L1 on the inner peripheral side of the housing body 10 is shorter than the outer peripheral side (pulley 100) by the sealing recess 101 (L1 <L). In other words, the length L in the X-axis direction of the pulley 100 is ensured longer than the inner peripheral side (L1) of the housing body 10. The pulley 100 is a gear that is composed of irregularities (teeth) extending in the X-axis direction and around which the belt B is wound. The pulley 100 is rotationally driven by the crankshaft of the engine and rotates together with the housing body 10 in the clockwise direction ( This corresponds to the direction of the arrow in FIG.

  On the inner periphery of the housing body 10, a plurality of shoes 11 to 13 projecting inward are formed integrally with the housing body 10. Specifically, the first to third shoes 11 to 13, which are three partition walls, are arranged at substantially equal intervals in a direction around the rotation axis O (hereinafter referred to as a circumferential direction). Projecting toward the inner diameter direction (direction toward the rotation axis O). The first, second, and third shoes 11, 12, and 13 are arranged in this order in the clockwise direction of FIG. Each of the shoes 11 to 13 is formed to extend in the X-axis direction, and their cross section in the direction perpendicular to the X-axis is provided in a substantially trapezoidal shape.

  The width | variety of each shoes 11-13 in the circumferential direction is provided in the substantially same magnitude | size. The circumferential width of the gap between the second shoe 12 and the third shoe 13 and the gap between the third shoe 13 and the first shoe 11 are set to be approximately the same size. The gap between the first shoe 11 and the second shoe 12 accommodates a first vane 41 having a wide width, which will be described later. Therefore, the circumferential width is slightly larger than the gap between the other shoes. .

  A bolt hole 110 through which the bolt b1 is inserted is formed in the X-axis direction at substantially the center of the trapezoidal cross section of the first shoe 11. Similarly, bolt holes 120 and 130 are formed through the second and third shoes 12 and 13, respectively.

  The end surfaces on the X axis positive direction side of the shoes 11 to 13 are fixedly fixed to the front plate 8. The end surfaces on the X-axis negative direction side of the respective shoes 11 to 13 provided as a part of the bottom surface 102 of the sealing recess 101 are firmly fixed to the rear plate 9.

  Plane portions 121 and 131 are formed on the second shoe 12 and the third shoe 13 in the clockwise direction when viewed from the X-axis positive direction side, respectively. The planar portions 121 and 131 are straight lines that are substantially coincident with a radial straight line passing through the rotation axis O of the housing body 10 when viewed from the X-axis direction.

  On the other hand, on the clockwise direction side of the first shoe 11, a built-up portion 112 is provided at the base portion (in the housing outer diameter direction), and a notch 113 is provided at the tip portion (in the housing inner diameter direction). . A flat portion 111 similar to the second shoe 12 and the third shoe 13 is formed between the build-up portion 112 and the cutout portion 113. The shape of the built-up portion 112 is a substantially circular arc shape having a predetermined curvature that is convex inward when viewed from the X-axis direction, and from the position where the first shoe 11 starts to rise along the inner peripheral surface of the housing body 10. It is formed to be gently curved.

  As shown in FIG. 6C, a positioning recess 114 having a diameter smaller than that of the bolt hole 110 is provided adjacent to the bolt hole 110 at the bottom portion 102 of the sealing recess 101 and on the build-up portion 112. ing. The build-up portion 112 enables the first shoe 11 to be provided with a positioning recess 114 and prevents the first vane 41 (described later) from contacting the first shoe 11 so that there is no problem in strength. The rigidity in the circumferential direction at the base portion of the shoe 11 is increased.

  Further, when viewed from the X-axis positive direction side, recesses 115, 125, and 135, which are wide grooves extending over the entire range in the X-axis direction, are formed on the counterclockwise direction side of the first to third shoes 11-13, respectively.

  The inner diameter-side surfaces of the tip portions 116, 126, and 136 of the first to third shoes 11 to 13 facing the rotation axis O are recessed along the outer peripheral surface 411 of the rotor 40 of the vane rotor 4 described later, as viewed from the X-axis direction. It is formed in an arc shape. A seal groove 117 is formed in the distal end portion 116 along the X-axis direction. Inside the seal groove 117, a seal member 118 that is in fluid-tight sliding contact with the outer peripheral surface of the rotor 40 and a seal spring (plate spring 119) that presses the seal member 118 toward the outer peripheral surface of the rotor 40 are fitted and held. Has been. The seal member 118 is made of a resin containing glass fiber, and has a substantially U shape when viewed from a direction perpendicular to the X axis. Similarly, seal members 128 and 138 and leaf springs 139 and 149 are also provided on the other tip portions 127 and 137, respectively (see FIG. 3).

  FIG. 9 shows the vane rotor 4. (A) is the front view which looked at the vane rotor 4 from the X-axis positive direction side, (b) shows DD sectional view of (a). Note that only a part of the oil passages 408 and 409 are shown. 10 and 11 show an intermediate state (material) in the manufacturing process of the vane rotor 4.

  The vane rotor 4 is formed from an aluminum extruded material as shown in FIG. First, an aluminum-based metal material is extruded from a mold, and is extruded into a continuous body having the outer peripheral shape of the rotor 40 and the vanes 41 to 43 as shown in FIG. 10 (this is referred to as a primary processed product Q1). Then, as shown in FIG. 11, the primary processed product Q1 is cut in the radial direction at constant axial intervals to form a plurality of members (these members are referred to as secondary processed product Q2). Then, the secondary processed product Q2 is cut to provide a final shape as shown in FIG. 9 by providing a boss portion 401, a fitting hole 402, and the like (this is referred to as a tertiary processed product Q3). . Thereafter, the entire outer peripheral surface of the tertiary processed product Q3 is subjected to an anodizing process to increase the hardness of the surface to obtain a finished product.

  The vane rotor 4 is a driven rotating body (driven member) that is rotatable relative to the pulley 100 (housing HSG), and is a vane member that rotates integrally with the camshaft 3a in the clockwise direction of FIG. The vane rotor 4 includes a rotor 40 that is a rotating shaft portion and first to third vanes 41, 42, and 43 that are three blades.

  The rotor 40 is fixed to the end portion 30 (insertion portion 301) on the X axis positive direction side of the camshaft 3a coaxially with the camshaft 3a by three cam bolts 31 to 33. The rotor 40 has a rotor body 400 and a boss portion 401 coaxially. The rotor body 400 is rotatably supported while sliding on seal members 118, 128, and 138 installed on the first to third shoes 11 to 13 of the housing, respectively.

  The boss portion 401 is formed so as to protrude from the rotor body 400 in the negative X-axis direction. The boss portion 401 is inserted into the support hole 92 of the rear plate 9 and is installed with respect to the support hole 92 through a slight gap. The outer diameter (the diameter of the outer peripheral surface) of the boss 401 is slightly smaller than the outer diameter of the rotor body 400. The length L3 in the X-axis direction of the boss 401 is slightly shorter than the length L2 in the X-axis direction of the sealing recess 101. The length of the rotor body 400 in the X-axis direction is substantially equal to the length L1 of the housing body 10 excluding the sealing recess 101 in the X-axis direction.

  On the inner periphery of the boss 401 and the rotor body 400, a fitting hole 402 having substantially the same diameter as the camshaft 3a is slightly less than 2/3 of the rotor body 400 from the X-axis negative direction toward the X-axis positive direction. It is drilled substantially coaxially with the rotor 40 to the depth. In the rotor body 400, a recess 403 having a diameter slightly smaller than the diameter of the rotor body 400 is substantially coaxial with the rotor 40 from the X axis positive direction side to the X axis negative direction to a depth of about 13% of the rotor body 400. Has been drilled.

  Further, bolt holes 404 to 406 through which the cam bolts 31 to 33 are inserted are formed in the rotor body 400 in the X-axis direction, and the recess 403 and the fitting hole 402 are communicated with each other. The bolt holes 404 to 406 are provided at substantially equal intervals around the rotation axis O of the rotor 40. The rotor body 400 is formed with a small-diameter air vent hole 407 passing through the rotation shaft O so as to communicate the fitting hole 402 and the recess 403.

  The first to third vanes 41 to 43 are provided radially on the outer peripheral surface of the rotor body 400 so as to protrude toward the outer diameter direction (the outer direction away from the rotation axis O) at substantially equal intervals in the circumferential direction. It has been. The first, second, and third vanes 41, 42, and 43 are arranged in this order in the clockwise direction of FIG. Each of the vanes 41 to 43 is formed integrally with the rotor 40 (rotor main body 400), and the cross-sectional shape in the direction perpendicular to the X axis of each of the vanes 41 to 43 is wider in the circumferential direction toward the outer diameter direction. It is formed in a substantially trapezoidal shape.

  The lengths of the vanes 41 to 43 in the X-axis direction are the same as the length L1 of the rotor body 400 in the X-axis direction. In a state where the vane rotor 4 is installed in the housing HSG, the surfaces on the X axis positive direction side of the vanes 41 to 43 are opposed to the surfaces on the X axis negative direction side of the front plate 8 with a very small gap. doing. Further, the surfaces on the X axis negative direction side of the vanes 41 to 43 are opposed to the surfaces on the X axis positive direction side of the rear plate 9 with a very small gap.

  The widths of the second and third vanes 42 and 43 in the circumferential direction of the vane rotor 4 are substantially the same. The circumferential width of the first vane 41 is formed wider than the second and third vanes 42 and 43, and is the maximum width among the vanes 41 to 43, and can accommodate the lock mechanism 5 described later. .

  The centers of gravity of the vanes 41 to 43 are provided at substantially equal intervals in the circumferential direction of the vane rotor 4. However, the first vane 41 is wide and slightly heavier than the other vanes 42 and 43 because the lock mechanism 5 is provided. For this reason, the gap between the first vane 41 and the second vane 42 and the gap between the third vane 43 and the first vane 41 are slightly wider than the gap between the second vane 42 and the third vane 43. Thus, the center of gravity of the vane rotor 4 is brought close to the rotation axis O as a whole.

  With the vane rotor 4 installed in the housing HSG, the first vane 41 is between the first shoe 11 and the second shoe 12, the second vane 42 is between the second shoe 12 and the third shoe 13, and the third vane. Reference numerals 43 are arranged in the gaps between the third shoe 13 and the first shoe 11, respectively.

  The outer peripheral surfaces 411, 421, and 431 on the rotor outer diameter side (the side away from the rotation axis O) of each vane 41 to 43 are formed in an arc shape along the inner peripheral surface of the housing body 10 when viewed from the X-axis direction. A groove 412 is formed in the outer peripheral surface 411 of the first vane 41 along the X-axis direction. Inside the groove 412, a seal member 413 that slides in liquid-tight contact with the inner peripheral surface of the housing body 10 and a seal spring (plate spring 414) that presses the seal member 413 toward the inner peripheral surface are fitted. Is retained. Similarly, seal members 423 and 433 and leaf springs 424 and 434 are provided on the outer peripheral surfaces 421 and 431 of the second and third vanes 42 and 43, respectively (see FIG. 2).

  A planar portion 415 is formed on the counterclockwise direction side of the first vane 41 when viewed from the X axis positive direction side. The flat portion 415 is a straight line that substantially matches a radial straight line that passes through the rotation axis O of the rotor when viewed from the X-axis direction. In addition, a notch 416 is provided at the root portion on the inner side in the rotor radial direction from the plane portion 415. The shape of the notch 416 is an arc shape that is convex (depressed) inward and has a predetermined curvature as viewed from the X-axis direction. Similarly, the second and third vanes 42 and 43 are provided with flat portions 425 and 435 and notches 426 and 436, respectively.

  As viewed from the X axis positive direction side, on the counterclockwise direction side of the first vane 41, a notch 417 is provided at a tip portion on the outer side in the rotor radial direction from the plane portion 415. The shape of the notch 417 is an arc shape having a curvature slightly larger than that of the built-up portion 112 of the first shoe 11 (substantially equal to a recess 900 described later), as viewed from the X-axis direction. The notch 417 makes it possible for the flat portion 415 of the first vane 41 to come into contact with the flat portion 111 of the first shoe 11 between the surfaces, and helps to reduce the weight of the first vane 41. .

  On the other hand, as viewed from the X axis positive direction side, concave portions 418, 428, and 438, which are wide grooves extending over the entire range in the X axis direction, are formed on the clockwise direction sides of the first to third vanes 41 to 43, respectively.

  Further, when viewed from the X axis positive direction side, the outer periphery of the rotor 40 (rotor main body 400) extends from the root portion (continuous to the rotor 40) to a predetermined circumferential direction length on the clockwise direction side of the first vane 41. A convex portion extending in the clockwise direction is provided. The convex portion is continuous with the root portion of the first vane 41 and protrudes from the outer periphery of the rotor 40 (rotor main body 400) to the outer end of the first vane 41 from the rotor 40 (rotor main body 400). The stopper portion 419 is configured by this convex portion. Similarly, a stopper portion 429 is configured on the clockwise direction side of the root portion of the second vane 42.

  The rotor main body 400 is provided with three retard oil passages 408 and three advance oil passages 409 that connect the fitting holes 402 and the outer peripheral surface of the rotor 40 (rotor main body 400). The first vane 41 is a substantially intermediate position in the X-axis direction of the first vane 41 when viewed from the direction perpendicular to the X-axis (see FIG. 9B) and is viewed from the positive direction of the X-axis. A retarded oil passage 408 is formed through the base of the vane 41 on the clockwise direction side (see FIG. 4) in the rotor radial direction. Further, it is on the negative X-axis side of the first vane 41 when viewed from the direction perpendicular to the X-axis (see FIG. 9B), and the counterclockwise direction of the first vane 41 when viewed from the positive X-axis direction. An advance oil passage 409 is formed through the base of the side (see FIG. 4) in the rotor radial direction. Similarly, the advance oil passage 408 and the retard oil passage 409 are formed through the bases of the other vanes 42 and 43, respectively.

  The vane rotor 4 forms an advance chamber A and a retard chamber R through which fluid (hydraulic oil) is supplied and discharged with the housing 1. That is, when viewed from the X-axis direction, three oil chambers are separated between adjacent shoes and the outer peripheral surface of the rotor 40 (rotor body 400), and these oil chambers are advanced by vanes 41 and the like. The chamber A and the retarded angle chamber R are separated. The advance chamber A and the retard chamber R are each kept in a liquid-tight state by the seal member 113 and the like. The hydraulic oil supplied from the oil pump P is introduced into these oil chambers A and R, and rotation is transmitted between the vane rotor 4 and the housing HSG via the hydraulic oil.

  Specifically, the X-axis negative direction side surface of the front plate 8, the X-axis positive direction side surface of the rear plate 9, both side surfaces in the circumferential direction of the vanes 41 to 43, and the shoes 11 to 13 are used. The three hydraulic working chambers, that is, the three advance chambers A1, A2, A3 and the three retard chambers R1, R2, R3 are separated from each other in the circumferential direction. For example, as shown in FIG. 4, the first advance chamber A <b> 1 is defined between the clockwise surface of the first shoe 11 and the counterclockwise surface of the first vane 41. In addition, a first retardation chamber R1 is defined between the surface on the clockwise direction side of the first vane 41 and the surface on the counterclockwise direction side of the second shoe 12.

  Similarly, the second advance chamber A2 is provided between the second shoe 12 and the second vane 42, and the second retard chamber R2, the third shoe 13 and the third shoe are provided between the second vane 42 and the third shoe 13. A third advance chamber A3 is defined between the vane 43 and a third retard chamber R3 is defined between the third vane 43 and the first shoe 11.

  When the vane rotor 4 attempts to rotate relative to the housing HSG in a counterclockwise direction by a predetermined angle or more, as shown in FIG. 4, the flat portion 111 provided on the side surface in the clockwise direction of the first shoe 11 and the first vane The flat portions 415 provided on the side surfaces of the counterclockwise direction 41 are in contact with each other and come into contact with each other. At this time, the flat portions 121 and 425 of the second shoe 12 and the second vane 42 face each other with a slight gap, and the circumferential side surfaces of the second shoe 12 and the second vane 42 do not contact each other (non-contact state) Maintain). Similarly, the flat portions 131 and 435 of the third shoe 13 and the third vane 43 are opposed to each other through a slight gap and do not contact each other.

  That is, the rotation of the vane rotor 4 in the counterclockwise direction with respect to the housing HSG is restricted by the contact between the flat surface portion 111 of the first shoe 11 and the flat surface portion 415 of the first vane 41. In this manner, the first stopper 11 that restricts the relative rotation of the vane rotor 4 in the counterclockwise direction (retard direction) is configured by the flat portions 111 and 415 that are the circumferential side surfaces of the first shoe 11 and the first vane 41. Yes.

  In the relative rotation restricting position of FIG. 4, the end surface on the clockwise side of the stopper portion 419 provided at the base portion of the first vane 41 and the counterclockwise direction side of the distal end portion 126 in the housing inner diameter direction of the second shoe 12. The angle α formed with the end surface with respect to the rotation axis O is opposite to the clockwise end surface of the stopper portion 429 provided at the root portion of the second vane 42 and the housing inner diameter direction front end portion 136 of the third shoe 13. It is slightly smaller than the angle β formed with the end surface on the clockwise direction side with respect to the rotation axis O.

  Therefore, when the vane rotor 4 rotates relative to the housing HSG in the clockwise direction from the position of FIG. 4 by an angle α, as shown in FIG. 5, the distal end portion 126 of the second shoe 12 and the stopper portion 419 of the first vane 41. Are in contact with each other and come into contact with each other. At this time, the tip portion 136 of the third shoe 13 and the stopper portion 429 of the second vane 42 face each other with a slight gap in the circumferential direction, and the third shoe 13 and the second vane 42 (stopper portion 429). Do not contact each other (maintain a non-contact state). Also, the first shoe 11 and the third vane 43 are opposed to each other with a predetermined gap, and do not contact each other.

  That is, the rotation of the vane rotor 4 in the clockwise direction with respect to the housing HSG is restricted by the front end portion 126 of the second shoe 12 and the stopper portion 419 of the first vane 11 contacting each other. Thus, the clockwise direction of the vane rotor 4 is formed by the clockwise side surface of the stopper portion 419 and the counterclockwise side surface of the second shoe 12 (the front end portion 126), which is a portion protruding from the rotor 40 toward the outer peripheral side. A second stopper portion that restricts relative rotation in the advance angle direction is configured. The relative rotation conversion angle of the vane rotor 4 with respect to the housing HSG is adjusted by the first and second stopper portions.

  The contact area between the tip 126 of the second shoe 12 and the stopper 419 of the first vane 11 (the contact area S2 of the second stopper) is the flat portion 111 of the first shoe 11 in the counterclockwise direction. Is smaller than the contact area between the first vane 41 and the flat surface portion 415 (contact area S1 of the first stopper portion) (S1> S2).

  Note that the volume of the retard chamber R or the advance chamber A is prevented from becoming zero over the entire angle range in which the vane rotor 4 rotates relative to the housing HSG, and the retard oil passage 408 or the advance angle is prevented. An opening of the oil passage 409 to the retard chamber R or the advance chamber A is secured. For example, in FIG. 4, the volume of the first advance chamber A1 and the opening of the advance oil passage 409 are determined by the space formed between the notch 113 of the first shoe 11 and the notch 416 of the first vane 41. Is secured. Similarly, the second space is formed by the space (the gap) formed between the flat portions 121 and 131 of the second and third shoes 12 and 13 and the cutout portions 426 and 436 and the flat portions 425 and 435 of the second and third vanes 42 and 43. The volumes of the third advance chambers A2 and A3 and the openings of the advance oil passages 409 and 409 are secured.

  The front plate 8 is formed by forging an iron-based metal material (iron alloy), and is formed in a disk (disk) shape that is thinner than the rear plate 9 described later. The front plate 8 seals the distal end side of the housing body 10 in the cam shaft axial direction, that is, the end of the advance chamber A and the retard chamber R on the X axis positive direction side of the housing body 10.

  As shown in FIG. 3, the diameter of the front plate 8 is slightly larger than the diameter (maximum diameter) of the pulley 100, and the outer peripheral portion 80 of the front plate 8 projects to the outer diameter direction side of the pulley 100. ing.

  As shown in FIG. 2, a large-diameter hole 81 into which the cam bolts 31 to 33 are inserted (when the apparatus 1 is assembled) is formed in the X-axis direction at a substantially central portion of the front plate 8 on the X-axis positive direction side. In addition, a cylindrical female screw portion 82 that surrounds the large-diameter hole 81 and protrudes in the positive X-axis direction is formed. A female screw 820 to which a male screw 700 of a plug 7 described later is screwed is formed on the inner peripheral surface of the female screw portion 82 (large diameter hole 81). An annular groove 821 for installing the seal ring S4 is formed on the annular end face of the female screw portion 82 on the X axis positive direction side.

  In the front plate 8, three bolt holes 83, 84, and 85 through which the bolts b <b> 1 to b <b> 3 are inserted are formed in the X-axis direction between the female screw portion 82 and the outer peripheral portion 80 at substantially equal intervals in the circumferential direction. ing. These bolt holes 83 to 85 are provided at respective locations facing the bolt holes 110 to 130 of the shoes 11 to 13 of the housing body 10 in the X-axis direction.

  In addition, around the bolt holes 83 to 85 in the front plate 8, in order to increase the strength against the axial force of the bolts b1 to b3, thick portions 86, 87, which are slightly thicker in the X-axis direction than other portions. 88 are formed respectively. The thick portions 86 to 88 are continuous with the female screw portion 82 while spreading toward the inner diameter direction. In other words, the front plate 8 is formed so as to be thinned as much as possible in the X-axis direction except for the thick portions 86 to 88 for securing the strength against the bolts b1 to b3.

  FIG. 12 is a perspective view of the front plate 8 as viewed from the X-axis negative direction side. A single annular groove 89 into which the seal ring S3 is inserted and installed is formed on the surface on the X axis negative direction side. The groove 89 extends along the inner peripheral side of the outer peripheral portion 80 from the outer peripheral edge of the front plate 8 through a slight radial distance r and bypasses the bolt holes 83 to 85 to the inner peripheral side of the bolt holes 83 to 85. It is provided so as to pass through (the rotation axis O side), and has a shape like a three-leaf clover that is recessed inward at three locations in the circumferential direction as a whole.

  The plug 7 is a bottomed cylindrical lid member and is formed by forging a ferrous metal material. The plug 7 includes a cylindrical male screw portion 70 extending in the X-axis direction, a partition wall portion 71 that closes an opening of the male screw portion 70, and a flange portion 72 that extends from the end of the male screw portion 70 on the X-axis positive direction side to the outer peripheral side. have. A male screw 700 is formed on the outer periphery of the male screw portion 70. In addition, a regular hexagonal columnar bolt head 710 is integrally provided in the center of the partition wall 71, and the plug 7 is screwed into the front plate 8 using the bolt head 710, and the female screw 820 of the front plate 8 is used. The large-diameter hole 81 of the front plate 8 is sealed by screwing the male screw 700 of the plug 7 onto the front plate 8.

  The rear plate 9 is inserted and fixed in the sealing recess 101 of the housing body 10, and is on the axial camshaft side of the housing body 10, that is, on the X axis negative direction side of the advance chamber A and the retard chamber R in the housing body 10. Seal the edges. The rear plate 9 is formed by forging a ferrous metal material such as S45C or S48, and has a disk-shaped plate body 90 and a bearing portion 91.

  The bearing portion 91 is a cylindrical extending portion provided on the X-axis negative direction side of the plate body 90, protrudes from the approximate center of the plate body 90 in the X-axis negative direction, and is formed substantially coaxially with the rotation axis O. Has been. A support hole 92 that is a hole through which the camshaft 3 a is inserted is provided on the inner periphery of the bearing portion 91. The support hole 92 is formed through the rear plate 9 in the X-axis direction. The diameter of the support hole 92 is slightly smaller than the large diameter hole 81 of the front plate 8.

  The boss portion 401 of the vane rotor 4 is inserted into the support hole 92. The boss portion 401 is installed with respect to the support hole 92 through a slight gap. By inserting the boss portion 401 into the support hole 92, the vane rotor 4 is positioned on the rear plate 9. The rear plate 9 (bearing portion 91) rotatably supports the vane rotor 4 (boss portion 401).

  An oil seal is installed on the outer peripheral surface of the bearing portion 91 on the X axis negative direction side, and the bearing portion 91 is rotatably supported by a cylinder block of the engine via the oil seal. The oil seal is for guiding hydraulic oil leaking from the device 1a through the gap CL (see FIG. 3) between the outer periphery of the camshaft 3a and the inner periphery of the bearing portion 91 to the inside of the engine (cylinder block). The space between the cylinder block and the bearing 91 is kept liquid-tight. As a result, the hydraulic oil leaking from the device 1a through the gap CL is prevented from coming into contact with the belt B and other auxiliary machines.

  Since the rear plate 9 is made of an iron-based metal material, the bearing portion 91 is also made of iron and has high hardness. Therefore, it is possible to prevent wear caused by the sliding of the (iron-made) oil seal on the outer peripheral surface of the bearing portion 91, and to more reliably seal between the cylinder block and the bearing portion 91.

  Moreover, since the plug 7, the front plate 8, and the rear plate 9 are formed by forging an iron-based metal material, the hydraulic oil of the apparatus 1a is different from the case where the iron-based metal material is formed by, for example, sintering. Oozes out of these members and is prevented from leaking out.

  The plate body 90 has a width that is slightly larger than the depth of the sealing recess 101 (the length L2 in the X-axis direction) at the maximum. The X-axis direction width of the outer peripheral surface 93 of the plate main body 90 is provided to have substantially the same dimension as the depth of the sealing recess 101 (X-axis direction length L2). The diameter of the plate body 90 is provided to be approximately the same as the diameter (R × 2) of the sealing recess 101.

  The plate body 90 is provided with three female screw portions 901, 902, and 903 that surround the bearing portion 91 and are substantially equidistant in the circumferential direction. Each of the female screw portions 901 to 903 has a bolt hole formed so as to penetrate the plate body 90 in the X-axis direction, and a female screw is formed on the inner periphery of the bolt hole. The male threads at the front ends of the bolts b1 to b3 on the X-axis negative direction side are screwed into the female threads, respectively. These female threaded portions 901 to 903 (bolt holes) are respectively opposed to the bolt holes 110 to 130 of the shoes 11 to 13 (and the bolt holes 83 to 85 of the front plate 8) of the housing body 10 in the X-axis direction. Is provided.

  As shown in FIG. 2, when viewed from the X axis positive direction side, the plate body 90 is adjacent to the female thread portion 901 (opposite to the bolt hole 110 of the first shoe 11) in the clockwise direction, and has a bottom. The concave portion 900 is provided to a predetermined depth inside the plate body 90 in the negative direction of the X axis.

  A bottomed pin hole 904 is provided at a position adjacent to the concave portion 900 in the counterclockwise direction on the outer peripheral side of the surface of the plate body 90 on the X axis positive direction side. Specifically, the pin hole 904 is formed between the concave portion 900 and the female screw portion 901 at a position corresponding to the positioning concave portion 114 (see FIG. 6C) of the housing body 100 in the plate radial direction. ing. FIG. 13 is a partial cross-sectional view passing through the axis of the pin hole 904. As shown in FIG. 13, the pin hole 904 is formed in a bag shape up to a predetermined depth of the plate body 90 toward the X-axis negative direction side. A positioning pin 905 is press-fitted and fixed inside the pin hole 904.

  The positioning pin 905 is a dowel pin, and one end of the positioning pin 905 projects from the surface of the plate body 90 on the X axis positive direction side to a predetermined height in the X axis positive direction. The one end is provided with a slightly smaller diameter than the positioning recess 114, and is engaged (fitted) into the positioning recess 114 from the X-axis negative direction side. The diameter of the one end of the positioning pin 905 and the diameter of the positioning recess 114 are such that the circumferential play between the housing body 10 and the rear plate 9 does not occur when the positioning pin 905 is engaged with the positioning recess 114. Respectively.

  In the pin hole 904, when the positioning pin 905 is engaged with the positioning recess 114, the bolt hole 110 of the housing body 10 (first shoe 11) and the female screw portion 901 of the rear plate 9 are positioned substantially coaxially. In addition, in a state where the first vane 41 (planar portion 415) of the vane rotor 4 is in contact with the first shoe 11 (planar portion 111) (see FIG. 4), a sliding hole 501 and a rear plate described later of the first vane 41 are provided. Nine concave portions 900 are arranged on the rear plate 9 so as to be substantially coaxial. The pin hole 904 is disposed closer to the oil chamber (first retardation chamber R1) than the seal grooves 906 and 907 described below, and the positioning pin 905 and the recess 900 are close to each other.

  On the outer peripheral surface 93 that surrounds the outer periphery of the plate main body 90, one groove 906 into which the seal ring S1 is inserted and installed is formed in the circumferential direction. In addition, annular grooves 907, 908, and 909, into which the seal ring S2 is inserted and installed, are formed on the surface of the plate body 90 on the X axis positive direction side so as to surround the female screw portions 901 to 903, respectively.

(Seal structure between housing body and plate)
The front plate 8, the housing main body 10, and the rear plate 9 are integrally coupled together by bolts b1 to b3 from the X-axis direction. The bolts b1 to b3 are respectively inserted into the bolt holes 83 to 85 of the front plate 8 and the bolt holes 110 to 130 of the housing body 10 from the X axis positive direction side, and screwed to the rear plates 9 901 to 903. Then, the front plate 8 and the rear plate 9 are fastened and fixed to the housing body 10. At that time, seal rings S1 to S3 are interposed between the housing body 10 and the rear plate 9 and between the front plate 8 and the housing body 10, respectively. Further, a seal ring S4 is interposed between the plug 7 and the front plate 8. These seal rings S1 to S4 maintain the liquid tightness in the housing HSG. The seal rings S1 to S4 are made of acrylic or fluorine rubber.

  The seal ring S1 is an annular seal member (an O-ring having a circular cross section) disposed between the wall surface 103 of the sealing recess 101 of the housing body 10 and the outer peripheral surface 93 of the rear plate 9 (plate body 90). is there. With the seal ring S1 installed in the groove 906 of the rear plate 9, the wall surface 103 of the sealing recess 101 is pressed against the seal ring S1, thereby compressing the seal ring S1. As a result, a sealing function is exhibited, and leakage of hydraulic oil from the joint surface between the rear plate 9 and the housing body 10 is prevented.

  The seal ring S2 is disposed between the periphery of each of the female screw portions 901 to 903 on the X axis positive direction end surface of the rear plate 9 and the X axis negative direction end surface of the housing body 10 (the shoes 11 to 13). This is an annular seal member (O-ring having a circular cross section). With the seal ring S2 installed in each of the grooves 907 to 909 around the female screw portions 901 to 903, the end surface on the X axis negative direction side of the housing body 10 (the shoes 11 to 13) is moved by the axial force of the bolts b1 to b3. The seal ring S2 is compressed by pressing against the seal ring S2. As a result, a sealing function is exhibited, and leakage of hydraulic oil from the joint surface between the rear plate 9 and the housing body 10 (specifically, the bolt holes of the female screw portions 901 to 903) is prevented.

  The seal ring S3 is located between the facing portion of the front plate 8 and the housing body 10, that is, between the end surface on the X-axis negative direction side of the front plate 8 and the end surface on the X-axis positive direction side of the housing body 10 (the shoes 11 to 13). An annular seal member (an O-ring having a circular cross section) disposed on the surface. The overall shape of the seal ring S3 is a three-leaf clover shape that is substantially the same as the groove 89 of the front plate 8. With the seal ring S3 installed in the groove 89, the X-axis positive direction end surface of the housing body 10 (the shoes 11 to 13) is pressed against the seal ring S3 by the axial force of the bolts b1 to b3 to compress the seal ring S3. To do. As a result, a sealing function is exhibited, and leakage of hydraulic oil from the joint surface between the front plate 8 and the housing body 10 is prevented.

  The seal ring S4 is an annular seal member (an O-ring having a circular cross section) provided between the end surface on the X axis positive direction side of the female screw portion 82 of the front plate 8 and the end surface on the X axis positive direction side of the flange portion 72 of the plug 7. ). In a state where the seal ring S4 is installed in the groove 821 of the female thread portion 82, the end face on the X-axis positive direction side of the flange portion 72 of the plug 7 is pressed against the seal ring S4. The leakage of the hydraulic oil from the joint surface with 8 is prevented.

  The camshaft 3a is made of iron and is rotatably supported on the inner side of the upper end of the cylinder head of the engine via a bearing. A drive cam (intake cam) is provided on the outer peripheral surface of the camshaft 3a at a position corresponding to the position of the intake valve. When the camshaft 3a rotates, the intake cam opens and closes the intake valve via a valve lifter or a rocker arm. Operate.

  As shown in FIG. 3, an insertion portion 301 that is inserted into the fitting hole 402 of the vane rotor 4 and is fitted into the fitting hole 402 is formed at the end 30 on the positive side of the X axis of the camshaft 3 a. . Further, as described above, the boss portion 401 is formed in the vane rotor 4 so as to surround the fitting hole 402, and the boss portion 401 is inserted through the support hole 92 of the rear plate 9 and installed. Therefore, in a state where the insertion portion 301 of the camshaft 3 a is fitted in the fitting hole 402 and fixed to the vane rotor 4, the end portion 30 of the camshaft 3 a is inserted through the support hole 92 of the rear plate 9. In other words, the vane rotor 4 is fixed to the end 30 of the camshaft 3 a via the support hole 92. When the end 30 is inserted into the fitting hole 402, the boss 401 is previously inserted into the support hole 92, and the vane rotor 4 (fitting hole 402) is positioned with respect to the rear plate 9 (housing HSG). Therefore, it is easy to insert.

  An air vent hole 31 is formed through the rotary shaft O on the positive side of the X axis of the camshaft 3a. The air vent hole 31 communicates with the inside of the engine. In addition, at the end portion 30, three female screw portions 32 are substantially equal around the rotation axis O (air vent hole 31) of the camshaft 3 a at positions facing the bolt holes 404 to 406 of the vane rotor 4 in the X-axis direction. It is formed at intervals. The female screw portion 32 has a female screw hole formed from the X axis positive direction side to a predetermined depth of the end portion 30.

  With the insertion part 301 fitted in the fitting hole 402, the cam bolts 31 to 33 are respectively inserted into the bolt holes 404 to 406 of the vane rotor 4 from the X axis positive direction side, and the tip ends of the cam bolts 31 to 33 are The end 30 of the camshaft 3 a is fastened and fixed integrally with the vane rotor 4 by being inserted into the female screw 32 and screwed together. At this time, the recess 403 of the vane rotor 4 communicates with the inside of the engine via the air vent hole 407 and the air vent hole 31.

  Note that when the vane rotor 4 is fixed to the camshaft 3a, for example, when the camshaft 3 is fastened with only one cam bolt, the vane rotor 4 slips with respect to the camshaft 3a, or a large surface pressure is applied to the vane rotor 4 due to the axial force of the cam bolt. The vane rotor 4 made of an aluminum material may be deformed. On the other hand, in the first embodiment, since the three cam bolts 31 to 33 are used for fastening, there is no possibility that the above-mentioned slip occurs, and the surface pressure acting on the vane rotor 4 is reduced by reducing the axial force of each cam bolt. Since it can be made small, deformation can also be suppressed.

  The device 1a fixed to the camshaft 3a is configured to be locked by the engaging member (lock piston 51) at the most retarded angle position where rotation is restricted by the first stopper portion. The lock piston 51 is an engagement member provided in the vane rotor 4 and moves forward and backward in and out of the X axis direction, which is the rotation axis direction according to the state of the engine, so that the relative rotation between the vane rotor 4 and the housing HSG is performed. A plunger that locks or releases this locked state. This will be specifically described below.

  Between the 1st vane 41 and the rear plate 9, the lock mechanism 5 which restrains rotation of the vane rotor 4 with respect to the rear plate 9 (housing HSG), and can cancel | release this restraint is provided. The lock mechanism 5 includes a lock piston 51, a lock hole component (sleeve 52), a coil spring 53, and a spring retainer 54. FIG. 14 is a partial cross section taken along line BB of FIG. 4 and shows the operating state of the lock piston 51 when the engine is stopped (when the engine is started).

  A sliding hole 501 is formed through the first vane 41 in the X-axis direction. A hollow cylindrical sealing member 502 is press-fitted into the inner periphery of the sliding hole 501 on the X axis negative direction side. The sealing member 502 is made by forming an iron alloy (carbon steel) such as S45C in a ring shape and carburizing and quenching. Inside the sliding hole 501, a lock piston 51 is slidably installed in the X-axis direction.

  The lock piston 51 is a bottomed cylindrical (pin-shaped) iron member having a bottom portion 510 on the X-axis negative direction side. A tip portion 511 having a substantially truncated cone shape (a taper shape having a substantially trapezoidal cross section in the axial direction) is formed on the X axis negative direction side adjacent to the bottom portion 510 via a step between the bottom portion 510. A cylindrical sliding portion 512 is formed adjacent to the bottom portion 510 and on the X axis positive direction side. An annular flange 513 is formed at the end on the X-axis positive direction side adjacent to the sliding portion 512.

  The sliding portion 512 has a diameter that is substantially the same as the inner peripheral surface of the sealing member 502. The X axis negative direction side of the sliding portion 512 is accommodated in the sealing member 502 and slides in the X axis direction with respect to the inner periphery of the sealing member 502. Since the sealing member 502 is made of iron and has high hardness, it is possible to prevent wear caused by the sliding of the sliding portion 512. Further, the outer diameter of the flange portion 513 is provided to be approximately the same diameter as the inner peripheral surface of the sliding hole 501. The flange portion 513 is accommodated in the sliding hole 501 and slides with respect to the sliding hole 501. Inside the first vane 41, the X-axis positive direction surface of the sealing member 502, the X-axis negative direction surface of the flange portion 513, the inner peripheral surface of the sliding hole 501, and the outer peripheral surface of the sliding portion 512 A pressure receiving chamber 55 is formed between the two.

  On the other hand, when viewed from the X-axis direction, the rear plate 9 is formed with a recess 900 at a position substantially coincident with the lock piston 51 at the (most retarded angle) position in FIG. The recess 900 is a position biased toward the advance chamber A1 in the oil chamber sandwiched between the first shoe 11 and the second shoe 12 when the rear plate 9 is viewed from the positive X-axis direction side. Is provided in a bottomed shape adjacent to the clockwise direction side of the rear plate 9 so as not to penetrate the rear plate 9.

  A hollow cylindrical engaging concave portion (sleeve 52 which is a lock hole constituting member) made of a member different from the rear plate 9 is fitted into the concave portion 900 by press-fitting. In other words, the sleeve 52 is fixedly installed on the rear plate 9 so as to be locked to the recess 900. A lock hole 521 is provided on the inner periphery of the sleeve 52. The cross section cut by a plane passing through the axis of the sleeve 52 is substantially trapezoidal, and the lock hole 521 gradually increases in diameter toward the opening on the X axis positive direction side. Due to the above-described position of the recess 900, the lock hole 521 (sleeve 52) is positioned on the retard side (when the lock piston 51 is engaged, the relative conversion angle between the housing HSG and the vane rotor 4 becomes an optimum conversion angle when the engine is started ( (Most retarded position).

  An annular spring retainer 54 having an outer diameter substantially the same as the inner periphery of the sliding hole 501 is installed on the X axis positive direction side of the sliding hole 501. The X-axis positive direction surface of the spring retainer 54 abuts the X-axis negative direction surface of the front plate 8, and the X-axis negative direction surface of the spring retainer 54 is the X axis of the lock piston 51 (flange portion 513). It is in contact with the surface on the positive direction side.

  A coil spring 53 is elastically mounted (installed in a compressed state) between the surface of the front plate 8 on the X axis negative direction side and the bottom 510 of the lock piston 51. In addition, since the front plate 8 is made of an iron-based metal material, the hardness is high. Therefore, it is possible to prevent wear resulting from the sliding of the coil spring 53 on the surface of the front plate 8 on the X axis negative direction side.

  The coil spring 53 always urges the lock piston 51 toward the X-axis negative direction side, that is, the rear plate 9 (the lock hole 521 of the sleeve 52). The X-axis positive direction side of the coil spring 53 is fitted to the inner periphery of the spring retainer 54, thereby restricting the displacement of the coil spring 53 (in the radial direction of the lock piston 51) in the sliding hole 501. Yes.

  When the vane rotor 4 rotates relative to the most retarded angle and the rotation is restricted by the first stopper portion, that is, the first vane 41 (the flat surface portion 415) and the first shoe 11 (the flat surface portion 111) contact each other. When the volume of the advance chamber A1 is minimized, the position of the lock piston 51 and the position of the lock hole 521 overlap substantially coaxially when viewed from the X-axis direction. At this time, the lock piston 51 is pressed by the spring force of the coil spring 53 to move / protrude in the negative direction of the X axis, and the tip 511 advances from the first vane 41 (sliding hole 501) and fits into the lock hole 521. Include. As a result, the lock piston 51 engages with the lock hole 521, and relative rotation between the rear plate 9 and the vane rotor 4, that is, relative rotation between the housing HSG and the camshaft 3a is restricted (locked).

  As described above, the tip portion 511 has a substantially truncated cone shape and is easily engaged with the lock hole 521. That is, both the tip 511 and the lock hole 521 are provided so as to have a smaller diameter in the negative direction of the X axis. The inclination of the inner peripheral surface of the lock hole 521 with respect to the X axis is substantially equal to the inclination of the outer peripheral surface of the tip 511 with respect to the X axis.

  As shown in FIG. 14, the axial center of the lock hole 521 is positioned in the counterclockwise direction of FIG. 4 (on the first shoe 11 side) with respect to the axial center of the tip 511. It is provided to be slightly offset. Therefore, when the tip portion 511 advances in the negative direction of the X axis and fits into the lock hole 521, the surface on the clockwise direction side of the tip portion 511 is in sliding contact with the surface on the counterclockwise direction side of the lock hole 521. The tip portion 511 (lock piston 51) receives a counterclockwise reaction force due to the wedge effect. As a result, the first vane 41 that houses the lock piston 51 receives a counterclockwise reaction force, and the first vane 41 is pressed against the first shoe 11.

  In addition, the first vane 41 is formed with a communication hole 56 that allows the retard chamber R1 and the pressure receiving chamber 550 to communicate with each other. Similarly, in the first vane 41, a communication groove 57 that connects the advance chamber A1 and the lock hole 521 is formed on the surface in the negative X-axis direction. The lock piston 51 receives an oil pressure on the positive side in the X axis direction at the flange portion 513 by the hydraulic pressure (fluid pressure) supplied from the retard chamber R1 into the pressure receiving chamber 550 through the communication hole 56. Further, the lock piston 51 receives hydraulic pressure on the X axis positive direction side at the distal end portion 511 by the hydraulic pressure supplied from the advance chamber A1 into the lock hole 521 via the communication groove 57.

  The lock piston 51 moves to the X-axis positive direction side against the spring force of the coil spring 53 due to any of the above oil pressures, and the front end portion 511 is retracted from the lock hole 521 and the sliding hole of the rear plate 9 is moved. Fits into 501. As a result, the engagement between the lock piston 51 and the lock hole 521 is released. Thus, the communication hole 56 and the communication groove 57 function as a release hydraulic circuit. On the other hand, the coil spring 53 that is an engaging elastic member functions as a lock state maintaining mechanism. The communication hole 56 and the communication groove 57 together with the coil spring 53 constitute an engagement / disengagement mechanism for the lock piston 51.

  As shown in FIG. 9A, a rectangular notch groove 58 that communicates the concave portion 403 of the rotor 40 and the sliding hole 501 of the first vane 41 is provided on the X axis positive direction side of the vane rotor. It has been. The notch groove 58 has substantially the same depth as the recess 403, extends in the outer diameter direction from the recess 403, and is formed so as to communicate the recess 403 and the X axis positive direction side of the lock piston. On the other hand, the recess 403 communicates with the inside of the engine through the air vent holes 407 and 31 (see FIG. 3).

  Therefore, the air on the X-axis positive direction side (the side where the coil spring 53 is installed) of the lock piston 51 is transmitted to the inside of the engine through the notch groove 58, the recess 403, and the air vent holes 407 and 31. As a result, the back pressure of the lock piston 51 is released, so that the favorable operation of the lock piston 51 (sliding in the sliding hole 501) is ensured in the entire relative rotation range of the vane rotor 4.

  The hydraulic supply / discharge mechanism 2 supplies the hydraulic oil to the advance chambers A1 to A3 or the retard chambers R1 to R3 and discharges it, thereby rotating the vane rotor 4 forward and backward by a predetermined angle with respect to the housing HSG. That is, by adjusting the supply and discharge of hydraulic oil to change the oil chamber volume, the vane rotor 4 is rotated with respect to the housing HSG, and in this state, the rotational force is transmitted between the two, thereby rotating the crankshaft. The rotation phase of the camshaft 3a is changed. As shown in FIG. 3, the hydraulic supply / discharge mechanism 2 has a pump P that is a hydraulic supply source, a hydraulic circuit, and a flow path switching valve 24 that is a hydraulic control actuator.

  The hydraulic circuit has two passages, that is, a retard passage 20 that supplies and discharges hydraulic oil to and from each retard chamber R1 to R3, and an advance angle that supplies and discharges hydraulic oil to each advance chamber A1 to A3. A passage 21 is provided. A supply passage 22 and a drain passage 23 are connected to both passages 20 and 21 via a passage switching valve 24. The supply passage 22 is provided with a pump P that pumps the oil in the oil pan 25 to the flow path switching valve 24. The pump P is installed on the crankshaft of the engine, and for example, a unidirectional variable displacement vane pump can be used. The downstream end of the drain passage 23 communicates with the oil pan 25.

  A part of the advance passage 21 is formed in the camshaft 3a. That is, the advance passage 21 from the flow path switching valve 24 is connected to the axial oil passage 211 formed in the X-axis direction inside the camshaft 3a (end 30) via the radial oil passage 210. ing. The axial oil passage 211 is connected to the second port 213 through the radial oil passage 212. The second port 213 is an annular groove that surrounds the outer periphery of the end of the camshaft 3a on the X axis positive direction side. Similarly, a part of the retard passage 20 is formed in the camshaft 3a. The retarded passage 20 from the flow path switching valve 24 is connected to the first port 215 via the axial oil passage and the radial oil passage 214.

  The first port 215 and each retarded passage 408 in the rotor 40 have substantially the same position in the X-axis direction, and each retarded passage 408 communicates with the first port 215 on the inner diameter side of the rotor 40 and On the radial side, the retard chambers R1 to R3 communicate with each other. Similarly, the second port 213 and each advance passage 409 in the rotor 40 have substantially the same position in the X-axis direction, and each advance passage 409 communicates with the second port 213 on the inner diameter side of the rotor 40. The outer diameter side communicates with the advance chambers A1 to A3, respectively.

  The flow path switching valve 24 is a direct-acting solenoid valve (a directional control valve at 4 ports and 3 positions), and controls the hydraulic pressure supplied to and discharged from the advance chambers A1 to A3 or the retard chambers R1 to R3. The flow path switching valve 24 has a valve body fixed to the cylinder head, a solenoid SOL fixed to the valve body, and a spool valve body slidably provided inside the valve body. The valve body has a supply port 240 communicating with the supply passage 22, a first port 241 communicating with the retard passage 20, a second port 242 communicating with the advance passage 21, and a drain port 243 communicating with the drain passage 23. 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 241 and the second port 242 are opened and closed.

  When the solenoid SOL is not energized, the spool valve body communicates the supply port 240 (supply passage 22) and the second port 242 (advance passage 21) with the spring force of the return spring RS, and the first port 241. It is biased to a position where the (retard passage 20) and the drain port 243 (drain passage 23) communicate with each other. On the other hand, in the state where the solenoid SOL is energized, the spool valve body is resisted against the spring force of the return spring RS by the control current from the controller CU, and the supply port 240 (supply passage 22) and the first port 241 (slow). The angular passage 20) is communicated, and the second port 242 (advanced passage 21) and the drain port 243 (drain passage 23) are communicated with each other, or are controlled to move 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 conducts the switching control of the flow path by applying a pulse control current to the solenoid SOL of the flow path switching valve 24 according to the detected engine operating state, or by shutting off the power supply, thereby advancing the angle. Hydraulic fluid is selectively supplied to and discharged from the chambers A1 to A3 or the retarded chambers R1 to R3.

(Exhaust side device configuration)
Next, the structure of the apparatus 1b applied to the exhaust side of the engine will be described with reference to FIGS. The same components as those in the intake-side device 1a are denoted by the same reference numerals, description thereof is omitted, and only portions different from the device 1a are described. FIG. 15 is a partial cross section passing through the camshaft rotation axis O of the apparatus 1b as in FIG. 3, and shows a G-O-G cross section (dashed line) in FIG. 16 and 17 are front views of the apparatus 1b with the front plate 8 and the like removed as seen from the X-axis positive direction side, as in FIGS.

  The apparatus 1b continuously changes the rotational phase of an exhaust camshaft 3b (hereinafter referred to as a camshaft 3b) with respect to the crankshaft using the hydraulic pressure supplied from the hydraulic supply / discharge mechanism 2, thereby providing a valve for the exhaust valve. Variable control of timing. The pulley 100 is rotationally driven by the crankshaft of the engine and rotates together with the housing body 10 in the clockwise direction in FIG. 16 (corresponding to the arrow direction in FIG. 1).

  As shown in FIG. 15, unlike the device 1a, the front plate 8 of the device 1b is not provided with the outer peripheral portion 80, and the diameter of the front plate 8 is smaller than the diameter (maximum diameter) of the pulley 100. It has been. The outer peripheral edge of the front plate 8 is close to the groove 89 via a distance shorter than the radial distance r as shown in FIG. Therefore, as shown in FIG. 1, when viewed from the X-axis direction, the outer periphery of the pulley 100 of the device 1 b protrudes further to the outer diameter direction side than the front plate 8. In other words, the diameter of the device 1b is smaller than the diameter of the device 1a (the outer peripheral portion 80 of the front plate 8 protrudes toward the outer diameter direction of the pulley 100).

  The housing main body 10 of the device 1b has a mirror image arrangement that is opposite to the front and back of the housing main body of the device 1a when viewed from the X-axis direction. 18A is a front view of the housing main body 10 of the apparatus 1b as viewed from the X axis positive direction side, FIG. 18B is a cross-sectional view taken along line EE of FIG. 18A, and FIG. It is the front view which looked at from the X-axis negative direction side. 7 and 8 show an intermediate state in the manufacturing process of the housing body 10.

  The housing main body 10 of the apparatus 1b is formed from the aluminum extrusion material (primary processed product P1) shown in FIG. 7 similarly to the apparatus 1a. The tertiary processed product P3 shown in FIG. 8 is obtained from the primary processed product P1 through the secondary processed product P2. Then, by cutting the tertiary processed product P3 and providing the sealing recess 101, the bolt hole 110, and the like, the housing body 10 having the final shape shown in FIG. 18 is obtained. In the apparatus 1a, the sealing recess 101 and the positioning recess 114 are formed from the side A in FIG. 8 in the tertiary processed product P3 (see FIG. 6), whereas in the apparatus 1b, the tertiary recess P101 in FIG. A sealing recess 101 and a positioning recess 114 are formed from the side (see FIG. 18).

  Similarly, the vane rotor 4 of the apparatus 1b has a mirror image arrangement that is opposite to the front and back of the vane rotor 4 of the apparatus 1a when viewed from the X-axis direction. FIG. 19A is a front view of the vane rotor 4 of the apparatus 1b as viewed from the X axis positive direction side, and FIG. 19B is a cross-sectional view taken along line FF in FIG. 10 and 11 show an intermediate state in the manufacturing process of the vane rotor 4.

  The vane rotor 4 of the apparatus 1b is formed from the aluminum extrusion material (primary processed product Q1) shown in FIG. 10 similarly to the apparatus 1a. By cutting the secondary processed product Q2 obtained from the primary processed product Q1 and providing the boss 401, the fitting hole 402, etc., the final processed tertiary processed product Q3 as shown in FIG. To do. In the apparatus 1a, the boss portion 401 is provided on the A side in FIG. 11 and the fitting hole 402 is formed from the A side (see FIG. 6) with respect to the secondary processed product Q2, whereas in the apparatus 1b, 11, a boss portion 401 is provided on the B side, and a fitting hole 402 is formed from the B side (see FIG. 18). Thereafter, the entire outer peripheral surface of the tertiary processed product Q3 is anodized to obtain a finished product.

  As described above, the housing main body 10 and the vane rotor 4 of the devices 1a and 1b use the same base materials P3 and Q2 formed before cutting, respectively, in a mirror image arrangement. Therefore, as shown in FIGS. 16 and 4, when viewed from the positive direction of the X-axis, the shape of the housing body 10 and the vane rotor 4 of the device 1b and the mutual positions are mirror images of the device 1a (mirrored). Sometimes in a matching relationship).

  The first, second, and third shoes 11, 12, and 13 are arranged in this order in the counterclockwise direction of FIG. Recesses 115, 125, and 135 are formed on the first to third shoes 11 to 13, respectively, in the clockwise direction when viewed from the X axis positive direction side. Further, on the counterclockwise direction side of the first to third shoes 11 to 13, flat portions 111, 121, and 131 are formed, respectively.

  The first, second, and third vanes 41, 42, and 43 are arranged in this order in the counterclockwise direction of FIG. Plane portions 415 to 435 are formed on the clockwise direction side of the first to third vanes 43 as viewed from the X axis positive direction side. On the counterclockwise direction side of the first to third vanes 41 to 43, concave portions 418 to 438 are formed, respectively. Further, stopper portions 419 and 429 are provided at the bases of the first and second vanes 41 and 42 on the counterclockwise direction side, respectively.

  With the vane rotor 4 installed in the housing HSG, the first vane 41 is between the first shoe 11 and the second shoe 12, the second vane 42 is between the second shoe 12 and the third shoe 13, and the third vane. Reference numerals 43 are arranged in the gaps between the third shoe 13 and the first shoe 11, respectively.

  The rotor body 400 has a substantially intermediate position in the X-axis direction of the vanes 41 to 43 (see FIG. 19B) and is located on the clockwise direction side of the vanes 41 to 43 when viewed from the positive X-axis direction. A retard oil passage 408 is provided at the base (see FIG. 16). Moreover, it is on the X-axis negative direction side of each vane 41-43 (see FIG. 19B) and at the root of each vane 41-43 on the counterclockwise direction side when viewed from the X-axis positive direction (FIG. 16). See), and an advance oil passage 409 is provided.

  A first advance chamber A1 is defined between the clockwise surface of the second shoe 12 and the counterclockwise surface of the first vane 41. In addition, a first retardation chamber R <b> 1 is defined between a surface on the clockwise direction side of the first vane 41 and a surface on the counterclockwise direction side of the first shoe 11. Similarly, the second advance chamber A2 is provided between the first shoe 11 and the third vane 43, and the second retard chamber R2, the third shoe 13 and the second shoe are provided between the third vane 43 and the third shoe 13. A third advance chamber A3 is formed between the vane 42 and a third retard chamber R3 is formed between the second vane 42 and the second shoe 12, respectively.

  The rotation of the vane rotor 4 in the clockwise direction relative to the housing HSG is such that the flat surface portion 111 of the first shoe 11 and the flat surface portion 415 of the first vane 41 are in contact with each other (at a position where the lock piston 51 is locked, as in the device 1a). It is regulated by touching (FIG. 16). That is, these flat portions 111 and 415 function as first stopper portions that restrict relative rotation of the vane rotor 4 in the clockwise direction (advance direction).

  On the other hand, the rotation of the vane rotor 4 in the counterclockwise direction with respect to the housing HSG causes the tip 126 of the second shoe 12 and the stopper 419 of the first vane 11 to move to a position where the lock piston 51 is locked (similar to the device 1a). Is regulated by contact (at a position on the opposite side in the circumferential direction) (FIG. 17). That is, the counterclockwise side surface of the stopper portion 419 and the clockwise side surface of the second shoe 12 (the end portion 126 thereof) restrict the relative rotation of the vane rotor 4 in the counterclockwise direction (retard direction). It functions as a part. Similar to the device 1a, the contact area S2 of the second stopper portion is smaller than the contact area S1 of the first stopper portion (S1> S2).

  The camshaft 3b is rotatably supported outside the upper end portion of the cylinder head of the engine. A drive cam (exhaust cam) is provided on the outer peripheral surface of the camshaft 3b at a position corresponding to the position of the exhaust valve. When the camshaft 3b rotates, the exhaust cam opens and closes the exhaust valve. The device 1b fixed to the camshaft 3b is configured to be locked by the engaging member (lock piston 51) at the most advanced angle position whose rotation is restricted by the first stopper portion.

  The device 1b is provided with a biasing member 6 that biases the vane rotor 4 in a direction to advance the vane rotor 4 with respect to the housing HSG. The urging member 6 has three spring units, that is, first to third spring units 61 to 63. These spring units 61 to 63 are provided in the advance chambers A1 to A3, respectively, and urge the vane rotor 4 (vane) in the clockwise direction against the housing body 10 (shoe).

  That is, the first spring unit 61 is between the second shoe 12 and the first vane 41 (first advance chamber A1), and the second spring unit 62 is between the first shoe 11 and the third vane 43 (first The third spring unit 63 is housed in the second advance chamber A2) and between the third shoe 13 and the second vane 42 (third advance chamber A3). As described above, the recesses 418 to 438 and the recesses 115 are provided on the counterclockwise direction side surfaces of the first to third vanes 41 to 43 and the clockwise direction side surfaces of the first to third shoes 11 to 13, respectively. To 135 are formed, and the first to third spring units 61 to 63 are arranged in the recesses 418 to 438 and 115 to 135, respectively.

  The first spring unit 61 includes one coil spring 610 and holding portions 611 and 612 that are support members (spring retainers) provided at both ends thereof. The holding part 611 has a plate-like part provided with a through-hole, and a hollow cylindrical part formed surrounding the through-hole and projecting from one side surface of the plate-like part. One end of a coil spring 610 is fitted to the outer periphery of the cylindrical portion.

  The plate-like portion of the holding portion 611 is formed in a rectangular shape that fits into the recess 125 of the second shoe 12 without backlash, and is fitted into the recess 125. The recess 125 restricts the movement of the holding portion 611 relative to the housing HSG (second shoe 12) in the housing radial direction. Further, the front plate 8 and the rear plate 9 are in contact with both ends of the plate-like portion in the X-axis direction, thereby restricting movement of the holding portion 611 in the recess 125 in the X-axis direction within a predetermined range.

  The first advance chamber A1 communicates with the pressure receiving chamber 55 (see FIG. 14) of the lock mechanism 5 through the through hole of the holding portion 611 and the communication hole 56 of the first vane 41. The first retardation chamber R1 communicates with the lock hole 521 of the lock mechanism 5 through the communication groove 57 of the first vane 41.

  The holding unit 612 is also provided in the same manner as the holding unit 611. In other words, the cylindrical portion of the holding portion 612 holds the other end of the coil spring 610, and the plate-like portion of the holding portion 612 is supported by the concave portion 418 of the first vane 41, so that the vane rotor 4 (first vane 41) is supported. Movement of the holding portion 612 (coil spring 610) in the radial direction and the axial direction is restricted. As described above, the axial and radial positions of both ends of the coil spring 610 are restricted.

  At the time of assembly, the first spring unit 61 is inserted into the first advance chamber A1 from the X-axis direction, the holding portion 631 is fitted into the concave portion 125, and the holding portion 612 is fitted into the concave portion 418. As a result, the coil spring 610 is housed in the first advance chamber A1 in a compressed state, and the coil spring 610 causes the first vane 41 to move clockwise with respect to the housing body 10 (second shoe 12). Always energize.

  The same applies to the other second and third spring units 62 and 63. The second spring unit 62 has a coil spring 620 and holding portions 621 and 622, and the third spring unit 63 has a coil spring 630 and holding portions 631 and 632. The urging forces of the coil springs 610 to 630 are substantially the same. The diameters of the coil springs 610 to 630 occupy about 70% of the maximum width in the housing radial direction of the first to third advance chambers A1 to A3, respectively.

  When the vane rotor 4 rotates counterclockwise with respect to the housing HSG, the coil springs 610 to 630 are compressed. Here, the coil spring 610 (the portion on the clockwise direction side thereof) is disposed on the outer peripheral side of the stopper portion 419 (of the first vane 41). Further, the height of the stopper portion 419 in the rotor radial direction is set such that the outer periphery of the stopper portion 419 is close to the outer periphery of the installed coil spring 610 and has a slight gap therebetween. .

  For this reason, when the coil spring 610 is compressed and deformed, the inner peripheral side of the coil spring 610 can be brought into contact with the outer peripheral surface of the stopper portion 419, whereby the coil spring 610 has a predetermined amount in the rotor inner diameter direction. The above deformation can be regulated. That is, the stopper part 419 exhibits the guide function of the coil spring 610. The stopper portion 429 (of the second vane 42) is also provided in the same manner as the stopper portion 419, and also serves as a guide for the coil spring 630 when the coil spring 630 is compressed when the vane rotor 4 is relatively rotated.

  As shown in FIG. 17, when the tip portion 126 of the second shoe 12 and the stopper portion 419 of the first vane 11 are in contact with each other, when the counterclockwise rotation is restricted, the first to third spring units In each of 61 to 63, the holding portions 611 and 612 facing each other on the vane side and the shoe side do not contact each other, and the windings do not adhere to each other in the coil springs 610 to 630. In other words, when the rotation of the counterclockwise direction is restricted by the second stopper portion, the circumferential clearances of the advance chambers A1 to A3 are when the windings of the coil springs 610 to 630 are completely in close contact with each other. Is set larger than the spring length.

  The configuration of the hydraulic supply / discharge mechanism 2 is the same as that of the device 1a. Although the flow path switching valve 24 is provided separately from the device 1a, the pump P and the oil pan 25 are shared by the devices 1a and 1b.

(Function of the device)
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.
First, the phase conversion action of the device 1a will be described. 4 shows the most retarded state when the engine is stopped (when the engine is started), and FIG. 5 shows the most advanced state when the engine is operating.

  When the engine is started, the lock mechanism 5 preliminarily restrains the vane rotor 4 at the initial position on the retard side optimum for starting (FIG. 4). For this reason, when start-up is started by turning on the ignition switch, good startability is obtained by smooth cranking.

  The control current from the controller CU is not output to the flow path switching valve 24 in a predetermined low rotation / low load range after the engine is started. The spool valve body remains in a position where the supply port 240 and the second port 242 communicate with each other and the first port 241 and the drain port 243 communicate with each other by the spring force of the return spring RS. Therefore, the hydraulic pressure discharged from the pump P flows into the valve body from the supply passage 22 via the supply port 240, and flows into the advance passage 21 from the second port 242. It passes through the corner oil passage 409 and is supplied to each advance chamber A1 to A3. The internal pressure in each of the advance chambers A1 to A3 increases as the discharge pressure of the pump P increases. On the other hand, the hydraulic oil in each retardation chamber R1 to R3 is discharged to the oil pan 25 through the retardation passage 20 and the drain passage 23, and the internal pressure of each retardation chamber R1 to R3 remains low.

  As the internal pressure of the advance chamber A1 rises, this hydraulic pressure is supplied from the communication groove 57 (see FIG. 14) to the lock hole 521, and the lock piston 51 (tip portion 511) reduces the oil pressure on the X axis positive direction side. receive. When the oil pressure becomes larger than the spring force of the coil spring 53, the lock piston 51 moves in the positive direction of the X axis. When the tip 511 is completely removed from the lock hole 521, the locked state is released. That is, free rotation of the vane rotor 4 is allowed, and the valve timing can be arbitrarily changed.

  Due to the hydraulic pressure supplied to each of the advance chambers A1 to A3, the vane rotor 4 rotates relative to the housing HSG in the rotation direction of the housing HSG (in the direction of the arrow in FIG. 4) from the position shown in FIG. The rotational phase (relative rotational angle) of the camshaft 3a is changed to the advance side. This increases the valve overlap, which is the period during which both the intake valve and the exhaust valve are opened. As a result, the opening / closing timing of the intake valve is advanced, and the combustion efficiency by using the inertial intake at the time of such low rotation and low load is improved, so that the engine rotation is stabilized and the fuel consumption is improved. As shown in FIG. 5, when the vane rotor 4 rotates relative to the position on the most advanced angle side where the volumes of the advance chambers A1 to A3 are maximized and the volumes of the retard chambers R1 to R4 are minimized, the valve overlap occurs. Is the maximum.

  On the other hand, 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 24. The spool valve body moves to a position where the supply port 240 and the first port 241 communicate with each other and the second port 242 and the drain port 243 communicate with each other against the spring force of the return spring RS. Therefore, the hydraulic pressure discharged from the pump P flows into the retarded passage 20 from the first port 241 of the flow path switching valve 24 and passes through each retarded oil passage 408 of the vane rotor 4 to each retarded chamber R1 to R1. Since the pressure is supplied to R3, the internal pressures of the retard chambers R1 to R3 are increased. On the other hand, the hydraulic oil in each advance chamber A1 to A3 is discharged to the oil pan 25 through the advance passage 21 and the drain passage 23, and the internal pressure in each advance chamber A1 to A3 is reduced.

  At this time, in the lock mechanism 5, the oil pressure in the lock hole 521 decreases, but this time, as the oil pressure in the retard chamber R <b> 1 increases, this oil pressure is supplied from the communication hole 56 (see FIG. 14) to the pressure receiving chamber 55. It acts on the pressure receiving surface of the flange portion 513 of the lock piston 51 as an oil pressure. As a result, the release state in which the lock piston 51 has come out of the lock hole 521 against the spring force of the coil spring 53 is maintained.

  Therefore, when the internal pressures of the retard chambers R1 to R3 become larger than the internal pressures of the advance chambers A1 to A3, the vane rotor 4 rotates counterclockwise on the side opposite to the rotation direction of the housing HSG (the arrow direction in FIG. 4). Rotate relative to the housing HSG in the direction to change the rotation phase (relative rotation angle) of the camshaft 3a with respect to the crankshaft to the retard side. Thereby, the rotational phase of the camshaft 3a with respect to the crankshaft is changed to the retard side, and the valve overlap is reduced. As a result, the opening / closing timing of the intake valve is controlled to the retard side, and the engine output at the time of such high rotation and high load can be improved. As shown in FIG. 4, when the vane rotor 4 rotates relative to the position of the most retarded angle side where the volumes of the retarded angle chambers R1 to R4 are maximized and the volumes of the advanced angle chambers A1 to A3 are minimized, the valve overlap occurs. Is minimized.

  Furthermore, for example, when the engine shifts to the middle rotation load region, the controller CU controls the flow path switching valve 24 to hold the spool valve body at the intermediate movement position. As a result, the internal pressures of the retard chambers R1 to R4 and the advance chambers A1 to A3 are kept constant, and the vane rotor 4 is controlled to the intermediate rotational 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, during rotation of the camshaft 3a, so-called alternating torque is generated in the camshaft 3a due to the rotational reaction force transmitted from the valve spring that biases the intake valve in the closing direction to the cam of the camshaft 3a. That is, due to the cam shape, a negative torque (counterclockwise) that prevents the camshaft 3a from rotating (clockwise) and a positive torque that assists the rotation of the camshaft 3a (clockwise) are: It acts alternately on the camshaft 3a. 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 period of the camshaft 3a are integrated over time, the camshaft 3a becomes negative, and the negative torque acts on the camshaft 3a 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 24 is interrupted. Accordingly, the supply of the hydraulic pressure to the advance chambers A1 to A3 and the retard chambers R1 to R3 is stopped. For this reason, immediately after the engine is stopped, the vane rotor 4 rotates in the rotation direction of the housing HSG with respect to the housing HSG (the direction of the arrow in FIG. 4) due to the friction generated in the camshaft 3a (alternating torque offset to the negative torque side) It tries to rotate in the opposite direction, that is, the retard side.

  Therefore, after the engine is stopped, the vane rotor 4 is moved to a predetermined initial position suitable for engine (re) starting in advance, that is, a position on the most retarded angle side shown in FIG. 4 by the friction (alternating torque) of the camshaft 3a. . In other words, the valve timing is a phase suitable for engine (re) starting.

  Further, when the vane rotor 4 rotates relative to the housing HSG relative to the most retarded angle side, the position of the lock piston 51 of the lock mechanism 5 and the position of the lock hole 521 overlap each other. Due to the spring force of the coil spring 53, the tip 511 is fitted into and engaged with the lock hole 521, and the lock piston 51 restricts free rotation of the vane rotor 4.

  As described above, in the apparatus 1a, when the engine is stopped, the vane rotor 4 is rotated to the initial position on the retard side with respect to the housing HSG by the alternating torque. Therefore, the apparatus 1a can be controlled from the initial position even when the engine is restarted, and the apparatus 1a can be stably operated.

  Next, the phase conversion action of the device 1b will be described. The operation of the device 1b is the same as that of the device 1a except that the retard side and the advance side are switched. 16 shows the most advanced angle state when the engine is stopped (when the engine is started), and FIG. 17 shows the most retarded angle state when the engine is operating.

  When the engine is started, the lock mechanism 5 preliminarily restrains the vane rotor 4 at the initial position on the advance side optimum for starting (FIG. 16). For this reason, when start-up is started by turning on the ignition switch, good startability is obtained by smooth cranking.

  In a predetermined low rotation and low load region after engine startup, the rotation phase of the camshaft 3a is converted to the retard side by the hydraulic pressure supplied to each retard chamber R1 to R3, and the valve overlap becomes large. As shown in FIG. 17, when the vane rotor 4 rotates relative to the position at the most retarded angle side where the volumes of the retarded angle chambers R1 to R4 are maximized and the volumes of the advanced angle chambers A1 to A3 are minimized, the valve overlap occurs. Is the maximum.

  On the other hand, in the high rotation and high load region of the engine, hydraulic pressure is supplied to the advance chambers A1 to A3, and the sum of the force of the hydraulic pressure of each advance chamber A1 to A3 and the urging force of the spring units 61 to 63 is delayed. If it becomes larger than the force by the hydraulic pressure of the corner chambers R1 to R4, the vane rotor 4 rotates relative to the advance side. Thereby, the rotation phase (relative rotation angle) of the camshaft 3b is changed to the advance side, and the valve overlap is reduced. In other words, the urging member 6 (first to third spring units 61 to 63) also has a function of assisting phase conversion to the advance side. As shown in FIG. 16, when the vane rotor 4 rotates relative to the position on the most advanced angle side where the volumes of the advance chambers A1 to A3 are maximized and the volumes of the retard chambers R1 to R4 are minimized, the valve overlap occurs. Is minimized.

  During engine operation, during the rotation of the camshaft 3b, a negative (counterclockwise) alternating torque is applied to the camshaft 3b to prevent rotation (clockwise). When the engine is stopped and the energization to the flow path switching valve 24 is interrupted, the vane rotor 4 tries to rotate in the counterclockwise direction, that is, the retard side with respect to the housing HSG by the alternating torque.

  On the other hand, the vane rotor 4 is urged clockwise with respect to the housing HSG, that is, the advance side by the urging member 6 (first to third spring units 61 to 63). Therefore, after the engine is stopped, the vane rotor 4 is not affected by the alternating torque, and in accordance with the urging force of the urging member 6, a predetermined initial position suitable for engine (re) starting in advance, that is, the maximum position shown in FIG. Move to the advanced position. In other words, the valve timing is a phase suitable for engine (re) starting.

  When the vane rotor 4 rotates relative to the housing HSG relative to the most advanced angle side, the positions of the lock piston 51 and the lock hole 521 overlap. Therefore, when the engine is stopped, the lock piston 51 engages with the lock hole 521 and the vane rotor 4 rotation is restricted.

  As described above, in the apparatus 1b, when the engine is stopped, the vane rotor 4 is rotated and moved to the initial position on the most advanced angle side with respect to the housing HSG by the urging force of the urging member 6 without being affected by the alternating torque. Therefore, the apparatus can be controlled from the initial position even when the engine is restarted, and the apparatus 1b can be stably operated.

(Operation of locking mechanism)
As described above, the relative rotation between the housing HSG and the vane rotor 4 can be restricted by operating the lock mechanism 5 at the initial positions of the devices 1a and 1b (FIGS. 4 and 16). That is, even in a state where no hydraulic pressure is generated at the time of engine (re) starting, the housing HSG and the vane rotor 4 can be held, and the devices 1a and 1b can be controlled from the initial position regardless of whether or not hydraulic pressure is generated. is there. Therefore, at the time of engine restart or idling while preventing fluttering (occurrence of abnormal noise due to a collision) or knocking between the vane rotor 4 and the housing HSG caused by the alternating torque acting on the camshafts 3a and 3b when the engine is restarted. Even at times, the engine or devices 1a and 1b can be operated stably.

  The lock means (lock mechanism 5) is a lock piston 51 housed in the first vane 41, and locks the relative rotation of the housing HSG and the vane rotor 4 by operating in the axial direction. Release the stop. That is, since the lock piston 51 automatically engages with the lock hole 521 when the vane rotor 4 is rotated to a predetermined initial position by the alternating torque or the urging force of the urging member 6, the actuator for the lock operation is provided. Not particularly necessary. Therefore, the mechanism is simpler than the case where a clutch mechanism or a lever mechanism is used as the locking means, and the reliability of the locking operation can be ensured while reducing the cost.

(Operation of positioning means)
In order to explain the operation of the positioning means such as the positioning pin 905, the outline of the assembly procedure of the devices 1a and 1b will be described first.

  First, the rear plate 9 is inserted and installed in the sealing recess 101 of the housing body 10. A state in which the X-axis positive direction surface of the rear plate 9 (with the sleeve 52 fixed to the recess 900) is directed vertically upward, the seal ring S1 is installed in the groove 906, and the seal ring S2 is installed in each of the grooves 907 to 909 Then, the housing body 10 is assembled to the rear plate 9 from the X axis positive direction side (vertically upward) so that the rear plate 9 fits into the sealing recess 101.

  At that time, the rotational position of the housing body 10 with respect to the rear plate 9 is adjusted so that the positioning recess 114 of the housing body 10 and the positioning pin 905 of the rear plate 9 face each other. Then, the positioning pin 905 is fitted into the positioning recess 114 and engaged. Thereby, the rear plate 9 is positioned in the (circumferential direction) relative to the housing body 10. At this time, the female screw portions 901 to 903 (bolt holes) of the rear plate 9 are substantially coaxial with the bolt holes 110 to 130 of the housing body 10, respectively.

  Next, the vane rotor 4 is inserted into the housing body 10. The lock piston 51 is inserted into the sliding hole 501 (the sealing member 502 press-fitted into the vane rotor 4), the coil spring 53 is inserted into the lock piston 51, and the spring retainer 54 is inserted into the sliding hole 501. Due to the positioning by the positioning pins 905, the sleeve 52 (fixed to the rear plate 9) is fixed to the sliding hole 501 (locking) while the vane 41 of the vane rotor 4 is in contact with the shoe 11 of the housing body 10. It is substantially coaxial with the piston 51).

  Then, the front plate 8 is brought into contact with the housing body 10 from the X axis positive direction side (vertically upward), and the respective members are fastened by bolts b1 to b3 to be integrated. The front plate 8 is assembled with the seal ring S3 inserted in the groove 89.

  As described above, the positioning pin 905 (pin hole 904) and the positioning recess 114 are arranged so that the rotational position of the rear plate 9 relative to the housing body 10, that is, the lock piston 51 and the lock hole 521, when assembling the constituent members of the devices 1a and 1b. Positioning means for adjusting and determining the relative position in the circumferential direction is configured. The radial relative positions of the lock piston 51 and the lock hole 521 substantially coincide with each other when the rear plate 9 is inserted (fitted) into the sealing recess 101 of the housing body 10. Thus, since the lock piston 51 and the lock hole 521 are accurately positioned using the positioning means, a smooth engagement action of the lock piston 51 is obtained.

  Here, since the positioning pin 905 is provided at a position close to the recess 900 (the lock hole 521), the lock piston 51 and the lock hole 521 can be positioned more accurately. Further, since the pin hole 904 is disposed closer to the oil chamber (first retardation chamber R1) than the grooves 906 and 907, the sealing performance of the seal rings S1 and S2 is not affected.

  The vane rotor 4 is fixed to one end side (end 30) of the camshaft 3a through a support hole 92 provided on the inner periphery of the rear plate 9 and through which the camshaft 3a is inserted. Therefore, the housing HSG is inclined within a slight angle range with respect to the rotation axis (X axis) of the vane rotor 4 by the force acting from the belt B hung on the pulley 100 (housing HSG), and the support hole 92 is provided. The bearing 91 (of the rear plate 9) can be used as a fulcrum to swing.

  On the other hand, in the first embodiment, since the lock hole 521 is provided in the rear plate 9, for example, from the swing fulcrum (bearing portion 91) to the lock hole 521, compared to the case where the lock hole is provided in the front plate 8, for example. The distance (moment arm) is short. Therefore, the rocking displacement (in the direction perpendicular to the X axis) of the lock hole 521 is small, and the possibility of the displacement of the lock piston 51 relative to the lock hole 521 is small. Further, since the boss portion 401 of the vane rotor 4 is inserted into the support hole 92, the inclination or swinging displacement of the vane rotor 4 with respect to the housing HSG is suppressed within a predetermined range.

(Operation of biasing member)
The biasing member 6 of the device 1b is a coil spring, and houses one coil spring 610 to 630 in each advance chamber A1 to A3. By using the coil spring in this way, it is easy to adjust the urging force and to be easily installed in the oil chambers A1 to A3, for example, compared to the case where a leaf spring or the like is used. Moreover, by storing one by one in each of the oil chambers A1 to A3, for example, the device 1b can be downsized in the axial direction as compared with a case where two coil springs are stacked and stored in the X-axis direction.

  Further, when two coil springs are installed in each of the oil chambers A1 to A3, it is difficult to assemble them unless they are installed in a support member (holding portion) and set as one spring unit. On the other hand, when one is housed in each of the oil chambers A1 to A3 as in the first embodiment, not only the assembly is easy, but also the coil springs 610 to 630 are supported by the support members (holding portions 611, 612, etc.). It is also possible to install them directly in the oil chambers A1 to A3 (recesses 418, 125, etc.) without being integrated with each other. In this case, the number of parts can be reduced by omitting the support member.

  Concave portions 418 to 438 formed on the counterclockwise direction side surfaces of the first to third vanes 41 to 43 and concave portions 115 to 135 formed on the clockwise direction side surfaces of the first to third shoes 11 to 13 opposed thereto. In addition, first to third spring units 61 to 63 (coil springs 610 to 630) are arranged. Therefore, even when the device 1b is in operation, the movement (displacement) of the first to third spring units 61 to 63 (coil springs 610 to 630) is restricted by the recesses 418 to 438 and 115 to 135. There is no need to provide a special support member (for example, the holding portions 611 and 612 may be omitted), and normal operation of the urging member 6 and the device 1b is ensured. However, when the holding portions 611, 612 and the like are provided as in the first embodiment, the above movement (displacement) can be more reliably prevented.

(Operation of the stopper)
As described above, when the engine is stopped, the vane rotor 4 is returned to the predetermined initial position with respect to the housing HSG in a state that is not controlled by the flow path control valve 24. In the apparatus 1a, the vane rotor 4 is rotationally moved to the retard side with respect to the housing HSG by alternating torque, and the first stopper provided on the housing member (housing body 10) and the vane rotor 4 at the initial position on the most retarded side. The relative rotation is restricted by the portion. In the apparatus 1b, the urging force of the urging member 6 rotates the vane rotor 4 to the advance side with respect to the housing HSG against the alternating torque, and the housing body 10 and the vane rotor 4 at the most advanced angle side initial position. Relative rotation is restricted by the first stopper portion provided at the top. As described above, the first stopper portion that functions when locked by the lock mechanism 5 at the initial position has many contact times.

  Further, in the state where the normal control is performed by the flow path control valve 24, the movement of the vane rotor 4 with respect to the housing HSG can be controlled, and therefore the first stopper portion hardly comes into contact with the housing HSG. However, when the engine is stopped, the movement of the vane rotor 4 with respect to the housing HSG cannot be controlled in the state where the control by the flow path control valve 24 is not performed and the hydraulic pressure is not applied. May end up. Therefore, the first stopper portion that functions when locking at the initial position is deformed due to the large number of times of contact and the strength of the contact force as described above, whereby the rotation restricting position (initial position) is changed. May change.

  In the device 1a and the device 1b according to the first embodiment, the contact area S1 of the first stopper portion is larger than the contact area S2 of the second stopper portion (S1> S2). Therefore, when the vane rotor 4 is rotated in one direction (on the initial position side) with respect to the housing HSG, the surface pressure (contact surface pressure) generated on the contact surface when the first stopper portion contacts is the vane rotor. When 4 is rotated in the other direction with respect to the housing HSG, it is smaller than the contact surface pressure generated when the second stopper portion contacts.

  Therefore, even when the engine is not controlled, such as when the engine is stopped, the first stopper portion is strongly (at the time of each abutment even if the abutment frequency is large) at the initial position locked by the lock mechanism 5. Since contact can be suppressed, deformation of the first stopper portion and change in the rotation restricting position can be prevented. In addition, since the 1st stopper part is comprised by the circumferential direction side surface (plane part 416,111) of the vane 41 and the shoe 11, it is advantageous to enlarge contact | abutting area S1.

  In the first embodiment, the first stopper portion is provided for the first vane 41 having the lock mechanism 5, and the first stopper portion is configured by the circumferential side surface of the first vane 41. Since the first vane 41 (the root portion thereof) is thick in the circumferential direction, the rigidity is sufficient, and it is advantageous that sufficient strength for restricting relative rotation can be obtained.

  In general, in an exhaust side device, when an urging member is disposed in an oil chamber, it is difficult to ensure a sufficient contact area of a stopper provided in the oil chamber. On the other hand, the abutting force of the stopper portion (on the side of the rotation direction opposite to the stopper portion) that is urged by the urging member is increased by the urging force of the urging member. In particular, when the housing member or the vane rotor is formed of a soft material such as an aluminum alloy, the problem appears remarkably. On the other hand, in the apparatus 1b of the first embodiment, the contact area S1 of the first stopper portion (contacted on the side urged by the urging member 6) provided in the retardation chamber R1 is set to (the urging member). 6), the contact area S2 of the second stopper portion provided in the advance chamber A1 (S1> S2). Thereby, the said problem can be solved, avoiding interference with a 2nd stopper part and the urging | biasing member 6. FIG.

  Even if the contact area S2 of the second stopper portion is small, only the hydraulic pressure of the retard chamber R acts on the second stopper portion that contacts on the opposite side to the direction urged by the urging member 6. (Furthermore, since the urging force of the urging member 6 acts in the direction opposite to the abutting direction), the abutting force is small and the abutting surface pressure is small. In addition, the second stopper portion regulates the relative rotation angle of the vane rotor 4 with respect to the housing HSG when the control hydraulic pressure is overshooted or the like in a state controlled by the flow path control valve 24 (in both the device 1a and the device 1b). And the number of contact is small. For this reason, there is no possibility that the restriction position changes due to the deformation of the second stopper portion.

  In addition, the vanes 41 to 43 are formed in a substantially trapezoidal shape whose circumferential width increases toward the outer radial direction, and the root side (radially inner side) is more circumferential than the distal end side (radial outer side). Low rigidity. In the first embodiment, the second stopper portion (stopper portion 419) is formed on the base side of the vane 41 by a portion protruding from the rotor 40 toward the outer peripheral side. Therefore, unlike the case where the second stopper portion is provided on the tip end side of the vane 41, the vane 41 is bent from the root (in the circumferential direction with respect to the rotor 40) when the rotation is restricted (when the second stopper portion is in contact). The force (moment arm) is small, and an excessive force hardly acts on the root portion of the vane 41. For this reason, when the 2nd stopper part is provided continuously with the vane 41 (integral with the vane 41), durability of the vane 41 can be improved and it is advantageous.

  Further, in the device 1b, the displacement amount (compression amount) of the biasing member 6 (coil springs 610 to 630) is restricted to a predetermined amount or less by the stopper function of the second stopper portion. Thereby, the plastic deformation of the urging member 6 (coil springs 610 to 630) is prevented, and the urging force can be prevented from changing irreversibly.

  In addition, even if an error in manufacturing and assembly, wear of the second stopper portion, or the like occurs, the second stopper is brought into contact with the stopper portion 429 of the second vane 42 and the tip of the third shoe 13 as a backup (backup). Since the same stopper function as the part is secured, the control accuracy can be improved. This is the same in the apparatus 1a, but in the apparatus 1b in particular, the above-described effect of preventing plastic deformation of the biasing member 6 can be obtained more reliably.

  The coil springs 610 and 630 are arranged on the outer peripheral side of the stopper portions 419 and 429 (of the first and second vanes 41 and 42), and the second stopper portion (the stopper portions 419 and 429 constituting the second spring portion 419 and 429) is connected to the biasing member 6 ( Also serves as a guide for the coil springs 610 and 630). For this reason, when the coil springs 610, 630 are compressed and deformed when the vane rotor 4 is relatively rotated, deformation of the coil springs 610, 630 in the inner diameter direction of the rotor is restricted. Therefore, appropriate elastic deformation is maintained while preventing plastic deformation of the coil springs 610 and 630. Therefore, normal operation of the biasing member 6 and the device 1b is ensured.

(Operation by mirror image arrangement)
In general, if devices are provided on both the intake and exhaust camshafts, if the materials of the constituent members (housing members and vane rotor) can be shared between the devices and the materials can be made compatible, This is advantageous because the manufacturing process can be simplified and the cost can be reduced. In the first embodiment, the device 1a and the device 1b are different from each other except that the direction in which the vane rotor 4 converts the rotational phase of the camshafts 3a and 3b is different by energization and non-energization of the flow path switching valve 24. The basic structure of the structural members is similar. Therefore, the material (P3) of the housing body 10 and the material (Q2) of the vane rotor 4 are shared between the devices 1a and 1b. That is, the shapes of the housing main body 10 and the vane rotor 4 of the apparatus 1a and the apparatus 1b are obtained by cutting each from the opposite surface (A surface, B surface) of the same extruded material (P3, Q2). Yes.

  In general, the housing member and the vane rotor of the apparatus have stoppers for restricting the relative rotation angle on the advance side and the retard side. For example, the housing member and the vane rotor are brought into contact with each other to form the stoppers. However, in the exhaust side device, when the urging member for returning the vane rotor to the initial position is provided in the retarded angle chamber, even if an attempt is made to increase the contact area between the housing member and the vane rotor that are opposed to each other through the retarded chamber. There is a limit, and the contact area between the two members facing each other through the advance chamber becomes smaller. Thus, in the exhaust side device, it is difficult to make the contact area (contact surface pressure) of the stopper that restricts relative rotation the same in both directions of relative rotation due to various design conditions. The shape of the vane rotor will be different in both directions.

  On the other hand, the operation direction (direction in which the rotation phase of the vane rotor with respect to the housing member is converted) in the intake side device is opposite to that in the exhaust side device, and the relative rotation direction when returning the vane rotor to the initial position with respect to the housing member The reverse is also true. That is, the direction of relative rotational movement in the state where the operating hydraulic pressure is not applied differs between the intake side and the exhaust side.

  Therefore, if the constituent members of the exhaust side device are used as they are for the intake side device, there will be a problem with the durability of the stopper in particular. For example, when the vane rotor 4 and the housing main body 10 of the device 1b of the first embodiment are transferred to the intake side as they are without considering the difference in shape in the circumferential direction, that is, from the device 1b shown in FIG. When the device on which the coil springs 610 to 630) are removed is used as it is as a device on the intake side, the second stopper portion comes into contact at the initial position and locks at this position. In this case, in the apparatus on the intake side, the second stopper portion having a small contact area may be deformed and the rotation restricting position may be changed.

  On the other hand, in the first embodiment, the vane rotor 4 and the housing body 10 of the exhaust side device 1b are turned over and the stopper portion is mirror-arranged and used for the intake side device 1a. Thereby, in both the device 1a and the device 1b, the first stopper portion having the larger contact area can be contacted at the initial position (FIGS. 4 and 16). In other words, the materials (materials) such as the vane rotor 4 are shared by the devices 1a and 1b so as to be compatible with each other, and the deformation of the stopper portion and the change of the rotation restricting position are changed in both devices 1a and 1b by the mirror image arrangement of the materials. It is possible to prevent.

(Operation by aluminum extrusion)
Since both the housing body 10 and the vane rotor 4 are formed of an aluminum metal material, the apparatus 1 can be reduced in weight.
Further, since the housing body 10 is formed by extrusion molding, the hydraulic oil is prevented from oozing from the inside of the housing HSG to the pulley 100, and deterioration of the rubber belt B can be prevented.
For example, when it is formed by die casting (high pressure casting), a draft (taper) is formed. If a draft is formed on the outer periphery of the housing body 10, for example, when the pulley is formed integrally with the outer periphery of the housing body 10, it is difficult to ensure the accuracy of the teeth of the pulley. On the other hand, since the draft cannot be formed by extrusion molding, the pulley 100 and the like can be processed with high accuracy.

  In the housing body 10, the entire outer peripheral surface and inner peripheral surface of the extruded aluminum material (primary processed product P1) is subjected to anodizing treatment to increase the hardness of the surface. In this way, the outer peripheral surface on which the belt B is wound and the driving force acts and the inner peripheral surface on which the vanes 41 to 43 slide are increased in hardness. Further, since the surface treatment is performed at the stage of the primary processed product P1 before cutting into a plurality of secondary processed products P2, the processing cost can be reduced. It should be noted that no anodic oxide film is formed on both axial end surfaces of the primary processed product P1 and both axial end surfaces of the cut secondary processed product P2, but these end surfaces are in contact with the front plate 8 and the rear plate 9. Since it does not slide with respect to other members, there is no particular problem even if the surface treatment is not performed.

  In the vane rotor 4, the entire outer peripheral surface of the final tertiary processed product Q3 is anodized. That is, not only the outer peripheral surface 411 of the vanes 41 to 43 that slide with respect to the inner peripheral surface of the housing body 10 but also the axial end surfaces of the vane rotor 4 that slides with respect to the front plate 8 and the rear plate 9 are processed. Thus, the surface is hardened. In order to secure the accuracy of the teeth of the pulley 100, the aluminum metal used as the material of the housing body 10 is slightly soft, but the vane rotor 4 does not need such a material. An aluminum-based metal having a slightly higher hardness than 10 may be used.

  As for the housing body 10, a long continuous body (primary processed product P1, secondary processed product P2) is obtained by extrusion molding, and a plurality of base materials (tertiary processed product P3 having the same shape) are obtained by cutting the continuous body. ) At a time. The same applies to the vane rotor 4. In this way, a large number of base materials (P3, Q2) can be obtained with a small number of steps, and these can be efficiently shared by the devices 1a, 1b. Therefore, the manufacturing process can be further simplified and the cost can be further reduced.

(Operation of pulley)
In the first embodiment, the apparatus 1 is reduced in size in the radial direction by integrally forming the pulley 100 on the outer periphery of the housing member (housing main body 10). Further, since the pulley 100 is provided in the entire axial range of the outer periphery of the housing main body 10, even when the lower limit of the width of the belt B is determined, the width of the teeth meshing with the belt B can be secured. In other words, even when the rear plate 9 is inserted and fixed in the sealing recess 101 of the housing body 10 so that the axial width of the housing HSG is as small as the width of the belt B (thin in the axial direction), the belt B A sufficient tooth width to engage and transmit power can be secured.

  In the device 1a, the diameter of the front plate 8 is slightly larger than that of the pulley 100. That is, since the outer peripheral portion 80 is provided so as to protrude from the pulley 100 in the outer diameter direction, even if the belt B stretched over the pulley 100 tries to move in the positive direction of the X axis, the outer peripheral portion 80 contacts and moves. Can not. As described above, the outer peripheral portion 80 exhibits a guide function as a belt guide portion, and prevents the entire belt B from shifting to the X axis positive direction side. Note that the cylinder block prevents the belt B from shifting to the negative side of the X axis and falling off the pulley 100 on the same side.

  On the other hand, in the device 1b, the diameter of the front plate 8 is slightly smaller than that of the pulley 100. That is, the diameter of the exhaust side device 1b (see FIG. 1) installed on both outer sides in the width direction of the cylinder block is smaller than the diameter of the intake side device 1a provided with the outer peripheral portion 80. For this reason, it is possible to suppress the dimension in the width direction of the engine provided with the devices 1a and 1b as a whole. Therefore, the degree of freedom in layout in the engine room can be improved. Here, since the displacement of the belt B on the X axis positive direction side is prevented by the intake side device 1a (outer peripheral portion 80) installed on the inner side in the width direction of the cylinder block as described above, the exhaust side device There is no problem even if the belt guide portion is not provided in 1b.

(Operation of sealing recess)
In the apparatus 1, both axial ends of the housing body 10 (which is reduced in size in the radial direction by integrally forming the pulley 100 on the outer periphery) are sealed by the front plate 8 and the rear plate 9, respectively. However, if both the front plate 8 and the rear plate 9 are fixed to the both axial end surfaces of the housing body 10 as they are, the axial dimension of the device 1 cannot be sufficiently suppressed. In the first embodiment, the apparatus 1 can be reduced in size in the axial direction by inserting and fixing the rear plate 9 in the sealing recess 101 of the housing body 10. Here, since the rear plate 9 is inserted and fixed in the sealing recess 101 over the entire range in the X-axis direction, the effect of downsizing in the axial direction is great.

  The rear plate 9 is inserted with a lock piston 51 protruding from the vane rotor 4 in the X-axis direction, and it is necessary to form a lock hole 521 (a recess 900 for fixing the sleeve 52) to engage with the lock piston 51 in the X-axis direction. is there. Therefore, it is necessary to make the rear plate 9 thicker than the front plate 8. If the relatively thick rear plate 9 is fixed in contact with the one axial end face of the housing body 10 as it is, the axial dimension of the entire device 1 becomes particularly long. In the first embodiment, the sealing recess 101 is formed at one end of the housing body 10 in the axial direction, and the rear plate 9 (not the front plate 8) is inserted and fixed in the sealing recess 101. Can be effectively downsized. Therefore, the degree of freedom of mounting the device 1 in the engine room is greatly improved.

  Further, the front plate 8, the rear plate 9, and the housing body 10 are fastened by a plurality of bolts b1 to b3. Here, the male screws of the bolts b <b> 1 to b <b> 3 need to be screwed into the female screw holes formed in either the rear plate 9 or the front plate 8. Since the female screw hole needs to have a certain length, the plate on which the female screw hole is formed needs to be thicker. For this reason, if a relatively thick plate is fixed in contact with the axial end surface of the housing body 10 as it is, the axial dimension of the entire device 1 becomes particularly long. In the first embodiment, since both the lock hole 521 and the female thread portion are formed in the rear plate 9, it is possible to greatly contribute to reducing the axial dimension of the device 1.

  That is, 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. For this reason, the front plate 8 is fixed in a state where it is in direct contact with the axial end surface of the housing body 10. However, the axial length of the device 1 is hardly increased. On the other hand, in order to form the lock hole 521, an internal thread portion is provided on the rear plate 9 that must be thick, and the thick rear plate 9 is inserted and fixed in the sealing recess 101. In other words, the lock hole 521 is provided in the rear plate 9 that must be thick in order to form the female screw portion, and the thick rear plate 9 is inserted and fixed in the sealing recess 101. For this reason, the axial direction dimension of the apparatus 1 can be effectively reduced as described above.

  It is possible to form a sealing recess on the front plate side of the housing body 10 and insert the front plate 8 into the sealing recess. However, since the axial movement range of the lock piston 51 needs to be secured to some extent, in the first embodiment, the front plate 8 is fixed in a state of being in contact with the axial end surface of the housing body 10 as it is. An axial movement range 51 (the length in the X-axis direction of the sliding hole 501 of the vane rotor 4) is secured.

(Operation of seal member)
As described above, the sealing recess 101 is formed at one end of the housing body 10 in the axial direction, and the rear plate 9 is inserted and fixed in the sealing recess 101. Therefore, the axial dimension of the device 1 can be reduced. Here, in the apparatus 1 in which the rotation of the crankshaft is transmitted by the belt B, the belt B deteriorates when the hydraulic oil adheres to the pulley 100 around which the belt B is wound. Therefore, it is necessary to seal the joint between the sealing recess 101 and the rear plate 9 so that the hydraulic oil in the housing HSG does not leak to the outside.

  However, as in the prior art, seal the portion where the axial end surfaces of the housing body 10 and the rear plate 9 are in contact (between the bottom surface 102 of the sealing recess 101 and the surface of the rear plate 9 on the X axis negative direction side). Then, the dimensions are insufficient. That is, as shown in FIG. 6C, the radial width (R-Ri) of the bottom surface 102 of the sealing recess 101 (excluding the portion where the shoe 11 and the like are formed) is used to install a seal member or seal It is short for cutting a groove (seal groove) for installing a member. Therefore, if an attempt is made to install a seal member (a seal groove is formed) by providing a sufficient space in a place where the end faces in the axial direction abut (the bottom surface 102 of the sealing recess 101), the housing body 10 is enlarged in the radial direction. I have to.

  On the other hand, the width in the X-axis direction of the sealing recess 101 and the width in the X-axis direction of the rear plate 9 have sufficient dimensions for sealing by installing a seal member (forming a seal groove) or the like. However, if a seal groove is provided on the inner peripheral surface of the housing main body 10 (the wall surface 103 of the sealing recess 101), the thickness of the housing main body 10 on the inner peripheral side of the pulley, that is, the radial width (Ro-R) is increased. Insufficient size. Therefore, if a seal groove is provided on the inner peripheral surface of the housing body 10 (the wall surface 103 of the sealing recess 101), the radial width (Ro-R) is increased to enlarge the housing body 10 in the radial direction. I must.

  On the other hand, in the first embodiment, the radial width (Ro-R), that is, the radial thickness of the housing body 10 is reduced. A groove 906 is provided on the outer periphery of the rear plate 9, and a seal ring S <b> 1 is installed in the groove 906, thereby sealing the joint between the sealing recess 101 and the rear plate 9. Such a sealing structure makes it possible to reduce the axial dimension of the device 1 by the sealing recess 101 and to seal the hydraulic oil in the housing HSG while suppressing an increase in the radial dimension of the device 1. Yes.

  On the other hand, on the surface on the X axis negative direction side of each shoe 11-13, there is a sufficient space around the bolt holes 110-130 for installing the seal member. Therefore, grooves 907 to 909 are provided around the bolt holes 901 to 903 of the rear plate 9 corresponding to the bolt holes 110 to 130, and the seal ring S2 is installed in the grooves 907 to 909 to seal the housing HSG. The hydraulic oil is prevented from leaking from the inside through the bolt holes 901 to 903.

  In addition, the bottom part is provided without penetrating the bolt holes 901 to 903 of the rear plate 9, and the bolt holes 901 to 903 are formed into a bottomed bag shape, thereby preventing leakage of hydraulic oil from the bolt holes 901 to 903. It is also possible. However, in this case, in order to fasten and fix the bolts b1 to b3 to the female screws of the bolt holes 901 to 903, a certain length of the bolt holes 901 to 903 is necessary. The plate 9 becomes thick in the axial direction. On the other hand, in the first embodiment, the bolt holes 901 to 903 are penetrated to make the bottom portion unnecessary, so that the axial dimension of the rear plate 9 is made as small as possible and thinned.

  The recess 900 of the rear plate 9 only needs to have a dimension in the X-axis direction necessary for engagement of the lock piston 51, and the pin hole 904 has a dimension in the X-axis direction necessary for press-fitting and fixing the positioning pin 905. Therefore, even if the bottom portion is provided, the rear plate 9 does not become thick in the axial direction. Therefore, in the first embodiment, the concave portion 900 and the pin hole 904 are both formed into a bottomed bag shape, so that leakage of hydraulic oil to the outside of the housing HSG is prevented without requiring a seal member.

  Female threads are formed on the inner periphery of the bolt holes 901 to 903 of the rear plate 9, and are screwed into the bolts b1 to b3. In a state where the bolts b1 to b3 are screwed into the female screw, the seal ring S2 provided around the bolt holes 901 to 903 is compressed and tries to return to the original state by elastic force. As a result, the engagement of the bolts b1 to b3 with the female screw is strengthened, and the tightened bolts b1 to b3 are prevented from loosening.

  On the other hand, regarding the structure for sealing the joint between the front plate 8 and the housing main body 10, the surface of the housing main body 10 on the X axis positive direction side is not provided with a sealing recess, and the sealing member is installed. Have sufficient radial space. That is, as shown in FIG. 6A, the radial width (Ro-Ri) of the housing body 10 is sufficiently large as a dimension for installing the seal member (forming a seal groove).

  Accordingly, a seal ring is provided at a position where the axial end surfaces of the housing body 10 and the front plate 8 abut each other (between the surface of the housing body 10 on the X axis negative direction side and the surface of the front plate 8 on the X axis positive direction side). 3 is installed. At that time, the seal ring 3 and the groove 89 were formed in a clover shape so as to pass through the inner peripheral sides of the bolt holes 83 to 85 so that the bolt holes 83 to 85 and the interior of the housing HSG were not communicated with each other. Thereby, the member which seals the circumference | surroundings of each bolt hole 83-85 separately is unnecessary, and assembly | attachment property can be improved, reducing a number of parts.

  In addition, in a state where the bolts b1 to b3 are screwed into the female screws of the bolt holes 901 to 903, the seal ring S3 in a portion located around each of the bolt holes 83 to 85 is compressed, and an attempt is made to return to the original state by elastic force. To do. As a result, the engagement of the bolts b1 to b3 with the female screw is strengthened, and the tightened bolts b1 to b3 are prevented from loosening.

  Each of the seal rings S1 to S3 is an O-ring having a circular cross section. Therefore, it is easy to install in each seal groove 906 etc. (the same applies to the seal ring S4). Moreover, a high sealing function can be ensured by compressing the O-ring in a state where the constituent members 8 to 10 of the housing HSG are fastened by the bolts b1 to b3.

[Effect of Example 1]
Hereinafter, effects of the device 1 of the present invention ascertained from the first embodiment will be listed.

  (1) A housing main body 10 having a sealing recess 101 formed at least at one axial end, and a first plate (rear plate 9) that is inserted and fixed in the sealing concave 101 to seal one axial end of the housing main body 10. And a second plate (front plate 8) for sealing the other axial end of the housing body 10.

  Therefore, the apparatus 1 can be reduced in size in the axial direction by inserting and fixing the first plate in the sealing recess 101 of the housing body 10. Therefore, the degree of freedom of mounting the device 1 in the engine room can be improved.

(2) The first plate (rear plate 9) is all inserted and fixed in the sealing recess 101 over the axial direction.
Therefore, the apparatus 1 can be effectively downsized in the axial direction, and the effect (1) can be improved.

(3) The first plate (rear plate 9) may be partially inserted and fixed in the sealing recess 101 over the axial direction.
That is, in the first embodiment, all the first plate (rear plate 9) is inserted and fixed in the sealing recess 101 in the axial direction, but may be partially inserted and fixed. In other words, the first plate may partially protrude from the housing body 10. Also in this case, the effect (1) can be obtained to some extent. In addition, it is possible to flexibly cope with various design conditions and to improve the degree of freedom of arbitrarily adjusting the axial dimensions of the inside of the housing and the first plate.

  (4) A housing body 10 having a sealing recess 101 formed at least at one end in the axial direction, and housed in the housing body 10 so as to be relatively rotatable, and by supplying and discharging fluid to and from the working chambers A1 to A3 and R1 to R3. A driven member (vane rotor 4) that rotates relative to the main body 10, an engaging member (lock piston 51) that is provided on the driven member and that moves in and out by the supply and discharge of fluid in the rotational axis direction, and an engaging member can be inserted. A first plate (rear plate 9) that is provided with an engaging recess (lock hole 521 of the sleeve 52) and is inserted and fixed in the sealing recess 101 to seal one end of the housing body 10 in the axial direction; And a second plate (front plate 8) for sealing the other end in the axial direction.

  That is, the first plate, which is relatively thick to provide the engaging recess, is inserted and fixed in the sealing recess 101. For this reason, the axial direction dimension of the apparatus 1 can be reduced more effectively.

  (5) The engaging recess (sleeve 52) of (4) above is constituted by a member separate from the first plate (rear plate 9), and is fixed to the first plate.

  Therefore, it is easy to adjust the shape, size, material, and the like of the engaging recess to those suitable for engagement / disengagement (engagement and release) of the engagement member (lock piston 51). It is possible to prevent the first plate from being worn or drowned.

  (6) The engaging recess (sleeve 52) of (4) is press-fitted into the bottomed recess 900 of the first plate.

  Thus, it can fix to a 1st plate more reliably by applying a pressure and pushing in an engagement recessed part. Further, by using the bottomed recess 900, the leakage of hydraulic oil can be prevented without requiring a seal member.

  (7) The engagement member (lock piston 51) of (4) is biased in a direction protruding toward the engagement recess (lock hole 521 of the sleeve 52), and at least at the tip (tip portion 511). Retreat from the engagement recess by the action of fluid pressure.

  In order to effectively apply fluid pressure to the front end of the engagement member in this way, even when the engagement member is engaged with the engagement recess, the engagement recess is in the engagement recess. It is necessary to provide a space γ (see FIG. 14) for supplying sufficient hydraulic oil. Therefore, it is necessary to ensure the axial thickness of the first plate by the space γ. Therefore, the axial dimension of the apparatus 1 can be reduced more effectively by inserting and fixing the thick first plate in the sealing recess 101 by providing the engaging recess having such a configuration.

  (8) A housing body 10 in which a sealing recess 101 is formed at least at one end in the axial direction and a plurality of first bolt insertion holes (bolt holes 110 to 130) are formed penetrating in the axial direction; A driven member (vane rotor 4) that is accommodated so as to be relatively rotatable and that rotates relative to the housing body 10 by supplying and discharging fluid to and from the working chambers A1 to A3 and R1 to R3, and a portion facing the first bolt insertion hole Female screw parts 901 to 903 are formed in the first plate, and a first plate (rear plate 9) that is inserted and fixed in the sealing recess 101 and seals one end in the axial direction of the housing body 10, and a first bolt insertion hole, A second bolt insertion hole (bolt holes 83 to 85) is formed at the opposite location, and the second plate (front plate 8) for sealing the other axial end of the housing body 10, the first bolt insertion hole and the first It is inserted into the bolt insertion hole, and a plurality of bolts b1~b3 screwed into the female screw portion 901 to 903, with a.

  That is, since the internal threaded portions 901 to 903 into which the bolts b1 to b3 are screwed are formed, the rear plate 9 that is relatively thick is inserted and fixed in the sealing recess 101. For this reason, the axial direction dimension of the apparatus 1 can be reduced more effectively.

  (9) In the above (8), the engaging member (lock piston 51) that appears and disappears by supplying and discharging fluid in the direction of the rotation axis is provided in the driven member (vane rotor 4), and the engaging recess into which the engaging member can be inserted. (Lock hole 521 of sleeve 52) is provided in the first plate (rear plate 9).

  Therefore, the effects (4) and (8) can be obtained in a superimposed manner. That is, since both the engaging recess and the female screw portions 901 to 903 are formed on the first plate, it can greatly contribute to reducing the axial dimension of the device 1.

  (10) The driven member (vane rotor 4) is fixed to one end side of the camshaft 3 via a camshaft insertion hole (supporting hole 92 of the bearing portion 91) provided on the inner periphery of the first plate (rear plate 9). Has been.

  Therefore, the housing HSG can swing with respect to the driven member with the camshaft insertion hole as a fulcrum. Here, when the engagement recess (lock hole 521 of the sleeve 52) is provided in the first plate as in (4) above, the distance (moment arm) from the swing fulcrum to the engagement recess can be shortened. Since the rocking displacement of the joint recess can be reduced, the displacement of the engagement member (lock piston 51) with respect to the engagement recess can be suppressed.

  (11) The driven member of (10) is provided with a boss 401 that is inserted through the camshaft insertion hole (support hole 92).

Therefore, by inserting the boss portion 401 into the camshaft insertion hole, the driven member can be rotatably supported on the first plate while being positioned with respect to the first plate. When the device 1 is installed on the camshaft 3, when the one end side (end portion 30) of the camshaft 3 is fixed to the driven member, the boss portion 401 is inserted into the camshaft insertion hole so that the driven member is first. Since it is positioned with respect to the plate, it is easy to fix the camshaft 3 to the driven member. Therefore, the assembly property can be improved. Further, since the boss portion 401 is inserted through the camshaft insertion hole, it is possible to suppress the inclination or swinging displacement of the driven member with respect to the housing HSG.
In particular, when the engagement recess (lock hole 521 of the sleeve 52) is provided in the first plate as described in (4) above, the tilt or swing displacement of the driven member with respect to the housing HSG is suppressed, so that the above (10). The effect of can be improved.

  (12) The housing body 10 is formed of an aluminum-based metal material, and the first plate (rear plate 9) is formed of an iron-based metal material.

  Therefore, the weight of the housing body 10 can be reduced. Further, when the female screw portions 901 to 903 are formed on the first plate as in (8) and the bolts b1 to b3 are screwed into the first plate, the strength of the female screw portions 901 to 903 can be ensured. . Furthermore, even when the bearing portion 91 is formed around the camshaft insertion hole (support hole 92) of (10) in the first plate and an oil seal is installed on the outer periphery of the bearing portion 91, the bearing portion 91 is Since wear is prevented by being made of iron, leakage of hydraulic oil from the inside of the apparatus 1 can be more reliably prevented.

  (13) The housing body 10 is formed by extrusion molding. By this extrusion molding, a pulley 100 is integrally formed on the outer periphery of the housing body 10 in the entire axial range. The first plate (rear plate 9) is formed by forging.

  Therefore, since the housing main body 10 is formed by extrusion, the seepage of hydraulic oil from the housing main body 10 is prevented, and the deterioration of the belt B wound around the pulley 100 can be prevented. Moreover, since the draft angle cannot be obtained as in die casting, the pulley 100 can be processed with high accuracy. Furthermore, since the first plate is formed by forging, it is possible to prevent the hydraulic oil from seeping out from the first plate.

  (14) The apparatus 1 of the above (4) to (7) and (10) to (13) is a vane type, and the housing body 10 is integrally formed with shoes 11 to 13 projecting inward on the inner periphery. The driven member is a vane rotor provided with vanes 41 to 43 that form advance chambers A1 to A3 and retard chambers R1 to R3 through which fluid is supplied to and discharged from the shoes 11 to 13, respectively. The engagement member protrudes and retracts in the rotation axis direction according to the state of the engine, and the first plate seals one axial end of the advance chambers A1 to A3 and the retard chambers R1 to R3 in the housing body 10. The second plate seals the other axial ends of the advance chambers A1 to A3 and the retard chambers R1 to R3 in the housing body 10.

  Therefore, the effects (4) to (7) and (10) to (13) can be obtained in the vane type device 1, respectively.

  Similarly, the device 1 of the above (8) to (13) is a vane type, and the housing main body 10 includes a plurality of shoes 11 to which first bolt insertion holes (bolt holes 110 to 130) are formed penetrating in the axial direction. 13 is a cylindrical member projecting inwardly on the inner periphery, and the follower members are advanced chambers A1 to A3 and retarded chambers R1 to R1 in which fluid is supplied to and discharged from the shoes 11 to 13, respectively. The vane rotor 4 includes vanes 41 to 43 that form R3, and the first plate (rear plate 9) is formed with female screw portions 901 to 903 of bolts at respective locations facing the first bolt insertion holes. The axial ends of the advance chambers A1 to A3 and the retard chambers R1 to R3 in the housing main body 10 are sealed, and the second plate (front plate 8) is placed at each position facing the first bolt insertion hole. 2 bolt insertion holes (bolt holes 83-85) It made which, it was decided to seal the axial end of the advancing chamber A1~A3 and a retarded angle chamber R1~R3 in the housing body 10.

  Therefore, the effects (8) to (13) can be obtained in the vane type device 1.

(15) The housing body 10 is a cylindrical member in which the pulley 100 is integrally formed on the outer periphery. Specifically, the housing body 10 is a hollow member in which the unevenness (pulley 100) extending in the axial direction is integrally formed in the entire axial range of the outer periphery.
Therefore, by integrally forming the pulley 100 on the outer periphery of the housing body 10, the apparatus 1 can be downsized not only in the axial direction but also in the radial direction.

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

  For example, in the first embodiment, the number of vanes (or shoes) is three, but other numbers may be used and are not particularly limited. Further, the number of bolts connecting the plates 8 and 9 and the housing body 10 is not limited to three.

  In the first embodiment, the device 1 of the present invention is installed on both the intake camshaft and the exhaust camshaft of the engine. However, it may be installed only on the intake side or only on the exhaust side.

  In Example 1, the sealing recess is formed only on the rear plate side of the housing body, and the rear plate is inserted and fixed in the sealing recess, but the sealing recess is also formed on the front plate side of the housing body, The front plate may be inserted and fixed in the sealing recess. In this case, the axial length of the device can be further shortened.

  In the first embodiment, the housing body is a member that opens at both axial ends, but may be a bottomed member that opens only at one end. Also in this case, the device can be miniaturized in the axial direction by providing a sealing recess at the opening end and inserting and fixing the first plate in the sealing recess.

  In the first embodiment, the female screw for fastening the bolts b1 to b3 is formed on the rear plate. However, the female screw is provided on the front plate instead of the rear plate, and the front plate, the housing body, and the rear plate are arranged in the negative direction of the X axis. The bolts b1 to b3 inserted from the side may be integrally fastened and fixed.

  In the first embodiment, the female screw is provided in the bolt hole of the rear plate. For example, the rear ends of the bolts b1 to b3 may be protruded through the rear plate, and nuts may be fastened thereto. Moreover, in Example 1, although the bolt hole was formed through the rear plate, it does not need to be penetrated.

  In the first embodiment, the seal recesses S1 and S2 are used to seal between the inner periphery of the sealing recess and the outer periphery of the rear plate, and between each bolt hole of the rear plate and the axial end surface of the shoe, respectively. However, sealing may be performed using a sealing agent instead of the seal ring. For example, if an adhesive also serving as a sealing agent is filled between the male screws of the bolts b1 to b3 and the female screw of the rear plate, not only the fastening force of the bolts b1 to b3 can be enhanced, but also the seal ring S2 (and its sealing groove). ) Can be made unnecessary.

  In the first embodiment, the seal rings S1 to S4 are O-rings, but other types of seal rings other than the O-rings may be used.

  In the first embodiment, the groove 89 for installing the seal ring S3 is provided on the front plate. However, the seal groove may be provided on the housing body side instead of the front plate. Further, although the seal groove 907 and the like of the seal ring S2 are provided on the rear plate, the seal groove may be provided on the housing body side instead of the rear plate.

  In the first embodiment, the clover-shaped seal ring 3 is provided. Instead of the seal ring 3, a seal ring that seals the inner peripheral side of the front plate (and the outer peripheral side of the bolt hole 83, etc.) and each bolt hole 83 are provided. It is also possible to provide a seal ring for sealing each of the surroundings.

  In the first embodiment, the front plate and the plug are formed by forging a ferrous metal material. However, the front plate and the plug may be formed by pressing or the like instead of forging. Other materials such as an aluminum-based metal material (aluminum alloy) may be used.

  In the first embodiment, the housing and the vane rotor are formed of an aluminum-based metal, but other materials such as an iron-based metal material may be used.

  In the first embodiment, the housing and the vane rotor (the material thereof) are formed by extrusion molding. However, the housing and the vane rotor may be formed by other methods such as die casting.

  In the first embodiment, the vane rotor is provided with the boss portion inserted through the camshaft insertion hole, but the boss portion may not be provided. Further, the configuration of the positioning means 905 is not limited to that of the first embodiment, and the positioning means 905 and the like need not be provided.

  In the first embodiment, the urging member of the device 1b is provided in all the advance chambers A1 to A3, but may be provided in a part of the advance chambers A. If the biasing member is not provided in the advance chamber A1 where the second stopper portion is provided, the contact area of the second stopper portion can be increased, thereby further deforming the second stopper portion. It can be surely prevented. In this case, even if an oil passage for operating the lock mechanism is formed in the vane 41 having the lock mechanism so as to communicate with the advance chamber A1, it does not interfere with the urging member and its support member (holding portion). Therefore, the degree of freedom in design is high.

  In the first embodiment, the urging member (spring unit) of the device 1b is provided in the advance chamber A, but may be provided in the retard chamber R. This is because, depending on the type in which the rotation of the crankshaft is transmitted to the camshaft, it may be necessary to bias the retarded side.

  In the first embodiment, the number of coil springs provided in the spring unit (biasing member) is one, but it may be two or more and is not particularly limited. Even if there are two or more, an increase in the axial dimension of the apparatus can be suppressed by arranging them in the radial direction instead of the housing axial direction.

  In the first embodiment, the coil spring is used in the spring unit. However, an elastic member such as a plate spring or a spiral spring may be used instead of the coil spring. In the first embodiment, each spring unit is provided with a support member (holding portion), but the support member (holding portion) may be omitted as appropriate.

  In the first embodiment, the coil spring is disposed in the concave portion formed on the opposite side surface of the vane and the shoe, but the concave portion is not formed, for example, a convex portion is formed to hold the coil spring. It is good to do.

  In the first embodiment, the first stopper portion is provided in the contact portion between the first vane 41 and the first shoe 11, and the other vanes 42 and 43 and the shoes 12 and 13 are configured to maintain the non-contact state. The first stopper portion may be provided in any one set of the other vanes 42 and 43 and the shoes 12 and 13 or a plurality of sets of contact portions. Similarly, the second stopper portion may be provided in any one set of vanes and shoes other than the first vane 41 and the first shoe 11 or a plurality of sets of contact portions.

  In the first embodiment, the first stopper portion is constituted by the circumferential side surfaces of the vane and the shoe, but may be constituted by other methods. For example, like the second stopper portion, the first stopper portion may be configured by forming a convex portion protruding from the outer periphery of the rotor.

  In the first embodiment, the second stopper portion is configured by the circumferential side surface of the portion protruding from the rotor toward the outer peripheral side and the circumferential side surface of the opposing shoe, but may be configured by other methods.

  In the first embodiment, the lock position is set to the most retarded angle side or the most advanced angle side. However, the present invention is not limited to this. In other words, the position where the relative rotation of the driven member and the housing is restricted does not have to coincide with the initial position locked for starting the engine.

  In the first embodiment, the lock piston that is engaged and disengaged by hydraulic pressure is used as the lock mechanism (engagement member), but another mechanism or member may be used. For example, a clutch mechanism or a lever mechanism may be used.

  In the first embodiment, the engagement concave portion of the lock mechanism is configured by a member (sleeve) different from the rear plate and is fixed to the rear plate. However, the engagement concave portion is directly provided integrally with the rear plate. It is good as well.

  In the first embodiment, the engagement concave portion (sleeve) of the lock mechanism is press-fitted into the concave portion of the rear plate.

  In the first embodiment, when the fluid pressure acts on the tip of the lock piston, the lock piston is retracted from the engagement recess and the lock is released, but the release mechanism may be configured by other configurations.

4 Vane rotor (driven member)
8 Front plate (second plate)
9 Rear plate (first plate)
DESCRIPTION OF SYMBOLS 10 Housing main body 11-13 The 1st-3rd shoes 41-43 The 1st-3rd vane 51 Lock piston (engaging member)
52 Sleeve (engaging recess)
521 Lock hole (engagement recess)
100 Pulley 101 Sealing recesses A1 to A3 First to third advance chambers (working chamber)
R1 to R3 1st to 3rd retarding chamber (working chamber)

Claims (8)

A toothed pulley is integrally formed on the outer periphery in the entire axial range, and a shoe that protrudes inward on the inner periphery is integrally formed, and a sealing recess is formed at least in one axial end. A housing body;
A vane rotor provided with a vane that is accommodated in the housing body so as to be relatively rotatable and forms an advance chamber and a retard chamber in which fluid is supplied to and discharged from the shoe;
An engagement member provided in the vane rotor and protruding and retracting in accordance with the state of the internal combustion engine in the rotation axis direction;
An engagement recess into which the engagement member can be inserted is provided, and a first plate that is inserted and fixed in the sealing recess and seals one axial end of the advance chamber and the retard chamber in the housing body,
A second plate fixed to the housing body and sealing the other axial end of the advance chamber and retard chamber;
Equipped with a,
The valve timing control device for an internal combustion engine , wherein the vane rotor is fixed to one end side of the camshaft through a camshaft insertion hole provided in an inner periphery of the first plate . The valve timing control apparatus for an internal combustion engine according to claim 1,
The valve timing control device for an internal combustion engine, wherein the first plate is inserted and fixed in the sealing recess in the axial direction. The valve timing control apparatus for an internal combustion engine according to claim 1,
The valve timing control device for an internal combustion engine, wherein the first plate is partially inserted and fixed in the sealing recess part in the axial direction. The valve timing control apparatus for an internal combustion engine according to claim 1,
The valve timing control device for an internal combustion engine, wherein the housing body is formed of an aluminum-based metal material, and the first plate is formed of an iron-based metal material. The valve timing control apparatus for an internal combustion engine according to claim 4,
The valve timing control device for an internal combustion engine, wherein the housing body is integrally formed with a pulley on the outer periphery by extrusion molding in the entire axial range, and the first plate is formed by forging. The valve timing control apparatus for an internal combustion engine according to claim 1,
The valve timing control device for an internal combustion engine, wherein the engaging recess is formed of a member separate from the first plate and is fixed to the first plate. The valve timing control apparatus for an internal combustion engine according to claim 6,
The valve timing control device for an internal combustion engine, wherein the engagement recess is press-fitted into a bottomed recess of the first plate. The valve timing control apparatus for an internal combustion engine according to claim 1,
The valve timing control for an internal combustion engine, wherein the engagement member is urged in a direction protruding toward the engagement recess, and retracts from the engagement recess when a fluid pressure acts on at least a tip thereof. apparatus.

Images