WO2016174957A1 - Oil pressure control valve and valve timing control device for internal combustion engine using oil pressure control valve - Google Patents

Abstract

An oil pressure control valve is equipped with: a hollow valve body (61) in the peripheral wall of which multiple ports for circulating operating oil are formed penetrating the peripheral wall in the radial direction; a first spool valve (65), which is provided so as to be movable in the axial direction inside the valve body (61), thereby switching the connected state of the operating oil with respect to the multiple ports in accordance with the position to which the spool valve is moved; and a second spool valve (63), which is provided coaxially with the first spool valve (65) and moves in the axial direction inside the valve body (61), thereby switching the connected state of the operating oil with respect to the multiple ports, in conjunction with the first spool valve (65) and in accordance with the position to which the first spool valve (65) has moved in the axial direction. Thus, it is possible to simplify control and reduce the size of the device.

Description

Hydraulic control valve and valve timing control device for internal combustion engine using the hydraulic control valve

The present invention relates to a hydraulic control valve capable of switching supply and discharge of hydraulic fluid to and from a plurality of hydraulic passages according to, for example, an operating state of a vehicle, and a valve timing control device of an internal combustion engine using the hydraulic control valve.

As a conventional hydraulic control valve, what was applied to the valve timing control device of the internal-combustion engine described in the following patent documents 1 is known. The hydraulic control valve is provided with a cylindrical cam bolt in which a supply / discharge port for letting hydraulic fluid flow in the radial direction of the peripheral wall penetrates, and the inside of the cam bolt can be moved axially in the axial direction. It has a first spool valve that switches the supply and discharge of hydraulic fluid to and from the change mechanism, and a second spool valve that is coaxially arranged with the first spool valve and that switches the supply and discharge of hydraulic fluid to the lock mechanism according to the movement position. ing.

The first and second spool valves are respectively connected to separate electromagnetic actuators, and the axial position is individually controlled by the respective electromagnetic actuators.

However, since the conventional hydraulic control valve has to independently control the axial position of the first and second spool valves by the respective electromagnetic actuators, it causes complication of control. By providing a plurality of electromagnetic actuators, the size of the apparatus is increased.

JP, 2012-193731, A

The present invention has been made in view of the above-described conventional technical problems, and hydraulic control that can suppress complication of control and upsizing of the device by enabling interlocking of the first and second spool valves. It is an object of the present invention to provide a valve and a valve timing control device in which the valve and the hydraulic control valve are used.

The present invention is provided with a hollow valve body in which a plurality of ports through which hydraulic fluid circulates in the radial direction of the peripheral wall are formed, and the valve body is axially movably provided inside the valve body. And a first spool valve for switching the communication state of the hydraulic fluid to the port, and coaxial with the first spool valve, and interlocked with the first spool valve according to the axial movement position of the first spool valve And a second spool valve which moves in the axial direction inside the valve body and switches the communication state of the hydraulic fluid to the plurality of ports.

According to the present invention, simplification and miniaturization of control can be achieved.

1 is an overall configuration diagram showing a valve timing control device according to an embodiment of the present invention in cross section. It is a front view which shows the state which the vane rotor provided to this embodiment rotated to the position of the most retarded phase. It is a front view which shows the state which the said vane rotor rotated to the position of the middle phase. It is a front view which shows the state which the same vane rotor rotated to the position of the most advance angle phase. It is an expanded sectional view showing operation of each lock pin in case a vane rotor of this embodiment is located near the most retarded angle. It is an expanded sectional view showing operation of each lock pin when the same vane rotor rotates to the advance side a little by alternating torque. It is an expanded sectional view showing operation of each lock pin when the same vane rotor rotates further to an advance side. It is an expanded sectional view showing operation of each lock pin when the same vane rotor rotates further to an advance side. It is an expanded sectional view showing operation of each lock pin when the same vane rotor rotates further to an advance side. It is an expanded sectional view showing operation of each lock pin when the same vane rotor rotates further to an advance side. It is the longitudinal cross-sectional view which disconnected the electromagnetic switching valve in this embodiment in the state which has a 1st, 2nd spool valve in a 1st position. It is a longitudinal cross-sectional view which shows the 2nd position of a 1st, 2nd spool valve. It is a longitudinal cross-sectional view which shows the 3rd position of a 1st, 2nd spool valve. It is a longitudinal cross-sectional view which shows the 4th position of a 1st, 2nd spool valve. It is a longitudinal cross-sectional view which shows the 5th position of a 1st, 2nd spool valve. It is a longitudinal cross-sectional view which shows the 6th position of a 1st, 2nd spool valve. It is a longitudinal cross-sectional view which shows the 7th position of a 1st, 2nd spool valve. FIG. 6 is a table showing the relationship between the stroke amount of the first spool valve and the supply and discharge of hydraulic oil to each hydraulic pressure chamber and lock passage. It is a longitudinal cross-sectional view of the electromagnetic switching valve concerning 2nd Embodiment. It is a longitudinal cross-sectional view of the electromagnetic switching valve concerning 3rd Embodiment. It is a whole block diagram of the valve timing control apparatus which concerns on 4th Embodiment.

Hereinafter, embodiments in which the hydraulic control valve according to the present invention is applied to a valve timing control device for an internal combustion engine will be described based on the drawings. In each embodiment, the valve timing control device is applied to the intake valve side of an internal combustion engine such as a hybrid car or an idle stop car, for example.
First Embodiment
The valve timing control device, as shown in FIG. 1 and FIG. 2, is disposed along a longitudinal direction of the engine with a sprocket 1 which is a drive rotating body rotationally driven by a crankshaft of the engine via a timing chain (not shown). And is disposed between the intake side camshaft 2 rotatably provided relative to the sprocket 1 and the sprocket 1 and the camshaft 2 so as to convert the relative rotational phase of the both 1 and 2 The hydraulic pressure is applied to the phase change mechanism 3, the lock mechanism 4 that locks the phase change mechanism 3 at an intermediate phase position between the most advanced phase and the most retarded phase, and the phase change mechanism 3 and the lock mechanism 4. And a hydraulic circuit 5 that operates to supply and discharge.

The sprocket 1 is configured as a rear cover that closes the rear end opening of the housing 7 described later, and is formed in a substantially thick disc shape, and has a gear portion 1a around which the timing chain is wound. At the same time, a support hole 1b rotatably supported on the outer periphery of the one end 2a of the camshaft 2 is formed in the center through. Further, in the sprocket 1, four female screw holes 1 c (not shown) are formed at circumferentially equally spaced positions on the outer peripheral side.

The camshaft 2 is rotatably supported by a cylinder head (not shown) via a plurality of cam bearings, and has a plurality of egg-shaped rotary cams for opening the intake valve (not shown), which is an engine valve, on the outer peripheral surface. While integrally fixed at a predetermined position in the axial direction, a bolt hole 6 into which a later-described valve body 61 having a function as a cam bolt is screwed is formed in the axial direction of the one end portion 2a. The bolt holes 6 are formed along the internal axial direction from the tip end side of the one end portion 2a. Further, the bolt hole 6 is formed in a step diameter reduction shape from the tip end side to the inner bottom side, and one end portion of a sleeve 62 described later is fitted to the inner peripheral surface of the large diameter portion 6a at the tip end side. On the other hand, a female screw 6c is formed in the small diameter portion 6b on the inner bottom side, and a male screw 61c of the valve body 61 is screwed to the female screw 6c.

Further, on the inner bottom side of the small diameter portion 6b of the bolt hole 6, there is formed a hydraulic pressure introducing chamber 6d to which hydraulic oil is pressure fed from an oil pump 45 described later.

The phase change mechanism 3 is fixed to the camshaft 2 via the valve body 61 and a housing 7 integrally provided in the axial direction of the sprocket 1 as shown in FIGS. 1 and 2. A vane rotor (movable member) 9, which is a driven rotating member rotatably accommodated in the housing 7, and four first members which are provided on the inner peripheral surface of the housing 7 so as to protrude inward (center). There are provided four retarding angles, a retarding hydraulic pressure chamber 11 and an advancing hydraulic pressure chamber 12, which are advance working chambers, respectively, which are separated by the fourth shoes 10a to 10d and the vane rotor 9.

The housing 7 comprises a cylindrical housing body 10, a front plate 13 formed by press molding to close the front end opening of the housing body 10, and the sprocket 1 as a rear cover closing the rear end opening. It is done.

The housing body 10 is integrally formed of a sintered metal, and the four shoes 10a to 10d are integrally protruded at substantially equal positions in the circumferential direction of the inner peripheral surface, and the shoes 10a to 10d are integrally formed. Bolt insertion holes 10 e are respectively formed to penetrate in the axial direction on the outer peripheral side of 10 d.

The front plate 13 is formed in the shape of a thin disc made of metal and has a through hole 13a at the center, and four bolt insertion holes 13b (not shown) at equally spaced positions in the circumferential direction on the outer peripheral side. It is formed through.

The sprocket 1, the housing body 10 and the front plate 13 are cofastened and fixed by four bolts 14 (not shown) which are inserted through the bolt insertion holes 13b and 10e and screwed to the female screw holes 1c. .

Incidentally, 1e in FIG. 2 is a positioning pin attached to the outer peripheral side of the inner surface 1d of the sprocket, and the positioning pin 1e is formed on the outer peripheral surface of the first shoe 10a of the housing main body 10. The housing main body 10 is positioned relative to the sprocket 1 at the time of assembly by being fitted into the positioning groove 10f.

The vane rotor 9 is integrally formed of a metal material, and as shown in FIGS. 1 and 2, a rotor 15 fixed to the one end of the camshaft 2 by the valve body 61 and an outer peripheral surface of the rotor 15. It is composed of four first to fourth vanes 16a to 16d radially projected at equal intervals of approximately 90 ° in the circumferential direction.

The rotor 15 is formed in a relatively thick, short cylindrical shape in the axial direction, and a bolt insertion hole 15a is formed substantially at the center position, and a head portion 61a of the valve body 61 described later is seated at the front end A circular seating surface 15b is formed.

Further, the rotor 15 is formed in a large diameter shape having a uniform outer diameter as a whole, and the amount of protrusion of each of the shoes 10a to 10d facing the outer peripheral surface in the radial direction is equal to the outer diameter of the rotor 15. Correspondingly, it is set relatively short and is formed in a substantially rectangular shape on the side.

In addition, seal members 17a which are in sliding contact with the outer peripheral surface of the rotor 15 are respectively fitted and fixed to the end edges of the first to fourth shoes 10a to 10d. Each seal member 17a is formed substantially in a U-shape, and is urged toward the outer peripheral surface of the rotor 15 by a plate spring (not shown) provided on the bottom surface side of each seal groove.

Each of the vanes 16a to 16d is set so that the total projection length is substantially the same, and the circumferential width is substantially the same and relatively thin, and each of the vanes 16a to 16d is between the shoes 10a to 10d. Is located in

Further, a seal groove having a rectangular cross section is formed along the axial direction on the tip outer peripheral portion of each of the vanes 16a to 16d, and the seal groove slides on the inner peripheral surface of the housing main body 10. U-shaped seal members 17 b are provided to be in contact with each other.

Between the retard hydraulic chamber 11 and the advance hydraulic chamber 12 is constantly sealed by the shoes 10a to 10d and the seal members 17a and 17b of the vanes 16a to 16d.

Further, as shown in FIG. 2, when the vane rotor 9 relatively rotates toward the retard side, the vane rotor 9 abuts against the opposing side face of the first shoe 10 a where one side face of the first vane 16 a faces, and the rotational position on the maximum retard side As shown in FIG. 4, when the relative rotation to the advance side is performed, the other vanes of the first vane 16a abut against the opposite side surface of the other second shoe 10b, and the rotational position on the maximum advance side is restricted. It is supposed to be That is, the first and second shoes 10a and 10b exhibit the stopper function of the vane rotor 9 via the first vane 16a.

At this time, the other vanes 16b to 16d are in a separated state without contacting the opposing surfaces of the shoes 10a to 10d whose both side surfaces are opposed in the circumferential direction. Therefore, the contact accuracy between the first vane 16a and the first and second shoes 10a and 10b is improved, and the supply speed of the hydraulic pressure to the hydraulic chambers 11 and 12 described later is increased. Rotational response is high.

In the normal relative rotation control with the housing 7, the vane rotor 9 is in contact with the first shoe 10a or the second shoe 10b to which the first vane 16a corresponds, according to the most retarded phase and the most advanced phase. The relative rotation control is also performed inside, that is, in a slightly middle range.

The aforementioned retarded oil pressure chambers 11 and advance oil pressure chambers 12 are separated between the side surfaces in the forward and reverse rotational directions of the vanes 16a to 16d and the side surfaces of the shoes 10a to 10d. The respective retarding hydraulic chambers 11 and the advancing hydraulic chambers 12 are provided with the hydraulic circuit 5 via the retarding oil holes 11a and the advancing oil holes 12a formed along the inner diameter direction of the rotor 15, respectively. It communicates with each of the

The lock mechanism 4 rotates the vane rotor 9 with respect to the housing 7 at the most retarded side relative to the housing 7 (the position shown in FIG. 2) and at the most advanced angled position (the position shown in FIG. 4). ) And the intermediate rotational phase position (position in FIG. 3).

That is, as shown in FIGS. 1 to 5, first to third locks which are first to third lock recesses formed at predetermined positions on the inner surface (sprocket inner surface 1d) of the sprocket 1 on the rotor 15 side. First to third lock pins which are three first to third lock members provided at three locations in the circumferential direction of the holes 15 to 26 and the inner circumferential direction of the rotor 15 and engaged with the respective lock holes 24 to 26 respectively 27 to 29, and first to third release pressure receiving chambers 30 to 32 for releasing the engagement of the lock pins 27 to the lock holes 24 to 26, respectively.

The first lock hole 24 is formed in the inner surface 1d of the sprocket on the side of the first large diameter portion 15c, and formed in a circular shape having a diameter larger than the outer diameter of the small diameter tip 27a of the first lock pin 27 described later. As a result, the inserted tip 27a is slightly movable in the circumferential direction. Further, the first lock hole 24 is formed at an intermediate position closer to the advancing side than the rotational position on the most retarded side of the vane rotor 9 of the inner surface 1 d of the sprocket. Further, in the first lock hole 24, the depth of the bottom surface 24a is set to be substantially the same depth as the second bottom surfaces 25b and 26b of the second and third lock holes 25 and 26 described later.

Therefore, when the tip end portion 27a of the first lock pin 27 is engaged with the first lock hole 24 and abuts against the bottom surface 24a as the vane rotor 9 rotates in the advancing direction, the side edge of the tip end portion 27a The movement in the retard direction of the vane rotor 9 is restricted at the time when it abuts against the inner edge 24 b in the circumferential direction of the lock hole 24.

The second lock hole 25 is formed in the sprocket inner surface 1 d on the side of the first large diameter portion 15 c as in the first lock hole 24, and is formed in a step shape of a long groove along the circumferential direction. That is, with the sprocket inner side surface 1d as the uppermost step, it is formed in a step-like shape in which the first bottom surface 25a and the second bottom surface 25b sequentially become lower than this. At the same time, the inner side edge 25c on the advance side of the second bottom surface 25b is also a wall surface rising vertically.

The second bottom surface 25b is formed slightly longer in the circumferential direction on the advance side, and the second lock pin 28 is in the advanced state as shown in FIGS. It can move slightly in the direction.

The third lock hole 26 is formed in a circular arc long groove shape extending in the circumferential direction of the sprocket 1 longer than the second lock hole 25 on the second large diameter portion 15 d side, and the sprocket inner side surface 1 d The vane rotor 9 is formed at an intermediate position closer to the advancing side than the rotational position on the most retarded side of the vane rotor 9. Further, the third lock hole 26 is formed in a three-step shape in which the bottom surface is lowered from the retardation side to the advance side, and this functions as a lock guide groove.

That is, the third lock hole 26 is formed in a step-like shape in which the first inner bottom surface 26a and the second bottom surface 26b sequentially become lower with the inner surface 1d of the sprocket as the uppermost step. Along with the wall surface that has risen, the inner edge 26c on the advancing side of the second bottom surface 26b also becomes a wall surface that has stood upright.

The lock holes 24 to 26 are formed by hole forming members fitted and fixed in the holding holes formed on the sprocket 1.

The first lock pin 27 is slidably disposed in a first pin hole 33a formed in an axial direction penetrating in an inner axial direction on the side of the first lock hole 24 of the rotor 15, and has a small diameter tip 27a and the tip A hollow large-diameter portion 27b located on the rear side of 27a and a step pressure receiving surface 27c formed between the tip 27a and the large-diameter portion 27b are integrally formed. The tip end portion 27 a is formed in a flat surface shape such that the tip end surface can be in close contact with the bottom surface 24 a of the first lock hole 24.

Further, the first lock pin 27 is a first lock by a spring force of a first spring 36, which is a biasing member resiliently mounted between the bottom of the concave groove in the large diameter portion 27b and the inner surface of the front plate 13. It is biased in a direction to engage the hole 24.

As shown in FIGS. 2 and 5, the first release pressure receiving chamber 30 communicates with the hydraulic circuit 5 via a first branch passage 30a formed along the inner radial direction of the rotor 15. When the hydraulic pressure is supplied from the hydraulic circuit 5, the hydraulic pressure acts on the step pressure receiving surface 27c to move the first lock pin 27 backward against the spring force of the first spring 36. The engagement between the first lock pin 27 and the first lock hole 24 is released.

The second lock pin 28 is slidably disposed in a second pin hole 33b formed in the axial direction of the rotor 15 on the side of the second lock hole 25 so that the outer diameter is formed in a step diameter shape. A small diameter distal end portion 28a, a hollow large diameter portion 28b located on the rear side of the distal end portion 28a, and a step pressure receiving surface 28c formed between the distal end portion 28a and the large diameter portion 28b; Are integrally formed. The tip end portion 28a is formed in a flat surface shape such that the tip end surface can be in contact with the bottom surfaces 25a and 25b of the second lock hole 25 in a close contact state.

The second lock pin 28 is a biasing member resiliently mounted between the bottom surface of the recessed groove formed in the axial direction from the rear end side of the large diameter portion 28 b and the inner surface of the front plate 13. The spring force of the spring 37 urges the second lock hole 25 to engage.

The second release pressure receiving chamber 31 communicates with the hydraulic circuit 5 via a second branch passage 31 a formed along the inner radial direction of the rotor 15, and the hydraulic pressure is supplied from the hydraulic circuit 5. The second lock pin 28 and the second lock pin 28 are moved backward by moving the second lock pin 28 against the spring force of the second spring 37 by acting the hydraulic pressure on the step pressure receiving surface 28c. The engagement with the lock hole 25 is released.

The third lock pin 29 is slidably disposed in a third pin hole 33c which is formed to penetrate in the inner axial direction on the third lock hole 26 side of the rotor 15, and the outer diameter is formed in a step diameter shape. A small diameter tip portion 29a, a hollow large diameter portion 29b located rearward of the tip portion 29a, and a step pressure receiving surface 29c formed between the tip portion 29a and the large diameter portion 29b; Are integrally formed. The distal end portion 29a is formed in a flat surface shape such that the distal end surface can be in close contact with the bottom surfaces 26a and 26b of the third lock hole 26.

The third lock pin 29 is a biasing member resiliently mounted between the bottom surface of the concave groove formed in the axial direction from the rear end side of the large diameter portion 29 b and the inner surface of the front plate 13. The spring force of the spring 38 biases the third lock hole 26 in a direction in which it is engaged.

The third release pressure receiving chamber 32 is in communication with the hydraulic circuit 5 via a third branch passage 32 a formed along the inner radial direction of the rotor 15, and hydraulic pressure is supplied from the hydraulic circuit 5. This hydraulic pressure acts on the step pressure receiving surface 29c to move the third lock pin 29 backward against the spring force of the third spring 38, whereby the third lock pin 29 and the third lock pin 29 are moved. The engagement with the lock hole 26 is released.

The rear end sides of the first to third pin holes 33a to 33c communicate with the atmosphere through a breathing hole (not shown) in order to ensure good slidability of the lock pins 27, 28 and 29. ing.

Further, as shown in FIGS. 1 to 4, between each pair of the retarding side oil hole 11 a and the advancing side oil hole 12 a which are adjacent to each other with the vanes 16 a to 16 d interposed therebetween, Two passage control mechanisms 50, 50 are provided to appropriately block or restrict communication between the retard side oil hole 11a and the advance side oil hole 12a.

Since both the passage control mechanisms 50, 50 have the same configuration, one side will be specifically described below for convenience. That is, the passage control mechanisms 50 are provided at substantially symmetrical positions on the opposite side of the pin holes 33 a to 33 c of the rotor 15, and the retarding oil holes 11 a along the internal axial direction of the rotor 15. And the advance-side oil hole 12a, and is provided slidably in the communication hole 51, and the communication hole 51 is provided via the communication hole 51 according to the sliding position. The valve body 52 which changes the communication state of both oil holes 11a and 12a, the spring 53 which is a spring member which biases the valve body 52 in the direction in which the oil holes 11a and 12a communicate, and the rotor 15 An oil passage hole 54, which is bored in a radial direction on the end face of the peripheral part and acts in a direction to block the communication of each oil hole 11a, 12a against the spring force of the spring 53, mainly formed. ing.

As shown in FIGS. 1 to 4, the communication hole 51 has an inner diameter set to substantially the same size as each of the pin holes 33 a to 33 c, and the advancing side and the retard side oil hole 11 a adjacent to each other. It is formed across the oil holes 12a.

The valve body 52 has a small diameter valve shaft 52a at the center, a valve portion 52b and a sliding portion 52c of the same large diameter formed at both ends of the valve shaft 52a, and a tip end surface of the valve portion 52b. The projection 52d is formed. An annular groove 52e is formed on the outer periphery of the valve shaft 52a, and the entire valve body 52 is urged to the right by the spring force of the spring 53 as shown in FIG. The two oil holes 11a and 12a are in communication with each other. Further, the valve portion 52b is set such that its axial length at least closes the open end of the advance side oil hole 12a.

The spring 53 has one end resiliently in contact with the bottom surface of the hollow sliding portion 52c, while the other end resiliently contacts the inner surface of the front plate 13 so that the entire valve body 52 can be seen in FIG. It is biased in the direction.

The oil passage hole 54 is disposed on the side of the pressure receiving surface 52f, which is the tip end surface of the projection 52d, and is formed to communicate with a lock communication hole 78 of the electromagnetic switching valve 60 described later. Then, the hydraulic pressure supplied through the lock communication hole 78 acts on the pressure receiving surface 52f, thereby pressing the valve body 52 in the left direction as shown by a dashed dotted line in FIG. Communication between the two oil holes 11a and 12a through 52e is shut off.

As shown in FIG. 1, the hydraulic circuit 5 is a hydraulic pressure that switches the supply and discharge of hydraulic fluid to the retarding hydraulic chambers 11, the advancing hydraulic chambers 12, and the first to third pressure receiving chambers 30 to 32, as shown in FIG. A single electromagnetic switching valve 60 which is a control valve, a supply passage 41 for supplying hydraulic oil drawn from an oil pan 44 to the electromagnetic switching valve 60, the retarding hydraulic chambers 11 and the advancing hydraulic chambers 12 and The first and second drain passages 42 and 43 for returning the hydraulic oil discharged from the first to third release pressure receiving chambers 30 to 32 through the electromagnetic switching valve 60 to the oil pan 44 .

The supply passage 41 is provided with an oil pump 45 in the middle of the flow passage, and an upstream side of the oil pump 45 is formed as a suction passage 41a, and a downstream side of the oil pump 45 is a discharge passage 41b. It is formed as.

One end of the first drain passage 42 is a drain communication hole 79 of a sleeve 62 (described later) of the electromagnetic switching valve 60 via a drain hole 42a formed along the radial direction of the camshaft 2 (FIG. 11). While the other end is connected to the oil pan 44.

One end of the second drain passage 43 is connected to a drain hole 90 (see FIG. 11) of the first spool valve 65 described later of the electromagnetic switching valve 60, and the other end is the oil pan 44. It is connected to the.

The oil pump 45 is a general one such as a trochoid pump rotationally driven by a crankshaft of an engine, and is operated by being sucked from the inside of the oil pan 44 through the suction passage 41a by rotation of the outer and inner rotors. Oil is discharged through the discharge passage 41b, and a part of the oil is supplied from the main oil gallery M / G to each sliding portion of the internal combustion engine, and the other is supplied to the electromagnetic switching valve 60 side. It is supposed to be. A flow control valve 47 is provided downstream of the discharge passage 41b for returning the excess hydraulic oil discharged from the discharge passage 41b to the suction passage 41a via a reflux passage 46 and controlling the flow to an appropriate flow rate. And a filtration filter 48 for collecting and filtering foreign matter in the hydraulic oil.

The electromagnetic switching valve 60 is, as shown in FIGS. 1 and 11, a 6-port, 7-position proportional valve including a substantially cylindrical valve body 61 and a cylinder fixed to the outer peripheral surface of the valve body 61. Sleeve 62, a second spool valve 63 axially slidably provided in the valve body 61, and an inner end of the valve body 61, the second spool valve 63 is shown in FIG. A second valve spring 64 biased leftward in 1; a first spool valve 65 slidably provided in the second spool valve 63 in the axial direction; and an inner end of the second spool valve 63 The first valve spring 66 is provided on the side to urge the first spool valve 65 in the left direction in FIG. 1 and the other end side of the valve body 61, and the first valve spring 66 is First and second spool valves 63, Wherein the 5 first, and the second solenoid 67 is an actuator that moves against the spring force of the valve spring 64, 66 to the right in FIG. 1, and is mainly comprised.

As shown in FIG. 11, the valve body 61 is formed of an iron-based metal material, functions as a cam bolt as described above, is provided at the other end, and a fastening jig such as a spanner can be fitted on the outer periphery A head portion 61a having a hexagonal portion is formed, and an externally threaded portion 61c axially extending from the base of the head portion 61a and screwed to the internally threaded portion 6c of the camshaft 2 is formed on the outer peripheral surface of the tip portion. And a cylindrical shaft portion 61b.

Further, a hole 68 is bored at a substantially axial position of the valve body 61 from the tip end surface side of the shaft 61b toward the head 61a. The hole 68 is formed in a step diameter shape, and a large diameter hole 68a from the opening end on the side of the shaft 61b to approximately 1/3 of the inner axial direction, and an annular step in the large diameter hole 68a. And a small diameter hole 68b connected to the surface 68c and extended to the inside of the head 61a.

Further, the hole 68 is formed as an introduction port 69 whose open end on the tip end side in the axial direction of the valve body 61 is connected to the downstream end of the discharge passage 41 b. The hydraulic fluid discharged from the discharge passage 41 b is introduced into the introduction port 69 via the hydraulic pressure introducing chamber 6 d of the bolt hole 6.

Further, the hole portion 68 is press-fitted and fixed to the inner circumferential surface in a state where the cup-shaped retainer 70 is in contact with the step surface 68c, and the working oil is directly supplied from the oil pump 45 to the internal space by the retainer 70. It is separated into a check valve chamber 71 on the side of the male screw portion 61c, which is introduced as described above, and a second spool valve chamber 72 on the side of the head 61a which houses and holds the second spool valve 63.

In the check valve storage chamber 71, four lead ports 73a for guiding the hydraulic oil introduced into the inside are formed in a penetrating manner along the cruciform radial direction in the peripheral wall, and the introduction port 69 is inserted from the lead port 73a. A check valve 74 for restricting the backflow of the hydraulic fluid discharged from the oil pump 45 is attached and fixed to the inner peripheral surface of the side.

The check valve 74 includes a bottomed cylindrical body portion 74a and a ball valve body 74b axially movably accommodated in the body portion 74a.

The body portion 74a is formed with an opening hole 74c communicating with the introduction port 69 of the valve body 61 on the tip end side.

The ball valve body 74b is biased by a coil spring 74d in a direction to be seated on the inner end hole edge of the opening hole 74c to close the opening hole 74c, and also acts on the introduction port 69 or more. It is moved backward against the spring force of the coil spring 74d by oil pressure to open the opening hole 74c. The hydraulic oil introduced into the body portion 74a from the opening hole 74c flows toward the outlet port 73a through an oil passage 74e formed in the body portion 74a.

The second spool valve accommodating chamber 72 has a drain wall 21a, a lock port 20a, a first reintroduction port 73b, and an advance port 19a in the circumferential wall sequentially from the male screw portion 61c to the head 61a. The second reintroduction port 73c and the retardation port 18a are respectively formed in a penetrating manner along the cross radial direction of the second spool valve accommodating chamber 72, and four are provided.

Each of the outlet ports 73a and the first and second reintroduction ports 73b and 73c are formed at substantially the same angular position in the circumferential direction, while the other ports 18a, 19a, 20a and 21a and Is set so that the angular position in the circumferential direction does not overlap.

Further, on the bottom wall of the hole 68, a through hole 68d having a diameter smaller than the inner diameter of the small diameter hole 68b of the hole 68 is formed to penetrate in the axial direction.

The sleeve 62 is formed of a synthetic resin material, and is divided into two in the radial direction, and the two divided portions are radially butted and joined by, for example, a welding method to form a cylindrical integral. It is formed.

The inner diameter of the sleeve 62 is substantially the same as the outer diameter of the shaft portion 61b of the valve body 61, and the inner peripheral surface is fixed to the outer peripheral surface of the shaft portion 61b from the outside. . Further, in the sleeve 62, a cylindrical positioning protrusion 62a protrudes from an end of the inner peripheral surface on the side of the electromagnetic solenoid 67, and the positioning protrusion 62a is used in the vicinity of the head 61a of the shaft 61b. The valve body 61 can be positioned in the circumferential direction and the axial direction by fitting it with a positioning hole 61 d drilled on the outer peripheral surface of the valve body 61.

Further, in the sleeve 62, four communicating grooves 75 respectively communicating with the respective outlet ports 73a are formed on the inner peripheral surface along the axial direction.

Each of the communication grooves 75 constitutes a communication passage between the inner peripheral surface thereof and the outer peripheral surface of the shaft portion 61b of the valve body 61, and one end portion on the male screw portion 61c overlaps with each of the outlet ports 73a. On the other hand, the other end is extended to a position where it communicates with the first and second reintroduction ports 73b and 73c. Thus, the outlet ports 73a are always in communication with the first and second reintroduction ports 73b and 73c through the communication grooves 75, respectively.

Further, in the peripheral wall of the sleeve 62, a retard communication hole 76 for communicating the respective retard side oil holes 11a with the respective retard ports 18a, the respective advance side oil holes 12a, the respective advance ports 19a, and the like. , The lock communication hole 78 for communicating the branch passages 30a, 31a and 32a with the lock port 20a, and the drain communication for communicating the drain hole 42a with the drain port 21a. Holes 79 are formed.

The communication holes 76 to 79 are axially offset (biased) with respect to the axial positions of the corresponding ports 18a, 19a, 20a and 21a, respectively. The sleeve 62 has an axial groove extending in the axial direction on the inner peripheral side of the sleeve 62. The communication holes 76 to 79 respectively communicate with the ports 18a, 19a, 20a and 21a via the axial grooves. Further, an annular groove groove 79a is formed at a portion on the outer peripheral side of the sleeve 62 of each of the drain communication holes 79.

The second spool valve 63 is formed in a bottomed hollow shape with one end 63a on the retainer 70 side open, and the internal space thereof accommodates and holds the first spool valve 65 so as to be movable in the axial direction. It is configured as a first spool valve storage chamber 80.

In the second spool valve 63, a cylindrical sliding hole 63c is formed through the bottom wall on the other end 63b side, and the first spool valve 65 is slid in the sliding hole 63c. It is inserted in a movable manner.

Furthermore, in the second spool valve 63, the opening is closed by a lid member 81 fitted on the inner peripheral surface of an annular groove formed on the inner peripheral surface of the opening of the one end portion 63a.

The lid member 81 is formed of a metal material, and has a bottomed cylindrical lid main body 81a, and a flange portion which is formed so as to protrude radially outward from the opening end edge of the lid main body 81a and is fitted in the annular groove And 81b.

The lid member 81 accommodates and holds the first valve spring 66 inside the lid main body 81a, and the end face of one end of the first spool valve 65 can be in contact with the inner end edge of the flange portion 81b. It has become.

In addition, the outer end edge of the flange portion 81 b elastically holds one end of the second valve spring 64.

Furthermore, in the bottom wall of the lid main body 81a, a cylindrical through hole 81c is formed in a penetrating manner along the axial direction, and the through hole 81c constitutes a part of the first drain passage 42.

One end of the second valve spring 64 elastically contacts the outer end surface of the flange portion 81 b in the axial direction, and the other end elastically contacts the inner bottom surface of the retainer 70 in the axial direction. Is always urged toward the electromagnetic solenoid 67 side.

In the second spool valve 63, a cylindrical guide portion 82 slidingly guiding the second spool valve 63 to the inner circumferential surface of the second spool valve chamber 72 is provided on the outer circumferential surface on the other end 63b side. While being formed, eight first to eighth land portions 83a to 83h are provided at predetermined intervals in the axial direction on the outer peripheral surface closer to the one end portion 63a than the guide portion 82.

The land portions 83a to 83h are guided in axial movement while the outer peripheral surface thereof is in sliding contact with the inner peripheral surface of the second spool valve accommodating chamber 72 with a minute gap.

On the outer peripheral surface between the first land portion 83a and the second land portion 83b adjacent thereto, there is formed a first groove groove 84a which appropriately communicates with the drain port 21a while always communicating with the lock port 20a. ing.

Further, a second groove groove 84b appropriately communicated with the first reintroduction port 73b is formed on the outer peripheral surface between the second land portion 83b and the third land portion 83c adjacent to the second land portion 83b. Further, a third groove 84c is formed on the outer peripheral surface between the third land portion 83c and the fourth land portion 83d adjacent to the third land portion 83c. The third groove 84c appropriately communicates with the advance port 19a.

In addition, a fourth groove groove 84d always communicating with the advance port 19a is formed on the outer peripheral surface between the fourth land portion 83d and the fifth land portion 83e adjacent thereto. Further, a fifth groove groove 84e appropriately communicated with the advance port 19a and the second reintroduction port 73c is formed on the outer peripheral surface between the fifth land portion 83e and the sixth land portion 83f adjacent thereto. ing.

Further, on the outer peripheral surface between the sixth land portion 83f and the seventh land portion 83g adjacent thereto, there is formed a sixth groove groove 84f which appropriately communicates with the second reintroduction port 73c and the retardation port 18a. ing. Further, a seventh groove 84g always communicating with the retardation port 18a is formed on the outer peripheral surface between the seventh land 83g and the eighth land 83h adjacent thereto.

Further, an eighth groove groove 84h appropriately communicating with the retardation port 18a is formed on an outer peripheral surface between the eighth land portion 83h and the guide portion 82 adjacent thereto.

The first to eighth groove grooves 84a to 84h are first to eighth communication holes 85a constantly communicating with the first spool valve accommodating chamber 80 at predetermined positions in the axial direction and circumferential direction of the respective bottom walls. The through holes 85 h are formed to penetrate in the radial direction.

The first spool valve 65 is formed in a substantially cylindrical shape, and most of the side from the one end 65 a to the other end 65 b on the side of the retainer 70 is accommodated in the first spool valve accommodation chamber 80, The other end 65 b protrudes outward of the valve body 61 through the through hole 68 d of the valve body 61 and the sliding hole 63 c of the second spool valve 63.

Further, the first spool valve 65 is configured as an oil passage through which the working oil flows, and the partition portion 86 for blocking the flow of the working oil at an axial intermediate position of the oil passage. Are integrally formed. The oil passage is separated by the partition 86 into a first oil passage hole 87 on the other end 65b side and a second oil passage hole 88 on the one end 65a side. In addition, this partition part 86 is formed using the remaining part at the time of carrying out drilling processing of the said 1st spool valve 65 by a drill etc. from both ends.

The opening end of the first oil passage hole 87 is closed by a ball-shaped blind plug 89, and a pair of upper and lower drain holes 90 are formed penetrating in the radial direction in the peripheral wall near the opening end. . The drain hole 90 communicates with the oil pan 44 via the second drain passage 43. As a result, the hydraulic oil flowing into the first oil passage hole 87 is always returned to the oil pan 44 via the two drain holes 90 and the second drain passage 43.

The second oil passage hole 88 has an annular groove formed on the inner peripheral surface of the opening, and the opening is closed by a disc-like plug 91 fitted on the inner peripheral surface of the annular groove. ing.

One end of the first valve spring 66 is in elastic contact with the end face of the plug body 91 on the side of the retainer 70 in the axial direction, and the other end is elastic against the inner bottom face of the lid member 81 of the second spool valve 63 from the axial direction. At the same time, the first spool valve 65 is always urged toward the electromagnetic solenoid 67 side.

In addition, a non-return that prevents the hydraulic oil supplied from the lock port 20a to the release pressure receiving chambers 30 to 32 from flowing back to the first reintroduction port 73b inside the second oil passage hole 88. A valve 92 is housed.

The check valve 92 is press-fit into the inner peripheral surface of the second oil passage hole 88, and an annular valve seat 93 having an opening hole 93a formed substantially at the axial center position, and the second oil passage hole 88 A metal ball valve body 94 provided on the opening side of the valve seat 93 of the valve seat 93 so as to be able to be seated on the hole edge of the opening hole 93a of the valve seat 93; And a coil spring 95 always biased toward the side 93.

When the hydraulic oil is not introduced into the second oil passage hole 88 from the first reintroduction port 73b, the check valve 92 is seated on the hole edge of the opening hole 93a by the coil spring 95 to open the opening. By closing the hole 93a, a backflow of hydraulic oil from the lock port 20a is suppressed. On the other hand, when the hydraulic oil is introduced, the hydraulic pressure of the hydraulic oil is drawn back against the spring force of the coil spring 95 by the hydraulic pressure of the hydraulic oil to lead the hydraulic oil to the lock port 20a. It is supposed to

Further, the first spool valve 65 has a cylindrical guide portion 96 slidingly guiding the first spool valve 65 to the inner peripheral surface of the first spool valve storage chamber 80 on the outer peripheral surface on the other end 65b side. As well as being formed, seven ninth to fifteenth land portions 97a to 97g are integrally formed on the outer peripheral surface on one end side with respect to the guide portion 96 at predetermined intervals in the axial direction.

The lands 97a to 97g have their outer peripheral surfaces in sliding contact with the inner peripheral surface of the first spool valve accommodating chamber 80 with a minute gap, and are guided in axial movement.

A ninth groove 98a is formed on the outer peripheral surface on one end side of the ninth land 97a so as to appropriately communicate with the first communication hole 85a of the second spool valve 63.

Further, a tenth groove groove 98b appropriately communicated with the first communication hole 85a is formed on the outer peripheral surface between the ninth land portion 97a and the tenth land portion 97b adjacent thereto. Further, an eleventh groove groove 98c always communicating with the second communication hole 85b is formed on the outer peripheral surface between the tenth land portion 97b and the eleventh land portion 97c adjacent thereto.

Further, a twelfth groove groove 98d appropriately communicated with the third communication hole 85c of the second spool valve 63 is formed on the outer peripheral surface between the eleventh land portion 97c and the twelfth land portion 97d adjacent thereto. ing. Further, on the outer peripheral surface between the twelfth land portion 97d and the thirteenth land portion 97e adjacent thereto, a thirteenth groove groove 98e appropriately communicated with the fourth and fifth communication holes 85d and 85e is formed. There is.

Further, a fourteenth groove groove 98f appropriately communicated with the fifth and sixth communication holes 85e and 85f is formed on an outer peripheral surface between the thirteenth land portion 97e and a fourteenth land portion 97f adjacent thereto. There is. Further, a fifteenth groove groove 98g appropriately communicated with the seventh communication hole 85g is formed on an outer peripheral surface between the fourteenth land portion 97f and a fifteenth land portion 97g adjacent thereto.

A sixteenth groove groove 98h always communicating with the eighth communication hole 85h is formed on the outer peripheral surface between the fifteenth land portion 97g and the guide portion 96 adjacent thereto.

In the tenth and eleventh groove grooves 98b and 98c, ninth and tenth communication holes 99a and 99b constantly communicating with the second oil passage hole 88 at predetermined positions in the axial direction and circumferential direction of each bottom wall. It penetrates along the radial direction, respectively. Among them, the ninth communication hole 99 a communicates with the opening side of the second oil passage hole 88 relative to the valve seat 93, and the tenth communication hole 99 b communicates with the valve seat of the second oil passage hole 88. The formation position is set to communicate with the partition wall side more than 93.

The twelfth, fifteenth, and sixteenth groove grooves 98d, 98g, and 98h communicate with the first oil passage hole 87 at predetermined positions in the axial direction and circumferential direction of each bottom wall. 13 communication holes 99c to 99e are respectively formed penetrating along the cross radial direction.

The electromagnetic solenoid 67 is, as shown in FIG. 1, a cylindrical solenoid casing 101 coaxially arranged and fixed to the valve body 61 via a bolt or the like on a chain cover (not shown), and the inside of the solenoid casing 101. And an electromagnetic coil 102 to which a control current is output from an electronic controller 107 described later, and a bottomed end fixed to the inner peripheral side of the electromagnetic coil 102. A cylindrical fixed yoke 103, a movable plunger 104 axially slidably provided inside the fixed yoke 103, and a distal end portion of the movable plunger 104 are integrally formed, and the distal end portion 105a is The first biasing force against the spring force of the two-valve spring 64 or the spring force of the first and second valve springs 64 and 66 A drive rod 105 for pressing the blind plug 89 pools valve 65 to the right in FIG. 1, and is mainly comprised.

The solenoid casing 101 is provided with a synthetic resin connector 106 having a terminal 106 a electrically connected to the electronic controller 107 at the rear end side.

In the electronic controller 107, the internal computer uses the current rotational phase of a crank angle sensor (engine speed detection), an air flow meter, an engine water temperature sensor, an engine temperature sensor, a throttle valve opening sensor, and a camshaft 2 not shown. An information signal from various sensors such as a cam angle sensor to be detected is input to detect the current engine operating condition, and as described above, a control pulse current is output to the electromagnetic coil 102 of the electromagnetic switching valve 60. The movement positions of the first and second spool valves 63 and 65 are controlled to selectively switch the ports.
[Position control of spool valve]
In the following, a table showing the relationship between the stroke amount of the first spool valve 65 shown in FIG. 18 and the supply and discharge of hydraulic oil to the respective hydraulic pressure chambers 11, 12 and the first through third pressure receiving chambers 30 through 32 will be described. The position control of the first and second spool valves 63 and 65 will be specifically described with reference to FIGS.

First, the electromagnetic solenoid 67 is not energized from the electronic controller 107, and the first and second spool valves 63 and 65 are configured of the first and second valve springs 64 and 66 as shown in FIG. When the second spool valve 63 is positioned in the maximum left direction by the spring force, that is, the other end surface of the second spool valve 63 is in contact with the other end surface of the second spool valve accommodating chamber 72 and the first spool valve 65 When the other end face is in contact with the other end face of the first spool valve storage chamber 80 (first position), the retardation port 18a is connected to the drain hole 90 for the seventh groove groove 84g and the seventh communication The lock port 20a is connected to the drain port 21a through the hole 85g, the fifteenth groove groove 98g, the twelfth communication hole 99d, and the first oil passage hole 87. The groove groove 84a, the first communication hole 85a, the ninth groove groove 98a, the first spool valve storage chamber 80, the through hole 81c of the lid member 81, and the second spool valve storage chamber 72 communicate with each other.

At this time, the advance port 19a is configured not to communicate with any port by closing the fourth communication hole 85d by the twelfth land portion 97d.

Therefore, in the first position, as shown in FIG. 18, after the hydraulic oil in the retardation hydraulic chamber 11 flows from the retardation oil passage 11a into the retardation port 18a of the electromagnetic switching valve 60, The hydraulic oil is discharged from the drain holes 90 to the oil pan 44 through the second drain passage 43, and the hydraulic oil in the first to third pressure receiving chambers 30 to 32 for release is the first to third, respectively. After flowing into the lock port 20a from the branch passages 30a, 30b, 30c, the oil is discharged from the drain port 21a to the oil pan 44 via the first drain passage 42 as well.

On the other hand, the hydraulic oil in the advance hydraulic chamber 12 is held in the advance hydraulic chamber 12 as the advance port 19a is closed.

However, at this first position, as shown by the solid line in FIG. 1, since the supply of hydraulic pressure to each of the passage control mechanisms 50 is stopped, the retard hydraulic chamber 11 and the advance hydraulic chamber 12 A communication state is established through the annular grooves 52e (the communication holes 51). For this reason, after the hydraulic oil of the advance hydraulic chamber 12 also flows into the retard hydraulic chamber 11 in practice, it is discharged to the oil pan 44 through the same path as the hydraulic oil in the retard hydraulic chamber 11. It is supposed to be

Next, as shown in FIG. 12, when the first spool valve 65 is energized from the electronic controller 107 to the electromagnetic solenoid 67, it slightly resists the spring force of the first valve spring 66 and moves to the right. When it moves and is not in contact with one end surface or the other end surface of the first spool valve storage chamber 80 (second position), the communication between the lock port 20a and the drain port 21a is maintained, The retardation port 18a is interrupted in communication with the drain hole 90, and the fifth groove groove 84e, the fifth communication hole 85e, the fourteenth groove groove 98f, and the sixth with respect to the second reintroduction port 73c. Communication is made via the communication hole 85 f and the sixth groove groove 84 f. At the same time, the advance port 19a also has the fifth groove groove 84e, the fifth communication hole 85e, the thirteenth groove groove 98e, the fourth communication hole 85d, and the fourth groove groove with respect to the second reintroduction port 73c. Communication is made via 84d.

Therefore, at the second position, as shown in FIG. 18, the discharge state of the hydraulic oil of the first to third pressure receiving chambers 30 to 32 is maintained, while the hydraulic oil discharged from the oil pump 45 is After being introduced to the introduction port 69 of the electromagnetic switching valve 60 through the discharge passage 41b and the hydraulic pressure introduction chamber 6d, the second re-introduction port 73c is connected to the retarding and advancing ports 18a and 19a, respectively. The retard and advance hydraulic pressure chambers 11, 12 are supplied.

The first spool valve 65 is further moved slightly to the right by large energization of the electromagnetic solenoid 67 as shown in FIG. 13 and abuts on one end surface of the first spool valve storage chamber 80. In the case (third position), the communication of the retardation and advance ports 18a and 19a with the second reintroduction port 73c is maintained, and the lock port 20a is shut off from the drain port 21a. The second groove groove 84b, the second communication hole 85b, the eleventh groove groove 98c, the tenth communication hole 99b, the second oil passage hole 88, and the first communication hole 85a with respect to the first reintroduction port 73b. And the first groove groove 84a.

Accordingly, at the third position, as shown in FIG. 18, the supply of hydraulic oil to the retarded and advancing hydraulic pressure chambers 11 and 12 is maintained, and the oil is discharged from the oil pump 45 and the first reintroduction is provided. The hydraulic oil having flowed into the port 73b is supplied from the lock port 20a to the release pressure receiving chambers 30 to 32 through the first to third branch passages 30a, 31a, 32a.

When the first spool valve 65 moves slightly further to the right as shown in FIG. 14, the second spool valve 63 is also pressed by the first spool valve 65 and the spring of the second valve spring 64 Move slightly to the right while resisting the force. In this case (fourth position), the communication between the retardation port 18a and the second reintroduction port 73c and the communication between the lock port 20a and the first reintroduction port 73b are maintained, and the advance port 19a is maintained. Is blocked from communicating with the second reintroduction port 73c, while the third groove groove 84c, the third communication hole 85c, the twelfth groove groove 98d, the eleventh communication hole 99c, and the first drain hole 90 with respect to the drain hole 90. (1) It is communicated via an oil passage hole 87.

Therefore, in the fourth position, as shown in FIG. 18, the supply state of the hydraulic oil to the retardation hydraulic chamber 11 and the pressure receiving chambers for release 30 to 32 is maintained, while the operation in the advancing hydraulic chamber 12 is performed. After the oil flows from the advance oil passage 12a to the advance port 19a, the oil is discharged from the drain holes 90 to the oil pan 44 through the second drain passage 43.

When the first and second spool valves 63 and 65 move slightly to the right as shown in FIG. 15 (fifth position), communication between the lock port 20a and the first reintroduction port 73c is performed. The communication between the retarding port 18a and the second reintroduction port 73c and the communication between the advancing port 19a and the drain hole 90 are performed at the relative positions of the second spool valve 63 and the first spool valve 65. It is cut off according to the relationship, and the retardation and advance ports 18a and 19a are closed.

Therefore, at the fifth position, as shown in FIG. 18, the supply state of the hydraulic oil to the release pressure receiving chambers 30 to 32 is maintained, while the hydraulic oil in the retard and advance hydraulic chambers 11 and 12 is maintained. However, with the closing of the retarding and advancing ports 18a and 19a described above, the hydraulic pressure chambers 11 and 12 are held inside.

When the first and second spool valves 63 and 65 move slightly further to the right as shown in FIG. 16 (sixth position), communication between the lock port 20a and the first reintroduction port 73c is performed. While the retard port 18a is in contact with the drain hole 90, the eighth groove groove 84h, the eighth communication hole 85h, the sixteenth groove groove 98h, the thirteenth communication hole 99e, and the first oil passage hole 87. It is connected via. Further, the advance port 19a is communicated with the second reintroduction port 73c through the fifth groove groove 84e.

Accordingly, at the sixth position, as shown in FIG. 18, the supply state of the hydraulic oil to the release pressure receiving chambers 30 to 32 is maintained, and the hydraulic oil in the retard hydraulic chamber 11 is the retard oil. After flowing into the retardation port 18 a from the passage 11 a, the oil is discharged from the drain holes 90 to the oil pan 44 via the second drain passage 43. On the other hand, after the hydraulic oil discharged from the oil pump 45 is introduced into the advance hydraulic pressure chamber 12 via the discharge passage 41b and the hydraulic pressure introduction chamber 6d into the introduction port 69 of the electromagnetic switching valve 60, It is supplied to the advance hydraulic chamber 12 from the second reintroduction port 73 c via the advance port 19 a.

In addition, when the first and second spool valves 63 and 65 move in the maximum right direction (the seventh position) by the maximum energization amount to the electromagnetic solenoid 67 as shown in FIG. While the communication between the port 18a and the drain hole 90 is maintained, the communication between the advance angle port 19a and the second reintroduction port 73c is blocked. The lock port 20a is disconnected from the first reintroduction port 73b, and is communicated with the drain port 21a through the first groove groove 84a.

Therefore, at the seventh position, as shown in FIG. 18, the hydraulic fluid in the retarding hydraulic pressure chamber 11 and the hydraulic fluid in each of the pressure receiving chambers 30 to 32 for release are respectively the first and second drain passages 42, While the oil is discharged to the oil pan 44 through 43, the hydraulic oil of the advance hydraulic chamber 12 is held in the advance hydraulic chamber 12.

That is, although the path through which the hydraulic oil flows is different, the communication state is the same as the first position described above.

The hydraulic oil in the advance hydraulic chamber 12 communicates with the retard hydraulic chamber 11 through the annular grooves 52e (the communication holes 51) of the passage control mechanism 50. It is the same as 1 position. Therefore, the hydraulic oil of the advance hydraulic chamber 12 is also discharged to the oil pan 44 through the same path as the hydraulic oil of the retard hydraulic chamber 11 as in the case of the first position.

As described above, each port is selectively switched by changing the axial movement position of the first and second spool valves 63 and 65 in accordance with the engine operating condition, and the vane rotor 9 with respect to the sprocket 1 is The relative rotation angle is changed, and the locking and unlocking of the lock pins 27 to 29 to the lock holes 24 to 26 is selectively performed to allow and restrict free rotation of the vane rotor 9. There is.

[Operation of this embodiment]
Hereinafter, the specific operation of the valve timing control device of the present embodiment will be described.

First, when the engine is stopped by turning off the ignition switch after the vehicle normally travels, the driving of the oil pump 45 is also stopped. Supply of hydraulic fluid to 32 to 32 is stopped.

When the working oil pressure is supplied to the respective retarding oil pressure chambers 11 and the vane rotor 9 is at the advancing side rotation position during idling rotation before the engine stop, if the ignition switch is turned off, A positive and negative alternating torque acting on the camshaft 2 is generated immediately before the engine stops. In particular, when the vane rotor 9 is rotated from the retard side to the advance side by the negative torque to be in the intermediate phase position, as shown in FIG. 10, the respective lock pins 27 to 29 are springs of the respective springs 36 to 38. The distal end portions 27a, 28a and 29a engage with the corresponding lock holes 24 to 26, respectively. Thus, the vane rotor 9 is held at an intermediate phase position between the most advanced angle and the most retarded angle shown in FIG.

That is, when the vane rotor 9 located in FIG. 5 slightly rotates on the advance side (in the direction of the arrow in FIG. 5) by the negative alternating torque acting on the camshaft 2, at this time, The output of the pulse current is stopped, and the supply of the hydraulic pressure to each of the release pressure receiving chambers 30 to 32 is stopped.

Therefore, as shown in FIG. 5, the tip portions 27a and 28a of the first and second lock pins 27 and 28 resiliently contact the inner surface 1d of the sprocket by the biasing force of the first and second springs 36 and 37. The distal end portion 29a of the third lock pin 29 slides on the advance side in the above state, and the first bottom surface of the third lock hole 26 is moved by the biasing force of the third spring 38, as shown in FIG. Engage and abut on 26a. Here, although positive alternating torque acts on the vane rotor 9 and tries to rotate to the retard side, the side edge of the tip portion 29a of the third lock pin 29 contacts the rising step surface of the first bottom surface 26a. The rotation to the retard side (in the direction of the arrow in FIG. 6) is restricted.

After that, as the vane rotor 9 rotates to the advance side according to the negative torque, the third lock pin 29 moves to move down the stairs sequentially and engages with the second bottom surface 26b as shown in FIG. It abuts, and moves to the intermediate position on the second bottom surface 26b while receiving a ratcheting action in the advancing direction.

Then, the tip end portion 28a of the second lock pin 28 abuts and engages with the first bottom surface 25a of the second lock hole 25 by the biasing force of the second spring 37, as shown in FIG. . Thereafter, when the vane rotor 9 further rotates to the advancing side, the third lock pin 29 moves to the vicinity of the inner edge 26c and the second lock pin 28 of the second lock hole 25 as shown in FIG. The second bottom surface 25b is in contact and engaged while receiving a ratcheting action.

Further, when the vane rotor 9 is further advanced to the advancing side by the negative torque, as shown in FIG. 10, the first lock pin is moved with the movement of the second and third lock pins 28 and 29 in the same direction. 27 is engaged with the first lock hole 24 and held between the opposed inner edges 24b, 25c of the respective lock holes 24, 25 by the first lock pin 27 and the second lock pin 28 as described above. Arranged as. As a result, as shown in FIG. 3, the vane rotor 9 is stably and reliably held at an intermediate position between the most retarded angle and the most advanced angle.

Also, when the engine is stopped by turning off the ignition switch after the vehicle normally travels, the energization of the electromagnetic switching valve 60 is also cut off, so the first and second spool valves 63 and 65 As shown in FIG. 11, the spring force of the first and second valve springs 64 and 66 holds the first position described above. As a result, the retarding port 18a and the second drain passage 43 are communicated with each other, and the lock port 20a and the first drain passage 42 are communicated with each other, so that the retarding hydraulic pressure chamber 11 and the pressure receiving chambers 30 to 30 The hydraulic oil in 32 is discharged to the oil pan 44 through the drain passages 42 and 43, respectively.

At this time, although the advance port 19a is in the closed state as shown in FIG. 18, the hydraulic oil in the advance hydraulic chamber 12 is also the same as the retard hydraulic chamber 11 as in the retard hydraulic chamber 11. It is discharged to the oil pan 44 via the passage control mechanism 50.

That is, since the supply of the hydraulic pressure from the lock port 20a to each passage control mechanism 50 is also stopped in a state where the electromagnetic switching valve 60 is not energized, each valve body 52 is a solid line in FIG. As shown in FIG. 5, the spring force of each spring 53 causes the head to move to the right. Therefore, on the side of each passage control mechanism 50, the retard side oil hole 11a and the advance side oil hole 12a are in communication with each other through the annular grooves 52e (the communication holes 51).

Therefore, the hydraulic oil in each advance angle hydraulic chamber 12 is made to flow in substitution to the respective retard side oil holes 11a via the respective advance angle oil holes 12a and the respective annular grooves 52e, and from here the second It is possible to lead to the drain passage 43. As a result, the vane rotor 9 can be rotationally moved without being affected by the hydraulic pressure of each of the hydraulic pressure chambers 11, 12, so that the amount of fluttering can be increased and the aforementioned ratcheting action can be sufficiently exhibited.

Thereafter, when the ignition switch is turned on to start the engine, the oil pump 45 is driven by the first explosion (cranking start) immediately thereafter, but the oil pressure discharged by the oil pump 45 is unstable during idling operation The first position of the first and second spool valves 63 and 65 is maintained without energization of the electromagnetic switching valve 60.

Subsequently, for example, before shifting to the engine low rotation low load region or the high rotation high load region, a control current is outputted from the electronic controller 107 to the electromagnetic switching valve 60, and the first spool valve 65 As shown in FIG. 12, it moves slightly in the other direction against the spring force of the first valve spring 66 (second position). As a result, hydraulic oil (hydraulic pressure) is supplied to the retarding and advancing hydraulic chambers 11 and 12 and preparation for releasing the lock state between the lock pins 27 to 29 and the lock holes 24 to 26 is made. Complete.

Subsequently, for example, immediately before the transition to the low engine speed low load area or the high engine speed high load area, a larger control current is output to the electromagnetic switching valve 60, and the first spool valve 65 is shown in FIG. Thus, it moves further to the right against the spring force of the first valve spring 66 (third position). Then, since the hydraulic oil (hydraulic pressure) is supplied to the first to third pressure receiving chambers 30 to 32 for release, the lock pins 27 to 29 are retracted against the spring force of the springs 36 to 38. The distal end portions 27a-29a move out of the lock holes 24-26. By this, the respective engagements are released, and free and reverse rotation of the vane rotor 9 is permitted.

At this time, since the hydraulic pressure is supplied to both the hydraulic pressure chambers 11 and 12 at the second position to prepare for release, the biting phenomenon to the lock holes 24 to 26 of the lock pins 27 to 29, the flapping, etc. Can be suppressed.

Thereafter, for example, in the case of transition to a low engine speed low load region, a larger control current is output to the electromagnetic switching valve 60, and as shown in FIG. 14, the first spool valve 65 is the first valve spring. The second spool valve 63 resists the spring force of the second valve spring 64 by being moved further to the right against the spring force of 66 and being pressed by one end of the first spool valve 65. Move slightly to the right (fourth position). As a result, the lock pins 27-29 are maintained in the state of being pulled out of the lock holes 24-26. Further, the vane rotor 9 has a low pressure as the advance hydraulic chambers 12 are discharged as the hydraulic pressure is discharged, while the retard hydraulic chambers 11 become relatively high pressure. Rotate to the corner side. Therefore, the camshaft 2 is converted into a relative rotational phase of the most retarded angle with respect to the sprocket 1 as shown by the arrow in FIG.

Therefore, the valve overlap between the intake valve and the exhaust valve is reduced, the residual gas in the cylinder is reduced, the combustion efficiency is improved, and the engine rotation can be stabilized and the fuel consumption can be improved.

After that, for example, in the case of transition to the high engine speed high load region, a larger control current is supplied to the electromagnetic switching valve 60, and the first and second spool valves 63 and 65 become large as shown in FIG. Move to the right (6th position). As a result, the engagement between the lock pins 27 to 29 is released, and the retard hydraulic chamber 11 has a low pressure, while the advance hydraulic chamber 12 has a high pressure. Therefore, the vane rotor 9 rotates to the most advanced side with respect to the housing 7. Therefore, the camshaft 2 is converted to the relative rotational phase of the most advanced angle with respect to the sprocket 1 as shown by the arrow in FIG.

Therefore, the valve overlap between the intake valve and the exhaust valve is increased, the intake charging efficiency is increased, and the output torque of the engine can be improved.

Further, in a state where the oil pressure is supplied to the lock port 20a from the discharge passage 41b, the oil pressure acts on the pressure receiving surface 52f of the valve portion 52b of each valve body 52 of each passage control mechanism 50, The body 52 moves leftward against the spring force of each of the springs 53, as indicated by the one-dot chain line in FIG. Therefore, the valve portion 52b closes the advance side oil hole 12a to shut off the communication with the retard side oil hole 11a. Therefore, there is no substitution flow of hydraulic fluid between the retardation hydraulic chamber 11 and the advance hydraulic chamber 12. For this reason, the vane rotor 9 is relatively rotated to the retard side or the advance side promptly by the hydraulic pressure to one of the hydraulic chambers 11 and 12.

Further, when transitioning to idling from the low engine speed low load area or the high engine speed high load area, the control current from the electronic controller 107 to the electromagnetic switching valve 60 is de-energized, and the first, the first and the second The two spool valves 63 and 65 are respectively moved in the maximum left direction by the spring force of the first and second valve springs 64 and 66 and controlled to the first position described above.

Therefore, even when the vane rotor 9 is at the retarded position, the vane rotor 9 rotates to the advancing side by the alternating torque acting on the camshaft 2 as described above. As a result, the lock pins 27 to 29 move forward by the spring force of the springs 36 to 38 and engage with the lock holes 24 to 26 while obtaining the above-mentioned ratchet action. Therefore, the vane rotor 9 is locked at an intermediate phase position between the most advanced angle and the most retarded angle shown in FIG.

Further, even when the engine is stopped, as described above, when the ignition switch is turned off, the lock pins 27 to 29 maintain the engaged state without coming out of the lock holes 24 to 26.

Furthermore, when the predetermined operation range is continued, the electromagnetic switching valve 60 is energized, and as shown in FIG. 15, the first and second spool valves 63 and 65 are in the fourth position and the sixth position. Move to the axial position between the positions (5th position). As a result, the hydraulic oil is held in the retarding hydraulic chambers 11 and the advancing hydraulic chambers 12, respectively, and the lock pins 27 to 29 are disengaged from the lock holes 24 to 26, respectively. It is maintained in the unlocked state.

Therefore, since the vane rotor 9 is held at a desired rotational position and the camshaft 2 is also held at a desired relative rotational position with respect to the housing 7, the intake valve is held at a predetermined valve timing.

Thus, according to the operating state of the engine, the electronic controller 107 controls the movement of the respective spool valves 63 and 65 in the axial direction by deenergizing or de-energizing the electromagnetic switching valve 60 with a predetermined amount of energization. Control to the predetermined position position. As a result, since the phase change mechanism, 3 and the lock mechanism 4 are controlled to control to the optimum relative rotational position of the camshaft 2 with respect to the sprocket 1, the control accuracy of the valve timing can be improved.

Furthermore, while the first and second spool valves 63 and 65 of the electromagnetic switching valve 60 energized in the electronic controller 107 are moved in the axial direction, contamination such as metal powder mixed in the hydraulic oil is the lands. If it is locked by locking between the port and the hole edge of each port, etc. and the flow path can not be switched, the following operation is performed.

That is, when the rotation phase control of the vane rotor 9 can not be performed due to the immovable state of the first and second spool valves 63 and 65, the electronic controller 107 detects this abnormal state from the rotational position of the camshaft 2. The control current of the maximum energization amount is output to the electromagnetic solenoid 67 of the electromagnetic switching valve 60.

Then, as shown in FIG. 17, the first and second spool valves 63 and 65 cut the contamination with a strong pressing force or move to the maximum position in the right direction while releasing the biting ( 7th position). Thus, the immovable state of the first and second spool valves 63 and 65 can be forcibly released.

Further, in the present embodiment, the two functions of the hydraulic pressure control of the hydraulic pressure chambers 11 and 12 and the hydraulic pressure control of the pressure release chambers 30 to 32 are performed by the single electromagnetic switching valve 60.

That is, the second spool valve 63 and the first spool valve 65 are coaxially arranged, and the second spool valve 63 is interlocked according to the axial movement position of the first spool valve 65 to move in the axial direction. By moving, the axial position of both the spool valves 63 and 65 is collectively controlled by the single electromagnetic solenoid 67 so that the two functions can be obtained.

As a result, the device can be miniaturized as compared with an electromagnetic switching valve which requires separate electromagnetic solenoids for position control of the first and second spool valves 63 and 65. Further, since it is not necessary to control the first and second spool valves 63 and 65 by cooperation of a plurality of electronic controllers, it is possible to simplify the control.

Moreover, in the present embodiment, since the first spool valve 65 is accommodated and disposed in the first spool valve accommodating chamber 80 inside the second spool valve 63, both the spool valves 63 and 65 are disposed in series. Since the axial width of the electromagnetic switching valve 60 can be shortened compared to the case where the valve switching control valve 60 is used, the axial length of the valve timing control device can be shortened, and the freedom of layout is improved.

Further, since the axial position of the second spool valve 63 can be controlled only by the contact between the one end portion (the lid member 81) of the second spool valve 63 and the one end side of the first spool valve 65, the electromagnetic The structure of the switching valve 60 can be simplified.

In addition, since the partition wall 86 that divides the internal space of the first spool valve 65 in the axial direction is integrally formed with the first spool valve 65, the number of parts can be reduced. Furthermore, in the present embodiment, since the remaining portion of the first spool valve 65 at the time of drilling is used as the partition 86, there is no need to newly process the partition 86, so the work process is simplified. Can be implemented.

Furthermore, since the check valve 92 is provided in the second oil passage hole 88 used for supplying and discharging the hydraulic oil to each lock port 20a of the first spool valve 65, the operation that has flowed into each lock port 20a It is possible to prevent the backflow of oil to the second reintroduction port 73c. As a result, the hydraulic pressure supplied into the release pressure receiving chambers 30 to 32 can be kept high, so that the unlocking operation can be performed more reliably. Further, since the pulsation of the hydraulic oil introduced into each lock port 20a is suppressed by the check valve 92, the vibration of each lock pin 27 to 29 accompanying the pulsation is reduced, so that each lock The biting phenomenon and the like of the pins 27 to 29 into the lock holes 24 to 26 can be suppressed.
Second Embodiment
The basic configuration of the second embodiment of the present invention shown in FIG. 19 is the same as that of the first embodiment, but the first spool valve 65 is divided into two in the axial direction at the partition 86. It is comprised by two cylindrical 1st spool valve structure parts 65A and 65B. That is, the first spool valve 65 in this embodiment is integrated by axially butting the bottom walls 86a and 86b of the two first spool valve components 65A and 65B from each other. The first spool valve components 65A and 65B may be in contact with the bottom walls 86a and 86b without being integrated.

Therefore, also according to this embodiment, it is possible to obtain the same effects as those of the first embodiment.

In this embodiment, the first spool valve components 65A and 65B are described as being cylindrical with a bottom, but one of them may be cylindrical without a bottom wall. In this case, the partition 86 is constituted only by the other bottom wall.
Third Embodiment
The basic configuration of the third embodiment of the present invention shown in FIG. 20 is the same as that of the first embodiment, but a partition is provided separately from the first spool valve 65.

That is, in the first spool valve 65 in this embodiment, a through hole is formed along the axial direction by drilling or the like, and a wedge-shaped press-fit plug 108, which is a partition, is formed on the inner peripheral surface of the through hole. The internal space is divided in the axial direction by press-fitting.

Therefore, according to this embodiment, it goes without saying that the same function and effect as the first embodiment can be obtained, but when drilling the first spool valve 65, it is necessary to process it from both axial end sides There is no need for processing, and only one side of the process is required, so the number of processes can be reduced.
Fourth Embodiment
In the fourth embodiment of the present invention shown in FIG. 21, the electromagnetic switching valve 60 constituting the hydraulic circuit 5 is provided separately without being directly incorporated into the valve timing control device.

That is, the electromagnetic switching valve 60 in this embodiment is a 6-port, 7-position proportional valve, and has a substantially cylindrical valve body 61 and a cylinder slidably provided in the valve body 61 in the axial direction. -Shaped second spool valve 63, a second valve spring 64 provided on one end side inside the valve body 61 and biasing the second spool valve 63 in the left direction in the figure, and the second spool valve A cylindrical first spool valve 65 slidably provided in the axial direction 63 and an inner one end side of the second spool valve 63 are provided in the left direction in the figure of the first spool valve 65. The first valve spring 66 for urging the valve body 61 and the other end of the valve body 61 are provided, and the first and second spool valves 63 and 65 are controlled according to the operating condition etc. 64, 66 springs An electromagnetic solenoid 67 that is an actuator for moving to the right in the drawing against, and is mainly comprised.

Hereinafter, although each component of the electromagnetic switching valve 60 in this embodiment is demonstrated, description is abbreviate | omitted about the structure similar to 1st Embodiment, and only a different point is demonstrated.

Unlike the first embodiment, the valve body 61 does not have a function as a cam bolt, and is provided in the engine while being caulked and fixed to the claw portion 101 a provided on the solenoid casing 101 of the electromagnetic solenoid 67. It is housed and fixed in the outer valve housing hole.

Further, the check valve chamber 71 at one end side of the retainer 70 is eliminated from the valve body 61, and the introduction port 69, the outlet port 73a and the check valve 74 are eliminated accordingly.

Furthermore, in the valve body 61, the first and second reintroduction ports 73b and 73c are eliminated, and the two reintroduction ports 73b and 73c are provided at the positions where the two reintroduction ports 73b and 73c were provided. The first and second introduction ports 109a and 109b having substantially the same shape are formed. The hydraulic oil is directly supplied from the discharge passage 41b to both the introduction ports 109a and 109b. In addition, the check valve 74 removed from the valve body 61 is disposed in the discharge passage 41b, and the backflow at the time of introducing the hydraulic oil to the first and second introduction ports 109a and 109b is suppressed. It is supposed to be.

Further, in the valve body 61, four second drain ports 110 are formed in a penetrating manner along the cruciform radial direction on the tip end side of the retardation port 18a of the peripheral wall. The second drain port 110 is connected to the oil pan 44 via the second drain passage 43.

In the second spool valve 63, four fourteenth communication holes 85i are formed at predetermined positions in the axial direction of the guide portion 82 along the cruciform radial direction.

On the other hand, in the first spool valve 65, four fifteenth communication holes 99f are formed through at predetermined positions in the axial direction of the guide portion 96 along the cross radial direction.

The 14th communication holes 85i and the 15th communication holes 99f are always in communication with each other through groove grooves formed on the outer periphery of the 15th communication holes 99f. It always communicates with the second drain port 110 via a groove formed on the outer periphery.

Thus, the first oil passage hole 87 in the first spool valve 65 is always in communication with the oil pan 44 through the fourteenth and fifteenth communication holes 85i and 99f and the second drain port 110. There is.

The hydraulic circuit 5 supplies and removes hydraulic pressure to the respective retard hydraulic chambers 11 via the respective retard side oil holes 11 a, and the respective advance hydraulic chambers 12. Advance passage 19 for supplying and discharging hydraulic pressure through the advance side oil holes 12a, and the first through third pressure receiving chambers 30 through 32 through the branch passages 30a, 31a, 32a. And lock passages 20 for supplying and discharging hydraulic pressure, respectively.

One end side of each of the retardation passage 18 and the advancing passage 19 is connected to the retardation port 18a and the advancing port 19a of the electromagnetic switching valve 60, and the other end is the retardation. It is connected to the side and advance side oil holes 11a and 12a.

One end of the lock passage 20 is connected to each lock port 20a of the electromagnetic switching valve 60, and the other end is connected to the branch passages 30a, 31a and 32a.

Therefore, also according to this embodiment, since the electromagnetic switching valve 60 can perform the same position control as that of the first embodiment, it is possible to obtain the same function and effect as that of the first embodiment.

The present invention is not limited to the configuration of each of the above-described embodiments, and the configuration can be changed without departing from the scope of the invention.

For example, in each of the above embodiments, the valve timing control device is applied to the intake side, but it is also possible to apply this to the exhaust side.

In each of the above embodiments, the first spool valve 65 has been described as being formed smaller in diameter than the second spool valve 63 and housed inside the second spool valve 63, both 63, The shape and arrangement relationship of 65 is not limited to this, For example, while forming the said 1st, 2nd spool valve 63 and 65 in the shape of the substantially same diameter, arrange | positioning in series, the one end part of one spool valve The two 63, 65 may be interlocked by bringing the other end of the other spool valve into contact with the other.

Also in this case, since the position control of the first and second spool valves 63 and 65 can be performed by the single electromagnetic solenoid 67, simplification of control and device as compared with the configuration having a plurality of electromagnetic solenoids Miniaturization can be achieved.

As a hydraulic control valve based on the embodiment described above and a valve timing control device for an internal combustion engine using the hydraulic control valve, for example, those of the aspect described below can be considered.

The hydraulic control valve, in one aspect thereof, is provided movably in the axial direction in a hollow valve body in which a plurality of ports through which hydraulic fluid flows in the radial direction of the peripheral wall are formed, A first spool valve that switches the communication state of hydraulic fluid to the plurality of ports according to the movement position, and coaxially disposed with the first spool valve, according to the movement position of the first spool valve in the axial direction And a second spool valve configured to move in the axial direction inside the valve body in conjunction with the first spool valve and to switch the communication state of the hydraulic fluid to the plurality of ports.

In a preferred aspect of the hydraulic control valve, the second spool valve is formed in a hollow shape, and the first spool valve is movably disposed inside the second spool valve.

In another preferable aspect, in any of the aspects of the hydraulic control valve, in the second spool valve, one axial end side of the first spool valve is in contact with one axial side end of the second spool valve. Operate at

In still another preferred aspect, in any of the aspects of the hydraulic control valve, the other end side of the first spool valve in the axial direction is in contact with the other end side in the axial direction of the second spool valve. The first position in contact, the second position in which both axial ends of the first spool valve are separated from both the axial one end and the other end of the second spool valve, and the axial direction of the first spool valve The one end side has the 3rd position contact | abutted to the axial direction one end side of this 2nd spool valve.

In still another preferred aspect, in any of the aspects of the hydraulic control valve, the first spool valve is hollow and the internal space is divided by a partition provided at an intermediate position in the internal axial direction. It is done.

In still another preferred aspect, in any of the aspects of the hydraulic control valve, the partition wall is integrally formed with the first spool valve.

In still another preferred aspect, in any of the aspects of the hydraulic control valve, the first spool valve is axially divided by the partition wall.

In still another preferred aspect, in any of the aspects of the hydraulic control valve, the partition wall is formed of a separate member.

Also, from another point of view, the hydraulic control valve is a hydraulic control valve used in a valve timing control device for an internal combustion engine that operates the movable member by supplying and discharging hydraulic oil to control the relative rotational phase of the camshaft with respect to the crankshaft. A hollow cam bolt in which the movable member is axially fixed to the end portion of the camshaft and through which a supply / discharge port for making the hydraulic oil flow in the radial direction of the peripheral wall is penetrated; A first spool valve movably provided to switch the communication state of the hydraulic fluid to the supply / discharge port according to the movement position, and coaxially disposed with the first spool valve, the axial direction of the first spool valve In accordance with the first spool valve, and moves axially inside the cam bolt to communicate the hydraulic fluid to the supply / discharge port. A second spool valve changing Ri, and a.

In a preferred aspect of the hydraulic control valve, the hydraulic control valve is disposed and fixed along the axial direction on the outer peripheral surface of the cam bolt, and is formed penetrating in the radial direction of the peripheral wall to communicate with the supply and discharge port An internal hollow sleeve is formed in the axial direction of the inner peripheral surface and has a communication hole communicating with any of the supply and discharge ports, and the second spool valve is hollow and the second spool is formed. The first spool valve is movably disposed inside the valve.

In another preferred aspect, in any of the aspects of the hydraulic control valve, an introduction port for introducing the hydraulic oil is formed at an axial tip end of the cam bolt.

In still another preferred aspect, in any of the aspects of the hydraulic control valve, the first spool valve is formed in a hollow shape, and an internal space portion is divided by a partition provided at an intermediate position in the inner axial direction. And a check valve is provided on one end side in the axial direction of the partition wall of the space portion.

In one aspect of a valve timing control device for an internal combustion engine, a driving rotating body to which a rotational force is transmitted from a crankshaft and in which an operating chamber is formed;
It is fixed to one axial end of a camshaft and rotatably accommodated in the drive rotor to separate the working chamber into an advancing working chamber and a retarding working chamber, and to the working fluid for both working chambers The supply and discharge of the hydraulic fluid restricts the relative rotation of the driven rotor relative to the drive rotor and the driven rotor relative to the drive rotor relative to the drive rotor, and the relative rotation of the driven rotor relative to the drive rotor. A lock mechanism for releasing the oil pressure, an oil pressure control valve for controlling supply and discharge of hydraulic oil pumped from an oil pump to both operation chambers, and an actuator provided outside the camshaft to operate the oil pressure control valve; The hydraulic control valve advances the hydraulic fluid to fix the driven rotating body to the end of the camshaft from the axial direction and circulate the hydraulic fluid in the radial direction of the peripheral wall to the advance operating chamber and the retarding operating chamber. Port and Retard And a cylindrical cam bolt in which a lock port for letting the hydraulic oil flow through the lock mechanism is formed so as to be axially movable inside the cam bolt, and the advance port or the like according to the movement position A first spool valve that switches the communication state of hydraulic fluid to the retard port and the lock port, and the first spool valve is disposed coaxially with the first spool valve, and the first spool valve moves according to the axial movement position of the first spool valve. And a second spool valve which moves axially inside the cam bolt and switches the communication state of hydraulic fluid to the advance port, the retard port and the lock port.

In a preferable aspect of the valve timing control device of the internal combustion engine, the first spool valve and the second spool valve are each formed in a hollow shape, and the first spool valve is an inside of the second spool valve. A partition is disposed movably at a middle position in the inner axial direction and axially divides an inner space portion.

In another preferable aspect, in any of the aspects of the valve timing control device of the internal combustion engine, one axial end side of the first spool valve across the partition wall communicates and shuts off hydraulic oil to the lock port. The other axial end of the first spool valve is provided for communication and blocking of hydraulic fluid to and from the advance port and the retard port.

In still another preferable aspect, in any of the aspects of the valve timing control device of the internal combustion engine, a check valve is disposed in an internal space portion on one axial end side of the partition wall of the first spool valve. The backflow of the hydraulic oil from the lock port is suppressed.

Claims (16)

1. A hollow valve body in which a plurality of ports through which hydraulic fluid flows in the radial direction of the peripheral wall are formed;
   A first spool valve provided so as to be axially movable inside the valve body, and switching a communication state of hydraulic fluid to the plurality of ports according to a movement position;
   The first spool valve is coaxially disposed, and is axially moved inside the valve body in conjunction with the first spool valve in accordance with the axial movement position of the first spool valve; A second spool valve that switches fluid communication with the port of
   The hydraulic control valve characterized by having.
2. In the hydraulic control valve according to claim 1,
   The second spool valve is hollow, and
   The hydraulic control valve according to claim 1, wherein the first spool valve is movably disposed in the second spool valve.
3. In the hydraulic control valve according to claim 2,
   A hydraulic control valve characterized in that the second spool valve is operated in a state where one axial end side of the first spool valve is in contact with one axial side end of the second spool valve.
4. In the hydraulic control valve according to claim 3,
   The first spool valve is
   A first position in which the other axial end of the first spool valve is in contact with the other axial end of the second spool valve;
   A second position in which both axial ends of the first spool valve are separated from both axial one end and the other end of the second spool valve;
   A third position in which one axial end of the first spool valve is in contact with one axial end of the second spool valve;
   Hydraulic control valve characterized by having.
5. In the hydraulic control valve according to claim 4,
   A hydraulic control valve characterized in that the first spool valve is formed in a hollow shape, and an internal space portion is divided by a partition provided at an intermediate position in the inner axial direction.
6. In the hydraulic control valve according to claim 5,
   The hydraulic control valve, wherein the partition wall is integrally formed with the first spool valve.
7. In the hydraulic control valve according to claim 5,
   A hydraulic control valve characterized in that the first spool valve is divided in the axial direction by the partition wall.
8. In the hydraulic control valve according to claim 5,
   The said partition is formed by another member, The hydraulic control valve characterized by the above-mentioned.
9. A hydraulic control valve used in a valve timing control device for an internal combustion engine, which operates a movable member by supplying and discharging hydraulic oil to control the relative rotational phase of a camshaft with respect to a crankshaft,
   A hollow cam bolt in which the movable member is axially fixed to the end portion of the camshaft, and through which a supply and discharge port for making the hydraulic oil flow in the radial direction of the peripheral wall.
   A first spool valve which is axially movably provided inside the cam bolt and switches the communication state of the hydraulic fluid to the supply / discharge port according to the movement position;
   The first spool valve is coaxially disposed, and is axially moved inside the cam bolt in conjunction with the first spool valve in accordance with the axial movement position of the first spool valve, and the supply and discharge A second spool valve that switches hydraulic fluid communication with the port;
   The hydraulic control valve characterized by having.
10. The hydraulic control valve according to claim 9 is
    The cam bolt is disposed and fixed along the axial direction on the outer peripheral surface of the cam bolt, and is formed penetrating in the radial direction of the peripheral wall, and is formed in the axial direction of the communication hole and the inner peripheral surface communicating with the supply and discharge port. And an internal hollow sleeve having a communication hole communicating therewith;
    A hydraulic control valve, wherein the second spool valve is formed in a hollow shape, and the first spool valve is movably disposed in the second spool valve.
11. In the hydraulic control valve according to claim 10,
    An oil pressure control valve characterized in that an introduction port for introducing the hydraulic oil is formed at an axial tip end of the cam bolt.
12. In the hydraulic control valve according to claim 11,
    The first spool valve is formed in a hollow shape, and an inner space portion is divided by a partition provided at an intermediate position in the inner axial direction, and the first spool valve is closer to one end in the axial direction than the partition of the space portion. A hydraulic control valve characterized in that a check valve is provided.
13. A driving rotating body having a working chamber formed therein, to which a rotational force is transmitted from a crankshaft;
    It is fixed to one axial end of a camshaft and rotatably accommodated in the drive rotor to separate the working chamber into an advancing working chamber and a retarding working chamber, and to the working fluid for both working chambers A driven rotor that rotates relative to the drive rotor with respect to the advancing side or the retarding side by supplying and discharging the
    A lock mechanism which regulates or cancels relative rotation of the driven rotary body with respect to the drive rotary body by supply and discharge of hydraulic oil;
    An oil pressure control valve that controls the supply and discharge of hydraulic oil pumped from an oil pump to both working chambers;
    An actuator provided outside the camshaft to operate the hydraulic control valve;
    Equipped with
    The hydraulic control valve is
    An advancing port and a retarding port for fixing the driven rotor to the end of the camshaft from the axial direction and allowing hydraulic fluid to flow through the advancing and actuating chambers in the radial direction of the peripheral wall, and the lock A cylindrical cam bolt in which a lock port is formed to allow hydraulic oil to flow through the mechanism;
    A first spool valve provided so as to be axially movable inside the cam bolt, and switching the communication state of hydraulic fluid to the advance port, the retard port and the lock port according to the movement position;
    The first spool valve is coaxially disposed, and is axially moved inside the cam bolt according to the axial movement position of the first spool valve, and the advance port, the retard port, and the lock A second spool valve that switches hydraulic fluid communication with the port;
    A valve timing control device for an internal combustion engine, comprising:
14. The valve timing control apparatus for an internal combustion engine according to claim 13.
    The first spool valve and the second spool valve are each formed in a hollow shape, and
    The first spool valve is movably disposed inside the second spool valve, and a partition is provided at an intermediate axial position to axially divide an internal space portion. Engine valve timing control device.
15. The valve timing control device for an internal combustion engine according to claim 14.
    One end side of the first spool valve in the axial direction sandwiching the partition wall is provided for communication and blocking of the hydraulic oil with respect to the lock port,
    A valve timing control device for an internal combustion engine, wherein the other end side of the first spool valve in the axial direction is used for communication and interruption of hydraulic fluid to and from the advance port and the retard port.
16. The valve timing control device for an internal combustion engine according to claim 15.
    A check valve is disposed in an internal space at one end side in the axial direction with respect to the partition wall of the first spool valve, and a backflow of hydraulic oil from the lock port is suppressed. Valve timing control system for internal combustion engines.

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