JP6295160B2 - Electromagnetic valve, electromagnetic valve and electromagnetic actuator used for valve timing control device of internal combustion engine - Google Patents

Description

  The present invention relates to, for example, an electromagnetic valve or an electromagnetic actuator used in a valve timing control device that variably controls the valve timing of an intake valve or an exhaust valve of an internal combustion engine according to an operating state.

  Conventionally, various electromagnetic valves have been provided, and one of them is described in Patent Document 1 below.

  Briefly, the electromagnetic valve includes a cup-shaped guide member formed of a non-magnetic material, a magnetic material mover provided in the guide member so as to be slidable in the axial direction, and the guide. A coil that is arranged on the outer peripheral side of the member and generates a magnetic force when energized, and a fixed that attracts the mover in the axial direction by forming a magnetic path with the mover when a magnetic force is generated in the coil And a child.

  The stator includes a cylindrical yoke disposed on the outer peripheral side of the guide member so as to cover the coil, and a suction portion disposed in contact with a front end portion of the yoke to suck the movable element in the axial direction. And an opposing portion that is disposed to face the front end surface in the axial direction of the mover and assists the magnetic force of the suction portion.

JP 2007-182938 A

  However, in the electromagnetic valve described in Patent Document 1, although the sliding property in the axial direction of the mover can be secured by the guide member, it is between the suction portion and the facing portion of the stator. Since the guide member is interposed, that is, the suction portion and the facing portion are separated from each other by the guide member, a magnetic path formed between the suction portion and the facing portion. There is a risk that the magnetic efficiency of the magnetic disk will be lowered.

  It is an object of the present invention to provide an electromagnetic valve and an electromagnetic actuator that can suppress a decrease in magnetic efficiency between a suction portion and a facing portion of a stator while ensuring good slidability of a mover by a guide member. Yes.

According to the first aspect of the present invention, there is provided a cup-shaped guide member formed of a non-magnetic material, a magnetic material mover provided in the guide member so as to be slidable in the axial direction, and an outer periphery of the guide member. A coil that is arranged on the side and generates a magnetic force when energized, and a stator that forms a magnetic path with the movable element when the magnetic force is generated in the coil and attracts the movable element in the axial direction; With
The stator is disposed between the guide member and the coil, and is disposed so as to be opposed to the suction portion that sucks the mover in the axial direction, and the end surface in the axial direction of the mover. And an opposing portion that assists the suction portion, and the suction portion and the opposing portion are provided in contact with each other.

  ADVANTAGE OF THE INVENTION According to this invention, the fall of the magnetic efficiency between the attraction | suction part of a stator and an opposing part can be suppressed, ensuring the favorable slidability of the needle | mover by a guide member.

It is a whole lineblock diagram showing the valve timing control device to which the solenoid valve concerning the present invention is applied. It is a front view which shows the state by which the vane rotor provided to this embodiment was hold | maintained in the rotation position of the intermediate phase. It is a longitudinal cross-sectional view of each component parts, such as a valve body of the solenoid valve provided for this embodiment. It is a perspective view which decomposes | disassembles and shows the valve body and sleeve of the solenoid valve with which this embodiment is provided. It is an expanded sectional view of a solenoid part provided for this embodiment. It is a longitudinal cross-sectional view which decomposes | disassembles and shows the solenoid part. It is a principal part enlarged view of the solenoid part shown in FIG. It is a top view of the valve body provided for this embodiment. 8 is a cross-sectional view taken along line AA in FIG. 8, B is a cross-sectional view taken along line BB in FIG. 8, and C is a cross-sectional view taken along line CC in FIG. It is a right view of the valve body provided to this embodiment. 10 is a longitudinal sectional view on the valve body side showing a state in which the spool valve of the electromagnetic valve provided in the present embodiment has moved to the maximum rightward position, wherein A is a sectional view taken along the line DD in FIG. 10, and B is FIG. It is the EE sectional view taken on the line. 10 is a longitudinal sectional view on the valve body side showing a state in which the spool valve of the electromagnetic valve provided for the present embodiment has moved to an intermediate position in the axial direction, where A is a sectional view taken along the line DD in FIG. 10, and B is a sectional view in FIG. It is the EE sectional view taken on the line. 10 is a longitudinal sectional view on the valve body side showing a state in which the spool valve of the electromagnetic valve provided in the present embodiment has moved to the maximum leftward position, where A is a sectional view taken along the line DD in FIG. 10, and B is a sectional view in FIG. It is the EE sectional view taken on the line.

  Hereinafter, an embodiment in which an electromagnetic valve according to the present invention is applied to a valve timing control device for an internal combustion engine will be described with reference to the drawings.

  As shown in FIGS. 1 and 2, the valve timing control device is arranged along a sprocket 1 that is a driving rotating body that is rotationally driven via a timing chain by a crankshaft outside the engine, and along the longitudinal direction of the engine. And is arranged between the intake side camshaft 2 provided so as to be rotatable relative to the sprocket 1 and between the sprocket 1 and the camshaft 2, and converts the relative rotational phase of the both 1 and 2. A phase changing mechanism 3, a lock mechanism 4 that locks the phase changing mechanism 3 at the most retarded phase position, and a hydraulic circuit 5 that operates the phase changing mechanism 3 and the lock mechanism 4 independently of each other. Yes.

  The sprocket 1 is formed in a substantially thick disk shape, has a gear portion 1a around which the timing chain is wound, and is configured as a rear cover that closes a rear end opening of the housing described later. In the center, a support hole 1b through which the one end 2a of the camshaft 2 is rotatably supported is formed.

  The camshaft 2 is rotatably supported by a cylinder head 01 via a plurality of cam bearings 02, and a plurality of egg-shaped rotary cams for opening an intake valve, which is an unillustrated engine valve, are shafts on the outer peripheral surface. A bolt hole 6 into which a cam bolt 50 to be described later is screwed is formed in the direction of the internal axis of the one end portion 2a.

  The bolt hole 6 is formed along the internal axial direction from the distal end side of the one end portion 2a, and is formed to have a stepped diameter from the opened front end side toward the inner bottom portion. A female threaded portion 6a having a diameter and a stepped portion 6b formed in a tapered shape with a reduced diameter inward from the rear end of the female threaded portion 6a. Yes.

  The step portion 6b is formed therein with a hydraulic pressure introducing chamber 6c that is pumped from an oil pump 20 described later.

  As shown in FIGS. 1 and 2, the phase change mechanism 3 includes a housing 7 that is integrally provided on the sprocket 1 in the axial direction, and a later-described valve body that becomes a cam bolt at one end 2 a of the camshaft 2. A vane rotor 9 which is a driven rotating body fixed in an axial direction through 50 and rotatably accommodated in the housing 7 and an operation chamber inside the housing 7 are arranged on an inner peripheral surface of a housing body 7a described later. There are provided a retarded hydraulic chamber 11 and an advanced hydraulic chamber 12 which are a retarded working chamber and an advanced working chamber, respectively, which are separated by four protruding shoes 10 and the vane rotor 9.

  The housing 7 includes a cylindrical housing body 7a integrally formed of sintered metal, a front cover 13 that is formed by press molding and closes the front end opening of the housing body 7a, and a rear cover that closes the rear end opening. It is comprised from the said sprocket 1 which is. The housing body 7a, the front cover 13, and the sprocket 1 are fastened and fixed together by four bolts 14 that pass through the bolt insertion holes 10a of the shoes 10. The front cover 13 has a relatively large-diameter insertion hole 13a formed through the center thereof, and seals the inside of each hydraulic chamber 11, 12 with the outer peripheral side inner peripheral surface of the insertion hole 13a. .

  The vane rotor 9 is integrally formed of a metal material, and has a rotor portion 15 fixed to one end portion 2a of the camshaft 2 by a valve body 50, and an outer peripheral surface of the rotor portion 15 having a circumferential direction of approximately 90 ° or the like. It consists of four vanes 16a to 16d projecting radially at the interval positions.

  The rotor portion 15 is formed in a relatively large-diameter cylindrical shape, and a bolt insertion hole 15a continuous with the female screw hole 6c of the camshaft 2 is formed through the central shaft in the central direction. The tip end surface of the one end portion 2a of the shaft 2 is in contact.

  On the other hand, each of the vanes 16a to 16d has a relatively short protruding length, and is disposed between the shoes 10 and has a circumferential width that is set to be substantially the same. It is formed in a plate shape. Seal members 17a and 17b for sealing between the inner peripheral surface of the housing body 7a and the outer peripheral surface of the rotor portion 15 are provided on the outer peripheral surfaces of the vanes 16a to 16d and the tips of the shoes 10, respectively. .

  As the vane rotor 9 rotates relative to the retard side as shown by a one-dot chain line in FIG. 2, the projecting surface 10b formed on the opposing side surface of the one shoe 10 that the one side surface of the first vane 16a faces. The rotational position on the maximum retarding angle side is regulated in contact with. In addition, as shown by a two-dot chain line in FIG. 2, when the relative rotation is performed toward the advance angle side, the other side surface of the first vane 16a is in contact with the opposite side surface 10c of the other shoe 10 and the maximum advance angle side rotation is performed. The position is regulated.

  At this time, the other vanes 16b to 16d are in a separated state without coming into contact with the facing surfaces of the shoes 10 whose side surfaces face each other in the circumferential direction. Therefore, the contact accuracy between the vane rotor 9 and the shoe 10 is improved, and the supply speed of hydraulic pressure to each of the hydraulic chambers 11 and 12 to be described later is increased, and the forward / reverse rotation response of the vane rotor 9 is increased.

  The retard hydraulic chambers 11 and the advance hydraulic chambers 12 described above are formed between both side surfaces of the vanes 16a to 16d in the forward and reverse rotation direction and both side surfaces of the shoes 10, respectively. The angle hydraulic chamber 11 and each advance hydraulic chamber 12 are respectively connected to a hydraulic circuit 5 described later via a retard side communication passage 11a and an advance side communication passage 12a formed substantially radially inside the rotor portion 15. Communicating with

  The lock mechanism 4 holds the vane rotor 9 at the rotational position on the most retarded angle side (the one-dot chain line position in FIG. 2) with respect to the housing 7.

  That is, as shown in FIGS. 1 and 2, the lock mechanism 4 includes a lock hole constituting portion 1c (described only in FIG. 1) that is press-fitted and fixed at a predetermined position on the inner peripheral side of the sprocket 1, and the lock hole. A lock hole 24 formed in the component 1c and a sliding hole 27 formed in the inner axial direction of the first vane 16a of the vane rotor 9 are provided to be movable forward and backward, and a small-diameter tip 25a is provided in each lock hole. 24, a coil spring 26 for urging the lock pin 25 toward the lock hole 24, and a lock spring 25 formed inside the lock hole 24. The main body includes a release pressure receiving chamber (not shown) that releases the engagement by retreating the lock holes 24 against the spring force of the coil spring 26, and a lock passage that supplies hydraulic pressure to the release pressure receiving chamber. It is constructed by.

  The lock hole 24 is formed in a circular shape having a diameter sufficiently larger than the outer diameter of the small-diameter tip portion 25a of the lock pin 25, and the rotation of the inner side surface of the sprocket 1 on the most retarded side of the vane rotor 9 is performed. It is formed at a position corresponding to the position.

  The lock pin 25 receives the hydraulic pressure supplied to the release pressure receiving chamber on the pressure receiving surface of the front end portion 25a and moves backward to come out of the lock hole 24 to be unlocked and provided on the rear end side. The tip portion 25 a is engaged with the lock hole 24 by the spring force of the coil spring 26 to lock the vane rotor 9 with respect to the housing 7.

  As shown in FIGS. 1 and 2, the hydraulic circuit 5 includes a retard passage 18 for supplying and exhausting hydraulic pressure to and from each retard hydraulic chamber 11 via a retard communication passage 11a, and each advance hydraulic pressure. An advance passage 19 for supplying and discharging hydraulic pressure to and from the chamber 12 via the advance side communication passage 12a, the lock passage for supplying and discharging hydraulic pressure to and from the release pressure receiving chamber, and the respective retard and advance angles An oil pump 20 that selectively supplies hydraulic oil to the passages 18 and 19, and a single electromagnetic valve 21 that is an electromagnetic valve that switches between the retard passage 18 and the advance passage 19 according to the engine operating state; It is equipped with.

  Each of the retard passage 18 and the advance passage 19 is connected at one end to a retard angle of a sleeve 52, which will be described later, of the solenoid valve 21, and the advance passage holes 64a and 64b, and the other end side is the retard angle. The retard hydraulic chambers 11 and the advance hydraulic chambers 12 communicate with the advance hydraulic chambers 11a and 12a, respectively.

  The lock passage communicates with the retard passage 18 so that the hydraulic pressure supplied to and discharged from the retard hydraulic chamber 11 is supplied to and discharged from the release pressure receiving chamber.

  The oil pump 20 is a general one such as a trochoid pump that is rotationally driven by an engine crankshaft, and hydraulic oil sucked from the oil pan 23 through the suction passage 20b by rotation of the outer and inner rotors. It is discharged through the discharge passage 20a, a part of which 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 valve 21 side. Yes. In addition, a filtration filter (not shown) is provided on the downstream side of the discharge passage 20a, and excess hydraulic oil discharged from the discharge passage 20a is returned to the oil pan 23 through the drain passage 22 to be appropriate. A non-illustrated flow rate control valve for controlling the flow rate is provided.

  As shown in FIGS. 1 and 3, the solenoid valve 21 is a three-port, three-position proportional valve, and is slidable in a cylindrical valve body 50 and the internal axis direction of the valve body 50. A cylindrical spool valve 51 provided; a cylindrical sleeve 52 fixed to the outer peripheral surface of the valve body 50; a drain plug 53 integrally press-fitted to the tip of the spool valve 51; and the drain A valve spring 54, which is an urging member that is urged between the plug 53 and an annular step surface formed inside the valve body 50 to urge the spool valve body 51 in the right direction in FIG. A solenoid portion 55 which is an electromagnetic actuator provided at one end of the valve body 50 and moves the spool valve 51 in the leftward direction against the spring force of the valve spring 54. It is configured.

  The valve body 50 is formed of an iron-based metal material and functions as a cam bolt as described above. As shown in FIGS. 1, 3, and 4, the head 50a on the solenoid unit 55 side, the head 50a, A cylindrical shaft portion 50b extending in the axial direction from the base portion of the portion 50a, and a male screw portion 50d formed on the distal end side of the cylindrical shaft portion 50b and screwed into the female screw hole 6b of the camshaft 2 on the outer peripheral surface. The main portion is mainly composed of the formed large-diameter cylindrical portion 50c and a sliding hole 50e formed in the inner axial direction from the front end surface side of the head portion 50a.

  The head portion 50a is formed with a hexagonal portion into which a tightening jig such as a spanner can be fitted on the outer periphery, and the solenoid portion of the spool valve 51 on the inner peripheral surface of the large-diameter groove portion formed on the inner tip side. An annular stopper 56 for restricting the maximum sliding position toward the 55 side is press-fitted and fixed.

  As shown in FIGS. 9A to 9C, the cylindrical shaft portion 50b is formed on the peripheral wall in order from the male screw portion 50d side to the head portion 50a side, the introduction port 57, the advance port 19a, the reintroduction port 58, and the like. Four retard ports 18a are formed penetratingly along the cruciform direction, and four retard ports 18a are provided. In FIG. 9, the introduction port 57 is not specifically described, but is formed in a cross-radial direction like the other ports.

  Further, as shown in FIG. 3, the cylindrical shaft portion 50b has a positioning hole 50f, which is a fitting hole for positioning the sleeve 52, formed along the radial direction on the outer peripheral surface in the vicinity of the retardation port 18a. ing.

  The large-diameter cylindrical portion 50c is formed therein with an introduction passage 59 communicating with the hydraulic introduction chamber 6c of the camshaft 2 from the axial direction, and the hydraulic pressure pumped from the discharge passage 20a of the oil pump 20 is hydraulically introduced. The introduction passage 59 is supplied to the introduction passage 59 through the chamber 6c. The introduction passage 59 is formed in a stepped diameter, and the introduction ports 57 communicate with the small diameter portion 59a inside.

  As shown in FIG. 3, the spool valve 51 has a drain passage 60 formed therethrough in the inner axial direction, and two cylindrical land portions on one end side in the axial direction on the outer peripheral small diameter portion 59a side. A first land portion 51a and a second land portion 51b, which are (valve portions), are formed. Further, between the land portions 51a and 51b, a groove groove 61 communicates appropriately with each retard port 18a, each advance port 19a and each reintroduction port 58 according to the sliding position of the spool valve 51. In addition, a discharge passage 62 is formed along the axial direction on the outer peripheral surface between the second land portion 51b and the drain plug 53. Further, a drain hole 63 communicating with the discharge passage 62 and the drain passage 60 is formed through the peripheral wall of the spool valve 51 on the side opposite to the land portions 51a and 52b in the radial direction.

  As shown in FIGS. 1 and 3, the drain plug 53 is formed in a substantially bottomed cylindrical shape from the same metal material as the spool valve 51, and extends from the axial direction so as to fit the one end opening 51 c of the spool valve 51. In addition to being press-fitted and fixed, a flange portion 53 a that elastically supports one end portion of the valve spring 54 is integrally provided on the outer periphery of the one end portion on the spool valve 51 side. Further, the drain plug 53 is formed with a drain chamber 66 communicating with the drain passage 60 from the axial direction in the inner axial direction, and a pair of openings communicating with the drain chamber 66 and the outside on the peripheral wall of the tip portion. A hole 66a is formed penetrating along the radial direction.

  The flange portion 53 a abuts against the inner peripheral portion of the stopper 56 from the axial direction, and regulates the maximum outward movement position of the spool valve 51.

  As shown in FIGS. 3 to 4, the sleeve 52 is formed of a synthetic resin material and is divided into two halves from the radial direction, and both the divided portions 52 a and 52 b are formed from the radial direction. For example, they are joined together by welding, for example, and are integrally formed in a cylindrical shape, and the inner peripheral surface is fixed to the outer peripheral surface of the cylindrical shaft portion 50b of the valve body 50 from the outside in a fitted state. Also, the sleeve 52 has a protrusion 52c provided at a substantially central position in the circumferential direction of the divided portion 52a on one side and is fitted into the positioning hole 50f of the cylindrical shaft portion 50b so that the entire sleeve body 52 is in contact with the valve body 50. The positioning in the rotational direction and the axial direction is fixed.

  In addition, it is also possible to join both the said division | segmentation parts 52a and 52b by a snap fit.

  The sleeve 52 is connected to the retard port 18a and the advance port 19a of the valve body 50, that is, at a position overlapped with the retard port 18a and the advance port 19a. 64b is formed so as to penetrate therethrough, and four communication grooves 65 communicating with the four reintroduction ports 58 are formed along the axial direction on the inner peripheral surfaces of the two divided portions 52a and 52b.

  Each communication groove 65c constitutes a communication path between the inner peripheral surface and the outer peripheral surface of the cylindrical shaft portion 50b of the valve body 50, and the large-diameter cylindrical portion 50c of the valve body 50 of each of the divided portions 52a and 52b. The inner end portion 65b extends along the axial direction from the outer end portion 65a on the side and extends to a position where it overlaps the reintroduction port 58, and the outer end portion 65a extends to the introduction port 57. The camshaft 2 is always in communication through a passage portion between the inner peripheral surfaces of the female screw portion 6a of the bolt hole 6 of the camshaft 2.

  As shown in FIGS. 1, 5 and 6, the solenoid portion 55 is a cylindrical solenoid casing 71 which is a stator fixed to a chain cover (not shown) by a bolt through a delivery stator 70 for magnetic delivery. A coil 72 that is housed and held in the solenoid casing 71 and is excited when a control current is output from an engine control unit (ECU) 37, and an insulating material in which the coil 72 is wound and held. A synthetic resin bobbin 73, a guide member 74 disposed on the inner peripheral side of the bobbin 73, integrally formed in a bottomed cylindrical shape, and slidable in the axial direction on the inner peripheral surface of the guide member 74 Between the plunger 75, which is a movable element guided and having the rear end portion of the drive rod 76 fixed to the front end portion, between the solenoid casing 71 and the bobbin 73, two A suction stator 79 that is supported by a ring 77 and 78 and forms a magnetic circuit together with the solenoid casing 71, and is integrally provided at the rear end of the solenoid casing 71. And a connector 80 that electrically connects the ECU 37 to each other via a harness.

  The delivery stator 70 is formed by press-molding a magnetic material, and as shown in FIG. 5, a cylindrical portion 70 a disposed so as to cover the outer periphery of the plunger 75 via the guide member 74, and the cylindrical portion It is comprised from the bracket part 70b extended along the radial direction on the outer periphery of 70a.

  The cylindrical portion 70a is integrally formed with a flange portion 70c bent in the diameter increasing direction at one end portion on the connector 80 side in the axial direction, and the other end portion is substantially in the center in the axial direction of the bobbin 73. It extends to the position.

  The bracket portion 70b has a bolt insertion hole 70e through which a bolt coupled to the chain case is inserted.

  As shown in FIGS. 5 and 6, the solenoid casing 71 is formed into a cup shape by press molding with a magnetic material, and has a large-diameter outer cylinder portion 71a fitted on the outer peripheral surface of the bobbin 73; A flat disk portion 71b bent at a right angle from one axial end portion of the outer cylinder portion 71a, and bent from the inner periphery of the disk portion 71b to the inside, that is, toward the plunger 75, the plunger 75 The inner cylinder part 71c which is a cylindrical opposing part which opposes the front-end surface of this from an axial direction is comprised. The outer cylinder portion 71a and the disc portion 71b constitute a stator main body.

  The outer cylindrical portion 71a is integrally provided with four claw portions 71d that are caulked and fixed to the delivery stator 70 at the other end portion in the axial direction, and is provided at equal intervals in the circumferential direction. A part of the outer end surface 71e is in contact with the inner side surface of the bracket portion 70 of the delivery stator 70 from the axial direction.

  The guide member 74 is formed integrally with a thin wall by a nonmagnetic material such as stainless steel or a hard synthetic resin material, and a bottom wall 74b at one end in the axial direction of the cylindrical main body 74a is formed in a cross-sectional wave shape to form the plunger. An action of suppressing the sticking of the rear end surface 75b of the 75 is exerted, and a flange piece 74c whose diameter is expanded to the one O-ring 78 is integrally formed on the other axial end side.

  The plunger 75 is formed in a substantially cylindrical shape by a magnetic material, and its outer peripheral surface is slidably guided in the axial direction on the inner peripheral surface of the cylindrical main body 74a of the guide member 74, and has an internal axis. A press-fitting hole 75a for press-fitting and fixing the drive rod 76 in the direction is formed therethrough.

  Further, when the plunger 75 is moved back to the maximum by the spring force of the valve spring 54, the rear end surface 75b comes into contact with the wave-shaped bottom wall 74b of the guide member 74, and the contact area is reached by the wave-shaped bottom wall 74b. And the sticking of the rear end surface 75b of the plunger 75 is suppressed.

  The drive rod 76 has a spherical tip surface that abuts against the bottom wall of the drain plug 53 from the axial direction.

  The suction stator 79 is formed into a generally annular shape by press molding, and is bent into a substantially crank shape in longitudinal section. From the inner peripheral side cylindrical portion 79a and the rear end edge of the cylindrical portion 79a. The disk wall 79b is bent in the radial direction, and the large-diameter cylindrical portion 79c is bent outward from the outer peripheral edge of the disk wall 79b in the axial direction.

  The cylindrical portion 79a is formed in a bowl shape so that the outer peripheral surface 79d of the tip portion guides and attracts the magnetism of the disk wall 79b to the vicinity of the plunger 75, and the inner peripheral surface and the outer peripheral surface of the plunger 75 Between the two, a magnetic flux delivery gap (side gap) is formed via the cylindrical main body 74a of the guide member 74.

  The disk portion 79b has one end surface on the outer peripheral side elastically contacting one side outer surface of the bobbin 73 via the O-ring 77, and one side surface of the flange piece 74c of the guide member 74 is formed on the other end surface. In addition, the outer peripheral side of the other end surface is in elastic contact with the inner surface of the disc portion 71b of the solenoid casing 71 via the flange piece 74c and the O-ring 78, and is elastically held between these O-rings 77 and 78. It is held.

  The large-diameter cylindrical portion 79c has an annular outer end surface 79e in contact with the inner surface of the disk portion 71b from the axial direction.

  The connector 80 is internally molded with a synthetic resin material to form terminal pieces 80a made of a conductive metal material such as a copper material. The terminal piece 80a is bent in a substantially L shape, and one end portion 80b is connected to the terminal portion of the coil 72, and the other end portion 80c connected to the ECU 37 is fitted on the other end side. It is exposed from the hole 80d.

  As shown in FIGS. 11 to 13, the solenoid unit 55 moves the spool valve 51 to three positions in the front-rear axial direction by the control current of the ECU 37 and the relative pressure of the valve spring 54. The groove groove 61 and the discharge passage 62 of the spool valve 51 are communicated with the retardation port 18a and the advance port 19a corresponding to the radial direction thereof, or the retardation port 18a is connected to the land portions 51a and 51b. In addition, the open end of the advance port 19a is closed to block communication.

  The introduction passage 59, the introduction port 57, the communication groove 65, and the reintroduction port 58 are always in communication at any sliding position of the spool valve 51. Therefore, the hydraulic pressure discharged from the oil pump 20 is The reintroduction port 58 is always supplied from the introduction passage 59 through the introduction port 57 and the communication groove 65.

In the ECU 37, an internal computer detects 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 current rotation phase of the camshaft 2 which are not shown. Information signals from various sensors such as a cam angle sensor are input to detect the current engine operating state, and as described above, a control current is output to the coil 72 of the electromagnetic valve 21 or the current is cut off. The movement position of the spool valve 51 is controlled to selectively switch the ports.
[Operation of this embodiment]
Hereinafter, specific operations of the electromagnetic valve and the valve timing control device of this embodiment will be described.

  First, for example, when the engine is stopped by turning off the ignition switch, the energization to the solenoid unit 55 from the ECU 37 is also cut off. Therefore, as shown in FIGS. It is held at the maximum rightward position by the spring force of the spring 54 (first position). At this time, each advance port 19a of the valve body 50 is opened by the first land portion 51a of the spool valve 51, and the drain passage 60 of the spool valve 51 is communicated. For this reason, the hydraulic oil in each advance hydraulic chamber 12 passes through each advance passage hole 64b of the sleeve 52, each advance port 19a of the valve body 50, and the spool valve 51, as indicated by broken line arrows in FIG. 11A. It passes through the drain passage 60, flows into the drain chamber 66 of the drain cap 53, and is discharged to the outside from each opening hole 66a. Thereby, the inside of each advance hydraulic chamber 12 becomes a low pressure.

  At the same time, as shown in FIGS. 11A and 11B, the spool valve 51 causes each retard port 18 a and each reintroduction port 58 to communicate with the groove groove 61. Therefore, in this state, the reintroduction ports 58 communicate with the communication grooves 65, the introduction ports 57, and the introduction passages 59.

  When the engine is stopped, the oil pump 20 is also stopped, so that no hydraulic pressure is supplied to the retard / advance hydraulic chambers 11 and 12, so that the vane rotor 9 is connected to the camshaft 2. Due to the negative alternating torque acting, as shown by the one-dot chain line in FIG. 2, the sprocket 1 rotates relative to the counterclockwise direction (most retarded angle direction). Therefore, the intake valve is controlled so that the valve timing is the most retarded phase.

  At this time, when the vane rotor 9 is held at the most retarded position, the lock pin 25 is advanced by the spring force of the coil spring 26 and is engaged with the lock hole 24 so that the vane rotor 9 is locked to the housing 7. It becomes a state.

  Next, when the engine is started by turning on the ignition switch, the oil pump 20 is also driven accordingly, and the hydraulic pressure discharged to the discharge passage 20a is as shown by the solid arrows in FIGS. 11A and 11B. From the introduction passage 59 through the introduction port 57, it flows into each communication groove 65. From here, each reintroduction port 58, groove groove 61, each retardation port 18 a, and each retardation passage hole 64 a are supplied to each retardation hydraulic chamber 11 through the retardation passage 18. As a result, each retarded hydraulic chamber 11 is in a high pressure state. Accordingly, since the vane rotor 9 is maintained in the state of relative rotation to the most retarded position, the valve timing of the intake valve is controlled to the retarded side, and thus the engine startability is improved. Become.

  At this time, the same hydraulic pressure as that of the retarded hydraulic chamber 11 is supplied to the release pressure receiving chamber through the lock passage. However, since the hydraulic pressure in the release pressure receiving chamber does not increase at the initial stage of cranking, The pin 25 is engaged with the lock hole 24 and locked. Therefore, flapping of the vane rotor 9 due to the alternating torque can be suppressed.

  Thereafter, when the hydraulic pressure supplied to the release pressure receiving chamber via the lock passage becomes high, the lock pin 25 is moved backward against the spring force of the coil spring 26 to release the lock state with the lock hole 24. As a result, the vane rotor 9 becomes free.

  At this time, each of the advance hydraulic chambers 12 is maintained in a low pressure state as described above.

  Next, for example, when the engine shifts from idling operation to steady operation, a predetermined amount of current is supplied from the ECU 37 to the coil 72 of the solenoid unit 55. As a result, the spool valve 51 slightly moves in the left direction in the drawing against the spring force of the valve spring 54 as shown in FIGS. 12A and 12B by the pressing force of the drive rod 75 (second position). In this state, the retard port 18a and the advance port 19a are closed by the first and second land portions 51a and 51b, and each reintroduction port 58 is also in communication with the groove groove 61. It will be in the state closed by 51a, 51b.

  Therefore, as shown in FIG. 12A, each of the retarded hydraulic chamber 11 and the advanced hydraulic chamber 12 has no hydraulic oil discharged from the inside thereof, and at the same time, the hydraulic fluid pumped from the oil pump 20 As shown in FIG. 12B, the supply to the hydraulic chambers 11 and 12 is interrupted.

  As a result, the vane rotor 9 is held at an intermediate position between the most retarded angle and the most advanced angle, as shown by the solid line in FIG. Therefore, the valve timing of the intake valve is controlled to an intermediate phase between the most retarded angle and the most advanced angle, so that the engine rotation can be stabilized and fuel consumption can be improved during steady operation.

  Next, for example, when the engine shifts from a steady operation to a high rotation / high load region, a larger current is supplied from the ECU 37 to the coil 72 of the solenoid unit 55, and the spool valve 51 is moved by the pressing force of the drive rod 75. As shown in FIGS. 13A and 13B, the valve spring 54 moves to the maximum left direction against the spring force (third position). As a result, the retard port 18a communicates with the discharge passage 62, and the reintroduction port 58 and the advance port 19a communicate with the groove groove 61, respectively.

  Accordingly, the hydraulic pressure in each retarded hydraulic chamber 11 is supplied to each drain hole 63 and drain passage 60 from the retarded passage hole 64a and the retarded port 18a through the discharge passage 62 as shown by the broken line arrows in FIG. 13A. And then continuously enters the drain chamber 66 and is discharged to the outside through the respective opening holes 66a. For this reason, the inside of each retarded hydraulic chamber 11 becomes a low pressure.

  On the other hand, hydraulic oil pumped from the oil pump 20 enters each advance hydraulic chamber 12 from the groove groove 61 to each advance port 19a, each advance passage hole, as shown by solid line arrows in FIGS. 64b is supplied to each advance hydraulic chamber 12 via the advance passage 19, and the interior of each advance hydraulic chamber 12 becomes high pressure.

  Therefore, the vane rotor 9 rotates in the clockwise direction and relatively rotates to the maximum advance angle side, as indicated by a two-dot chain line in FIG. As a result, the valve timing of the intake valve becomes the most advanced angle phase, the valve overlap of the exhaust valve increases, the intake charging efficiency increases, and the output torque of the engine can be improved.

  Thus, the ECU 37 controls the position of the spool valve 51 in the axial direction by energizing or shutting off the solenoid valve 21 with a predetermined energization amount according to the operating state of the engine. As a result, the phase change mechanism 3 and the lock mechanism 4 are controlled to control the camshaft 2 to the optimum relative rotational position with respect to the sprocket 1, so that the valve timing control accuracy can be improved.

  In addition, since the solenoid portion 55 is provided with the plunger 75 in the guide member 74 made of a synthetic resin material, the sliding guide performance in the axial direction of the plunger 75 is improved, and the sliding response can be improved. .

  Moreover, when the coil 37 is energized from the ECU 37, the magnetic flux generated in the coil 72 forms a magnetic circuit among the solenoid casing 71, the suction stator 79, the delivery stator 70, and the plunger 75. As indicated by the arrows, when the solenoid casing 71 flows into the disk portion 71b from the outer cylindrical portion 71a, it flows into the inner cylindrical portion 71c as it is, and the suction force in the axial direction (left direction in the figure) is applied to the plunger 75. Make it work. On the other hand, a part of the magnetic flux flowing into the disk portion 71b flows into the large-diameter cylindrical portion 79c of the suction stator 79 that is in contact with the disk portion 71b, passes through the disk wall 79b and the cylindrical portion 79a. Similarly, a suction force in the axial direction (left direction in the figure) is applied to the plunger 75.

  For this reason, the magnetic efficiency between the solenoid casing 71 and the suction stator 79 and the cylindrical portion 71c is greatly improved. As a result, the suction force in the left direction in the figure with respect to the plunger 75 is increased, and the slidability is further improved in combination with the good slidability in the guide member 74 of the plunger 75.

  Further, since the solenoid casing 71 (the outer cylinder portion 71a and the disk portion 71b) is integrally provided with the inner cylinder portion 71c which is a facing portion, the magnetic fluidity is improved and the magnetic efficiency is further increased. Can do.

  Furthermore, since the suction stator 79 is formed separately by a press, it can be manufactured at a lower cost than cutting or forging.

  In this embodiment, the spool valve 51 is slidably provided inside the valve body 50, and the sleeve 52 is fixed to the outer peripheral surface of the cylindrical shaft portion 50b of the valve body 50. Therefore, the entire structure of the electromagnetic valve 21 is simplified. Can be In addition, since the hydraulic paths such as the passage holes and the ports can be simplified, the manufacturing work efficiency can be improved and the manufacturing work cost can be reduced.

  Further, since the sleeve 52 is not provided inside the valve body 50 but simply fixed to the outer peripheral surface of the valve body 50, the sleeve 52 is not required to have high dimensional accuracy. However, manufacturing cost can be reduced.

  Moreover, since the high dimensional accuracy is not required, the sleeve 52 can be formed of a synthetic resin material, so that the weight of the solenoid valve 21 can be reduced.

  Further, since the sleeve 52 is formed in two parts and joined by welding, the assembling property to the valve body 50 is improved.

  Further, the shortening of the axial length of the bolt hole 6 and the simplification of the longitudinal sectional shape facilitate the drilling operation of the camshaft 2.

  In the present embodiment, since the two functions for controlling the hydraulic pressure to the retard hydraulic chamber 11 and the advanced hydraulic chamber 12 and controlling the hydraulic pressure to the release pressure receiving chamber are performed by the single electromagnetic valve 21, the engine The degree of freedom of layout on the main body can be improved and the cost can be reduced.

  Furthermore, since each passage hole is closed by the sliding position of the spool valve 51 of the electromagnetic valve 21 and the vane rotor 9 is held at the intermediate phase position, this holding property is improved.

  The present invention is not limited to the configuration of the above-described embodiment, and the case where the electromagnetic valve is applied to a valve timing control device has been shown. However, other than the valve timing control device, for example, other automatic transmissions of vehicles, etc. It is also possible to apply to equipment.

  Further, the valve timing control device can be applied not only to the intake side but also to the exhaust side.

  The sleeve can be formed of a metal material such as an aluminum alloy material, or can be formed of a single cylindrical member.

1 ... Sprocket (drive rotor)
DESCRIPTION OF SYMBOLS 2 ... Camshaft 2a ... One end part 3 ... Phase change mechanism 4 ... Lock mechanism 5 ... Hydraulic circuit 6 ... Bolt hole 6a ... Female thread part 7 ... Housing 7a ... Housing main body 9 ... Vane rotor (following rotary body)
DESCRIPTION OF SYMBOLS 11 ... Delay angle hydraulic chamber 12 ... Advance angle hydraulic chamber 16a-16d ... Vane 18 ... Delay angle passage 19 ... Advance angle passage 18a ... Delay angle port 19a ... Advance angle port 20 ... Oil pump 20a ... Discharge passage 21 ... Solenoid valve 37 ... Control unit (ECU)
50 ... Valve body (cam bolt)
51 ... Spool valve 52 ... Sleeve 53 ... Drain plug 54 ... Valve spring (biasing member)
55 ... Solenoid part (electromagnetic actuator)
70 ... Delivery stator (stator)
71 ... Solenoid casing (stator)
71a ... Outer cylinder part 71b ... Disk part 71c ... Inner cylinder part (opposite part)
72 ... Coil 73 ... Bobbin 74 ... Guide member 75 ... Plunger (mover)
76 ... Driving rod 79 ... Suction stator (suction part)
79a ... Cylindrical portion 79b ... Disc wall 79c ... Large diameter cylindrical portion

Claims (7)

A cup-shaped guide member formed of a non-magnetic material;
A mover of magnetic material provided slidably in the axial direction inside the guide member;
A coil that is arranged on the outer peripheral side of the guide member and generates a magnetic force when energized;
A stator that forms a magnetic path with the mover when a magnetic force is generated in the coil, and attracts the mover in an axial direction;
With
The stator is disposed between the guide member and the coil, and is disposed so as to be opposed to the suction portion that sucks the mover in the axial direction, and the end surface in the axial direction of the mover. An opposing portion that assists,
An electromagnetic valve characterized in that the suction part and the opposing part are provided in contact. The solenoid valve according to claim 1,
The solenoid valve according to claim 1, wherein the facing portion is formed integrally with a main body of the stator that covers an outer periphery of the coil. The solenoid valve according to claim 2,
An electromagnetic valve characterized in that the suction portion is formed separately from the main body of the stator and is provided in contact with the main body of the stator. The solenoid valve according to claim 3,
An electromagnetic valve characterized in that the suction part is formed by press molding. An electromagnetic valve used in a valve timing control device for an internal combustion engine that operates a driven rotating body by supplying and discharging hydraulic oil to change a relative rotational phase of a camshaft with respect to a crankshaft,
The solenoid valve is
An internal hollow cam bolt in which the driven rotating body is fixed to the end of the camshaft from the axial direction, and a supply / discharge port through which hydraulic oil flows through the peripheral wall extends in the radial direction;
A spool valve provided slidably in the internal axial direction of the cam bolt, and having a communication hole communicating with the supply / discharge port according to the sliding position;
An electromagnetic actuator for controlling the sliding position of the spool valve;
With
The electromagnetic actuator is
A cup-shaped guide member formed of a non-magnetic material;
A mover of magnetic material provided slidably in the axial direction inside the guide member;
A coil that is arranged on the outer peripheral side of the guide member and generates a magnetic force when energized;
A stator that forms a magnetic path with the mover and attracts the mover in the axial direction when a magnetic force is generated in the coil;
With
The stator is disposed between the guide member and the coil, and is disposed so as to be opposed to the suction portion that sucks the mover in the axial direction, and the end surface in the axial direction of the mover. An opposing portion that assists,
An electromagnetic valve used in a valve timing control device for an internal combustion engine, wherein the suction portion and the facing portion are provided in contact with each other. In the solenoid valve used for the valve timing control device of the internal combustion engine according to claim 5,
The internal combustion engine is characterized in that the opposing portion is provided integrally with the main body of the stator by press molding, while the suction portion is provided separately from the main body of the stator by press molding. A solenoid valve used in an engine valve timing control device. A cup-shaped guide member formed of a non-magnetic material;
A mover of magnetic material provided slidably in the axial direction inside the guide member;
A coil that is arranged on the outer peripheral side of the guide member and generates a magnetic force when energized;
A stator that forms a magnetic path with the mover and attracts the mover in the axial direction when a magnetic force is generated in the coil;
An electromagnetic actuator comprising:
The stator is disposed between the guide member and the coil, and is disposed so as to be opposed to the suction portion that sucks the mover in the axial direction, and the end surface in the axial direction of the mover. An opposing portion that assists,
An electromagnetic actuator characterized in that the suction portion and the facing portion are provided in contact with each other.

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