JP6581475B2 - solenoid valve - Google Patents

Description

  The present invention relates to, for example, an electromagnetic valve 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 used in a valve timing control device for an internal combustion engine have been provided, and one of them is described in Patent Document 1 below.

  Briefly, this electromagnetic valve is provided with a cylindrical valve body inserted and fixed in a valve hole formed in a cylinder block of an internal combustion engine, and provided in the valve body so as to be slidable along the axial direction. A cylindrical spool valve, a valve spring that urges the spool valve in one direction, and an axial end of the valve body that is fixed to one end of the valve body in the other direction against the spring force of the valve spring. And a solenoid for pressing the

  The valve body is formed with a plurality of ports penetrating along the radial direction in the peripheral wall, while the spool valve is formed with a plurality of land portions at the front and rear end portions in the axial direction of the peripheral wall and the outer periphery in the center. In addition, a drain hole communicating with the internal passage hole is formed at a predetermined position in the axial direction of the peripheral wall. Further, the spool valve integrally has a small-diameter cylindrical transmission shaft portion that is in axial contact with the movable iron core of the solenoid at one end portion on the solenoid side in the axial direction, and a so-called breathing hole is formed in the peripheral wall of the transmission shaft portion. It is formed through.

  Then, by moving the spool valve in the axial direction by energizing or de-energizing the solenoid from the control unit, the hydraulic oil pumped from the oil pump is separated by a vane rotor or the like by opening and closing each port. The relative advance phase of the camshaft with respect to the crankshaft is changed by selectively supplying and discharging to the advanced hydraulic chamber and the retarded hydraulic chamber.

JP2013-145030A

  However, in the electromagnetic valve described in Patent Document 1, the spool valve has a complicated overall structure due to many land portions, transmission shaft portions, and the like, and thus the spool valve is manufactured and processed. In this case, a large number of processes are required, and a reduction in manufacturing work efficiency and an increase in cost due to an increase in the number of processing steps are forced.

  An object of this invention is to provide the solenoid valve which can aim at the improvement of manufacturing work efficiency, such as a spool valve.

The invention according to claim 1 is provided with a cylindrical valve body in which a plurality of ports are formed, and is provided in the valve body so as to be slidable in the axial direction. A cylindrical spool valve that switches between opening and closing, holding portions formed on both axial end faces of the spool valve, and one end portion held by one holding portion of the holding portions, An urging member for urging the valve toward one axial side of the valve body; and an urging member provided on one axial end side of the valve body, the spool valve against the urging force of the urging member. A solenoid part to be moved to the other side in the axial direction, and one end part in the axial direction are held by the holding part on the other side of the two holding parts of the spool valve, and the other end is pivoted on the movable iron core of the solenoid part Abutting from the direction, the movable iron core and A coupling member that links a pool valve from the axial direction,
With
The spool valve is characterized in that it is formed in a symmetric shape with a radial line extending in the direction perpendicular to the center of the axis of the spool valve as a center .

  According to the present invention, since the spool valve and the linking member are configured separately, the number of processing steps for one component can be reduced, and the manufacturing work efficiency of the solenoid valve can be improved.

It is a whole lineblock diagram showing an embodiment of a valve timing control device to which a solenoid valve concerning the present invention is applied. It is a longitudinal cross-sectional view which shows the electromagnetic switching valve of this embodiment. It is a disassembled perspective view of the electromagnetic switching valve of this embodiment. The spool valve provided for this embodiment is shown, A is a side view of a spool valve, B is a perspective view. The linkage rod provided for this embodiment is shown, A is a side view of the linkage rod, and B is a longitudinal sectional view. The magnetic member with which this embodiment is provided is shown, A is a side view of a magnetic member, B is a longitudinal cross-sectional view. It is the A section enlarged view of FIG. It is a longitudinal cross-sectional view of the electromagnetic switching valve explaining the effect | action for hold | maintaining the vane rotor provided to this embodiment in the rotation position of an intermediate phase. It is a longitudinal cross-sectional view of the electromagnetic switching valve explaining the effect | action for controlling the vane rotor provided to this embodiment to the rotation phase of an advance angle side.

  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. The valve timing control device is provided on the intake valve side of the internal combustion engine.

  As shown in FIG. 1, the valve timing control device is arranged along a sprocket 1 that is a driving rotary body that is rotationally driven by a crankshaft of an engine via a timing chain (not shown), and in the longitudinal direction of the engine. An intake side camshaft 2 provided so as to be relatively rotatable with respect to the sprocket 1, and a phase change disposed between the sprocket 1 and the camshaft 2 to convert the relative rotational phase of the both 1 and 2. A mechanism 3; a lock mechanism 4 that locks the phase change mechanism 3 at the most retarded phase position; and a hydraulic circuit 5 that operates the phase change mechanism 3 and the lock mechanism 4 respectively.

  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 through which one end of the camshaft 2 is rotatably supported is formed.

  The camshaft 2 is rotatably supported by a cylinder head (not shown) via a plurality of cam bearings, and a plurality of egg-shaped rotary cams for opening an intake valve, which is an engine valve, are axially arranged on the outer peripheral surface. A bolt hole is formed that is integrally fixed to the position and into which a cam bolt 6 described later is screwed in the direction of the inner axis of the one end.

  As shown in FIG. 1, the phase changing mechanism 3 includes a housing 7 integrally provided in the sprocket 1 from the axial direction, and is fixed to one end of the camshaft 2 from the axial direction. A vane rotor 8 which is a driven rotating body accommodated in a freely rotatable manner, and a working chamber inside the housing 7 is separated by four shoes 9 projecting from an inner peripheral surface of the housing body described later and the vane rotor 8. There are four retarded hydraulic chambers 10 and advanced hydraulic chambers 11 which are the retarded working chamber and the advanced working chamber, respectively.

  The housing 7 is a cylindrical housing body 7a integrally formed of sintered metal, a front cover (not shown) that is formed by press molding and closes the front end opening of the housing body 7a, and the rear end opening is closed. The sprocket 1 is a rear cover. The housing body 7a, the front cover and the sprocket 1 are fixed together by four bolts 12 penetrating through the bolt insertion holes of the shoes 9. The front cover has a relatively large-diameter insertion hole formed in the center thereof, and seals the interior of each hydraulic chamber 10 and 11 with the outer peripheral side inner peripheral surface of the insertion hole.

  The vane rotor 8 is integrally formed of a metal material, and is fixed to one end portion of the camshaft 2 by a cam bolt 6, and an outer circumferential surface of the rotor portion 13 is positioned at substantially equal intervals of 90 ° in the circumferential direction. And four vanes 14a to 14d projecting radially.

  The rotor portion 13 is formed in a relatively large-diameter cylindrical shape, and has an insertion hole 13a through which the shaft portion of the cam bolt 6 is inserted in the center internal axial direction. A fitting hole 13b into which one end of the shaft 2 is fitted is formed.

  On the other hand, each of the vanes 14a to 14d is formed to have a relatively short protruding length, and each vane 14a to 14d is disposed between the shoes 9, and the circumferential width is set to be substantially the same. It is formed in a meat plate shape. Seal members 15a and 15b for sealing between the inner peripheral surface of the housing body 7a and the outer peripheral surface of the rotor portion 13 are provided on the outer peripheral surfaces of the vanes 14a to 14d and the tips of the shoes 9, respectively. It has been.

  Further, when the vane rotor 8 rotates relative to the counterclockwise direction (retarding direction) in FIG. 1, one side surface of the first vane 14 a contacts the projection surface formed on the opposing side surface of the one shoe 9. The rotational position on the maximum retarding angle side is regulated in contact therewith. In FIG. 1, when the relative rotation is clockwise (advance angle direction), the other side surface of the first vane 14a is in contact with the opposite side surface of the other shoe 9, and the rotation position on the maximum advance side is restricted. It has become so.

  At this time, the other vanes 14b to 14d are in a separated state without coming into contact with the facing surfaces of the shoes 9 whose both side surfaces are opposed in the circumferential direction. Therefore, the contact accuracy between the vane rotor 8 and the shoe 9 is improved, and the supply speed of hydraulic pressure to each of the hydraulic chambers 10 and 11 to be described later is increased, and the forward / reverse rotation response of the vane rotor 8 is improved.

  The retard hydraulic chambers 10 and the advance hydraulic chambers 11 described above are formed between both side surfaces of the vanes 14a to 14d in the forward and reverse rotation direction and both side surfaces of the shoes 9, respectively. The angular hydraulic chamber 10 and each advanced hydraulic chamber 11 are respectively connected to the hydraulic circuit 5 via a retard passage hole and an advance passage hole (not shown) formed in the rotor portion 13 along the radial direction. Communicate.

  The lock mechanism 4 locks and holds the vane rotor 8 at the most retarded rotational position with respect to the housing 7.

  That is, as shown in FIGS. 1 and 2, the lock mechanism 4 includes a lock hole (not shown) formed at a predetermined position on the inner peripheral side of the sprocket 1 and an inner shaft of the first vane 14 a of the vane rotor 8. A lock pin 16 which is provided in a sliding hole 17 formed in a direction so as to be freely movable back and forth, and whose tip is engaged with and disengaged from the lock hole, and a coil spring (not shown) that urges the lock pin 16 toward the lock hole. A release pressure receiving chamber which is formed inside the lock hole and releases the engagement by retreating the lock hole against the spring force of the coil spring by the supplied hydraulic pressure; And a lock passage for supplying hydraulic pressure to the release pressure receiving chamber.

  The lock hole is formed at a position corresponding to the rotational position of the innermost surface of the sprocket 1 on the most retarded side of the vane rotor 8.

  The lock pin 16 receives the hydraulic pressure supplied to the pressure-receiving chamber for release on the pressure-receiving surface at the tip, and moves backward to come out of the lock hole, thereby releasing the lock, and no hydraulic pressure acts on the pressure-receiving surface. In this case, the tip of the coil spring is engaged with the inside of the lock hole by the spring force of the coil spring to lock the vane rotor 8 with respect to the housing 7.

  As shown in FIGS. 1 and 2, the hydraulic circuit 5 includes a retard passage 18 that supplies and discharges hydraulic pressure to and from each retard hydraulic chamber 10 through a retard passage hole, and each advance hydraulic chamber 11. The advance passage 19 for supplying and discharging hydraulic pressure via the advance passage hole, the lock passage for supplying and discharging hydraulic pressure to the release pressure receiving chamber, and the respective retard and advance passages 18, 19 An oil pump 20 that selectively supplies hydraulic oil to the engine, and a single electromagnetic switching 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. ing.

  One end of each of the retard passage 18 and the advance passage 19 is connected to a retard angle, advance port 36, 37 of the valve body 30 (to be described later) of the electromagnetic switching valve 21, while the other end is the retard passage. The retard angle hydraulic chambers 10 and the advance angle hydraulic chambers 11 communicate with the respective advance angle hydraulic chambers 11 through corner and advance angle passage holes.

  The lock passage communicates with the retard passage 18 so that the hydraulic pressure supplied to and discharged from the retard hydraulic chamber 10 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 discharges hydraulic oil sucked from the oil pan 22 through the suction passage 20a by the rotation of the outer and inner rotors. It is discharged through the passage 20b, 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 switching valve 21 side. Yes. A filtration filter (not shown) is provided on the downstream side of the discharge passage 20b, and excess hydraulic oil discharged from the discharge passage 20b is returned to the oil pan 22 through the drain passage 22 to be appropriate. A flow rate control valve for controlling the flow rate is provided.

  As shown in FIGS. 1 to 3, the electromagnetic switching valve 21 is a four-port, three-position proportional valve, and includes a cylindrical valve body 30 inserted and held in a valve hole of a cylinder block, and the valve body. A cylindrical spool valve 31 slidably provided in a sliding hole 30a formed in the inner axial direction of the valve 30, an inner bottom surface of an end wall 30b at one axial end of the valve body 30, and the spool A valve spring 32, which is a biasing member that is elastically mounted between one end portion of the valve 31 in the axial direction and biases the spool valve 31 rightward in FIG. 2, and the other end in the axial direction of the valve body 30. And a solenoid part 33 that moves the spool valve 31 in the left direction in the figure against the spring force of the valve spring 32.

  The valve body 30 is formed of an aluminum alloy material, and a drain hole 34 communicating with the outside is formed through the center of the end wall 30b on one end side, and the axial direction of the peripheral wall is substantially at the center position. A supply port 35 communicating with the discharge passage 20b of the oil pump 20 is formed penetrating along the radial direction. Further, a retard port 36 communicating with the retard passage 18 is formed in a side portion of the supply port 35 on the solenoid portion 33 side along the radial direction, and on the side portion on the end wall 30b side, An advance port 37 communicating with the advance passage 19 is formed through the radial direction. The supply port 35, the retard port 36, and the advance port 37 each have a groove formed on the outer peripheral side in cooperation with the inner peripheral surface of the valve hole of the cylinder block.

  Further, the valve body 30 is integrally provided with a rear end peripheral wall 39 on the solenoid portion 33 side, and a cylindrical press-fit groove 39a having an inner diameter larger than the sliding hole 30a is formed in the rear end peripheral wall 39. Yes. An oil seal 38 is fitted and fixed in an annular seal groove formed at the front end portion of the outer peripheral portion of the rear end peripheral wall 39 so that the outer peripheral portion is in elastic contact with the inner peripheral surface of the valve hole. A seal ring 40 is fitted into an annular holding groove formed on the inner peripheral side of the outer peripheral surface of the cylindrical rear end peripheral wall 39 so as to contact and seal a flange portion 50b of a cap sleeve 50 described later in the axial direction. It is fixed.

  The spool valve 31 is integrally formed of an aluminum alloy material, and is formed in a cylindrical shape as shown in FIGS. 4A and 4B. The spool valve 31 is symmetric about a radial line X extending in the direction perpendicular to the center of the axis. In addition, a drain passage 31a, which is an oil passage communicating with the drain hole 34 in the direction of the internal axis, is formed to penetrate therethrough. Here, the “substantially symmetrical shape” described above is established regardless of which of the first and second land portions 42 and 43 is assembled to the solenoid portion 33 side when the spool valve 31 is assembled in the valve body 30. It includes a shape in which the shapes of the cylindrical first and second land portions 42 and 43 are different from each other.

  This spool valve 31 slides on the inner peripheral surface of the sliding hole 30a of the valve body 30 at both ends of the central small-diameter shaft portion 41 to make the opening areas of the ports 35 to 37 variable. 1 and second land portions 42 and 43, and a cylindrical annular groove 41a which forms a passage in the outer periphery of the small-diameter shaft portion 41 in cooperation with the inner peripheral surface of the sliding hole 30a. Is formed. The land portions 42 and 43 have annular first and second concave grooves 42a and 43a which are holding portions (concave portions) communicating with both ends of the drain passage 31a on the outer end surfaces.

  A linkage rod 44, which is a linkage member, is inserted and held in the first concave groove 42a on the solenoid portion 33 side of the spool valve 31. Note that holding by press-fitting may be used. As shown in FIG. 2 and FIGS. 5A and B, the linkage rod 44 is formed of a synthetic resin material in a hollow trumpet shape, and has a passage portion 44a formed in the internal axial direction and one end portion in the axial direction. That is, the large-diameter cylindrical portion 44b that is one end portion on the spool valve 31 side, the small-diameter cylindrical portion 44c that is the other end portion, and the inclined step formed between the large-diameter cylindrical portion 44b and the small-diameter cylindrical portion 44c. 44d.

  The large-diameter cylindrical portion 44b has a distal end outer peripheral surface that is press-fitted and fixed to the inner peripheral surface of the first concave groove 42a from the axial direction, and at the central position is an axial direction that can communicate with the retard port 36. Two first communication holes 44e having a long hole shape extending along the radial direction are formed penetrating along the radial direction. The first communication hole 44e communicates with a retarding port 36 described later as appropriate through a gap between the outer peripheral surface of the large-diameter cylindrical portion 44b and a sliding hole 30a described later.

  The small-diameter cylindrical portion 44c has two small circular communication holes 44f penetratingly formed along the radial direction at the tip, and the tip edge is formed at the center of the front end surface of a plunger 51 (to be described later) of the solenoid portion 33. The valve spring 32 abuts from the axial direction through the spring force. The second communication hole 44f functions as a so-called breathing hole and oil discharge for ensuring good movement of the plunger 51 described later.

  The stepped cylindrical portion 44d is formed in a smooth inclined shape in which the large diameter cylindrical portion 44b and the small diameter cylindrical portion 44c are continuously connected.

  One end of the valve spring 32 is in elastic contact with the inner bottom surface of the end wall 30 b of the valve body 30, and the other end is in elastic contact with the bottom surface of the second concave groove 43 a of the spool valve 31. 31 is urged toward the solenoid 33.

  A magnetic member 45 constituting a part of the solenoid portion 33 is press-fitted and fixed in the press-fitting groove 39 a of the rear end peripheral wall 39 of the valve body 30. As shown in FIGS. 6A and 6B, the magnetic member 45 is formed of a ferrous metal material in a stepped cylindrical shape as a whole, and includes a fixing portion 45a that is a large-diameter fixing portion on the valve body 30 side, and the fixing portion 45a. And a bottomed small-diameter fitting portion 45b that is integrally provided on the edge of the connecting rod 45c so as to surround the connecting rod 44 on the outer peripheral side of the connecting rod 44. Is arranged.

  The outer peripheral surface of the fixing portion 45a is press-fitted and fixed to the inner peripheral surface of the press-fitting groove 39a, and the axial length thereof is substantially the same as the axial length of the press-fitting groove 39a.

  The fitting portion 45b has a guide hole 45e through which a small-diameter cylindrical portion 44c of the linkage rod 44 can slide in the center of the bottom wall 45d, and fits into a fitting hole 48c of a bracket 48 described later. Match.

  The step 45c is formed in a downwardly inclined manner from the fixed portion 45a to the fitting portion 45b, and its inner peripheral surface 45f is formed in a size that does not hinder the movement of the linkage rod 44 in the maximum axial direction. Yes.

  Further, a trumpet-shaped gap passage 55 communicating with the first communication hole 44e is formed between the inner peripheral surface of the magnetic member 45 and the outer peripheral surface of the connecting rod 44.

  As shown in FIGS. 1 to 3, the solenoid 33 includes a cylindrical casing 46 made of a magnetic material, a cylindrical coil 47 fixed to the inner peripheral side of the casing 46, and a front end of the casing 46. A bracket 48 which is a first fixed iron core made of a magnetic material which is fixed by crimping to the cylinder block and which fixes the entire solenoid valve to the cylinder block, and a magnetic material cylinder which is a second fixed iron core fixed to the inner peripheral side of the coil 47 It is mainly composed of a portion 49 and a plunger 51 which is a columnar movable iron core slidable in the axial direction via a bottomed cylindrical cap sleeve 50 on the inner peripheral side of the cylindrical portion 49.

  The casing 46 retains the shape by rounding a flat plate into a cylindrical shape and engaging the concavo-convex portions 46a and 46b at the opposite ends, and four claw portions 46c for caulking at the tip of the valve body 30 side. Are provided integrally.

  The coil 47 is integrally formed with a connector 52 electrically connected to the ECU 54 via a harness at a rear end portion, and is deenergized by a control current supplied from the ECU 54. .

  The bracket 48 is integrally formed by press molding, and includes a large-diameter annular portion 48a and a fixing arm 48b integrally formed on the outer peripheral edge of the annular portion 48a. As shown in FIG. 7, the annular portion 48 a is formed with a fitting hole 48 c in which the fitting portion 45 b of the magnetic member 45 is fitted by a clearance fit through a cap sleeve 50 made of a magnetic material. In addition, a cylindrical protrusion 48d through which magnetic flux flows is integrally projected along the inner circumferential axis direction of the coil 47 at the hole edge of the fitting hole 48c. The fixing arm 48b is formed with a bolt insertion hole 48e through which a bolt fixed to the cylinder block is inserted.

  The cap sleeve 50 is formed of a stainless steel material in a thin cylindrical shape, and its axial length is longer than the moving length of the plunger 51, and the maximum retreating movement of the plunger 51 is regulated by a raised bottom-like bottom wall 50a. In addition, a flange portion 50b provided integrally with the front end edge is in elastic contact with one side surface of the seal ring 40.

  In addition, the cap sleeve 50 has an inner peripheral surface on the flange portion 50b side that is in pressure contact with an outer peripheral surface of the fitting portion 45b of the magnetic member 45, and the outer peripheral surface is the inner surface of the protrusion 48c as described above. The peripheral surface is confronted from the radial direction through a minute air gap C.

  The plunger 51 is formed with a through hole 51a for ensuring mobility in the inner axial direction, and an annular shape in which the distal end surface of the small-diameter cylindrical portion 44b of the linkage rod 44 abuts from the axial direction on the distal end side. Spacer 53 is provided. The plunger 51 is moved in the direction of the spool valve 41 by the magnetic force of the bracket 48 and the cylindrical portion 49 by excitation by energization of the coil 47.

  That is, the magnetic field generated by energizing the coil 47 flows from the casing 46 to the annular portion 48a of the bracket 48 as shown by the arrow in FIG. 7, and from here the protrusion 48d side and the air gap C Then, it flows into the fitting portion 45b and the cylindrical portion 49 of the magnetic member 45 via the pin, and generates an attractive force in the direction of the spool valve 41 with respect to the plunger 51. In particular, the magnetic member 45 assists the magnetic force applied to the plunger 51 to increase the attractive force toward the spool valve 41.

  In the ECU 54, 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. An information signal from various sensors such as a cam angle sensor is input to detect the current engine operating state, and as described above, a control current is output to the coil 47 or the energization is cut off to cut the spool valve 31. The movement position is controlled to selectively switch the ports.

That is, as shown in FIGS. 2, 8, and 9, the solenoid unit 33 causes the spool valve 31 to move in three positions in the front-rear axial direction by the relative pressure between the control current of the ECU 54 and the valve spring 32. Move to. In other words, the supply, retard angle, and advance port 35, 36, 37 of the valve body 30 are relatively communicated or blocked by moving the three positions, and at the same time, the advance port 37 or the retard port 36 is connected to the drain hole 34, The drain passage 31 a is communicated, and the communication between the retard port 36 and the advance port 37 is blocked with respect to the supply port 35.
[Operation of this embodiment]
Hereinafter, a specific operation of 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 portion 33 (coil 47) from the ECU 54 is also cut off, so the spool valve 31 is as shown in FIG. The valve spring 32 is held at the maximum rightward position by the spring force (first position). At this time, the advance port 37 of the valve body 50 and the drain hole 34 are communicated by the first land portion 43 of the spool valve 31, and the supply port 35 and the retard port 36 are connected by the second land portion 42 via the annular groove 41a. Communicate. Therefore, the hydraulic oil in each of the advance hydraulic chambers 11 is discharged from the drain hole 34 to the oil pan 22 through the advance passage 19 and the advance port 37, as indicated by the broken arrow in FIG. Each advance hydraulic chamber 11 is in a low pressure state.

  When the engine is stopped, the drive of the oil pump 20 is also stopped, so that no hydraulic pressure is supplied to the retard hydraulic chamber 10, so that the vane rotor 8 has an alternating torque acting on the camshaft 2. Due to the negative torque, 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 8 is held at the most retarded position, the lock pin 16 of the lock mechanism 4 is advanced by the spring force of the coil spring and is engaged with the lock hole so that the vane rotor 8 is locked to the housing 7. It will be in the state.

Next, when the engine is started by turning on the ignition switch, the oil pump 20 is also driven, and the hydraulic pressure discharged to the discharge passage 20b is changed to the annular groove 41a as shown by the solid line arrow in FIG. Are supplied into the respective retard hydraulic chambers 10 through the retard ports 36 and the retard passages 18, and the respective retard hydraulic chambers 10 are in a high pressure state.
Accordingly, since the vane rotor 8 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 therefore the engine startability is improved. Become.

  At this time, the same hydraulic pressure as that of the retarded hydraulic chamber 10 is supplied to the release pressure receiving chamber via 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 16 enters the lock hole 24 and is locked. Therefore, flapping of the vane rotor 8 due to the alternating torque can be suppressed.

  Thereafter, when the hydraulic pressure supplied to the release pressure receiving chamber via the lock passage increases as the hydraulic pressure of each retarded hydraulic chamber 10 increases, the lock pin 16 is moved backward against the spring force of the coil spring. To unlock the lock hole. As a result, the vane rotor 8 becomes free.

  At this time, each of the advance hydraulic chambers 11 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 54 to the coil 47 of the solenoid unit 33, and the plunger 51 slightly moves leftward by the attractive force of the magnetic force. . As a result, as shown in FIG. 8, the spool valve 31 slightly moves in the left direction in the figure against the spring force of the valve spring 32 by the pressing force of the linkage rod 44 (second position). In this state, both the retard port 36 and the advance port 37 are closed by the first and second land portions 42 and 43.

  Therefore, each of the retarded hydraulic chamber 10 and the advanced hydraulic chamber 11 does not discharge the hydraulic oil from the inside thereof, and at the same time, the hydraulic fluid fed from the oil pump 20 is also sent to the hydraulic chambers 11 and 12. Is interrupted. As a result, the vane rotor 8 is held at an intermediate position between the most retarded angle and the most advanced angle, as shown 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 54 to the coil 47 of the solenoid unit 33, and the spool valve 31 is moved by the pressing force of the plunger 51. As shown in FIG. 9, the valve spring 32 moves to the left in the maximum direction against the spring force (third position). As a result, the retard port 36 communicates with the drain passage 31a through the first communication hole 44e.

  Accordingly, the hydraulic pressure in each retarded hydraulic chamber 10 flows from the retarded port 36 into the drain passage 31a through the clearance passage 55, the first communication hole 44e, and the passage portion 44a as shown by the broken line arrows in FIG. From here, the oil is discharged into the oil pan 22 through the drain hole 34. For this reason, each retarded hydraulic chamber 10 is in a low pressure state.

  On the other hand, hydraulic oil pumped from the oil pump 20 is advanced into each advance hydraulic chamber 11 from the groove groove through the advance port 37 and the advance passage 19 as shown by solid line arrows in FIG. It is supplied to each advance hydraulic chamber 11 through the corner passage hole, and the inside of each advance hydraulic chamber 11 becomes a high pressure state.

  Therefore, the vane rotor 8 rotates clockwise from the position of FIG. 1 and relatively rotates to the maximum advance angle side. 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 54 controls the position of the spool valve 31 in the axial direction by energizing or shutting off the electromagnetic switching 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 this embodiment, since the spool valve 31 and the linkage rod 44 are configured as separate members, the structural complexity of one component is suppressed as compared with the case where the spool valve 31 and the linkage rod 44 are integrally formed. it can. Therefore, it is possible to improve the manufacturing work efficiency. Here, by forming the linkage rod 44 from a resin material, the linkage rod 44 having a relatively complicated structure can be easily formed. On the other hand, by forming the spool valve 31 from a metal material, It is possible to form parts such as the second land portions 42 and 43 that require dimensional accuracy.

  Further, in the present embodiment, the spool valve 31 is formed in a substantially symmetrical shape with the radial line X extending in the direction perpendicular to the axis at the center of the axis, so that the structure is simplified and the machining operation is simplified. . As a result, the manufacturing work efficiency of the spool valve 31 can be improved.

  Further, since the spool valve 31 is formed in a bilaterally symmetric shape, when the spool valve 31 is assembled in the valve body 30 together with other components, it can be inserted and assembled from either the left or right direction. Therefore, the assembling work becomes easy and the assembling management becomes easy.

  A first concave groove 42a and a second concave groove 43a having substantially the same shape that can be held by either the valve spring 32 or the linking rod 44 are formed on both end faces of the spool valve 31, and the both concave grooves 42a, 43a are formed. Since the large-diameter cylindrical portion 44b of the connecting rod 44 can be press-fitted and fixed, and one end portion of the valve spring 32 can be elastically supported, the assembling property can be improved and the two concave grooves 42a and 43a can be effectively used. I can plan.

  Since the linkage rod 44 is not fixed to the general plunger 51 but is inserted and held in the first concave groove 42a of the spool valve 31, the weight of the plunger 51 can be reduced. For this reason, the inertia weight of the plunger 51 is reduced, and the axial mobility associated with the de-excitation of the coil 47 is improved.

  Since the linkage rod 44 is formed of a synthetic resin material, the entire spool valve 31 can be reduced in weight, so that the inertia weight of the spool valve 31 itself is reduced and axial mobility is improved. Moreover, since the linkage rod 44 can be formed by injection molding or the like, the manufacturing operation is facilitated and the shape and structure can be freely changed.

  By inserting the fitting portion 45b of the magnetic member 45 into the fitting hole 48c of the bracket 48, the magnetic force generated by the coil 47 can be assisted and the plunger 51 can be moved quickly. . As a result, the movement responsiveness of the spool valve 31 is improved.

  With the simplification of the structure of the spool valve 31, the overall structure of the electromagnetic switching valve 21 can be simplified, and the hydraulic circuits such as the passage holes and the ports can be simplified. Manufacturing work costs can be reduced.

  In the present embodiment, the single electromagnetic switching valve 21 performs two functions for controlling the hydraulic pressure to the retard hydraulic chamber 10 and the advanced hydraulic chamber 11 and controlling the hydraulic pressure to the release pressure receiving chamber. The degree of freedom of layout on the engine 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 31 of the electromagnetic switching valve 21 and the vane rotor 8 is held at the intermediate phase position, this retainability 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 holding portion is not limited to the annular concave grooves 42a and 43a, and may be a convex portion, for example, as long as the valve spring 32 can be held.

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

DESCRIPTION OF SYMBOLS 1 ... Sprocket 2 ... Camshaft 2a ... One end part 3 ... Phase change mechanism 4 ... Lock mechanism 5 ... Hydraulic circuit 7 ... Housing 7a ... Housing main body 9 ... Vane rotor 11 ... Delay angle hydraulic chamber 12 ... Advance hydraulic chamber 18 ... Delay angle Passage 19 ... Advance passage 20 ... Oil pump 21 ... Electromagnetic switching valve (solenoid valve)
DESCRIPTION OF SYMBOLS 30 ... Valve body 31 ... Spool valve 31a ... Drain passage 32 ... Valve spring 33 ... Solenoid part 34 ... Drain hole 35 ... Supply port 36 ... Retarded port 37 ... Advance port 42 ... 1st land part 42a ... 1st groove (Holding part, concave part)
43 ... 2nd land part 43a ... 2nd ditch | groove (holding part, recessed part)
44. Linking rod (linking member)
44a ... passage 44e ... first communication hole 44f ... second communication hole 45 ... magnetic member 45e ... guide hole 46 ... casing 47 ... coil 48 ... bracket (first fixed iron core)
49 ... Cylindrical part (second fixed iron core)
51 ... Plunger (movable iron core)
55. Clearance passage

Claims (11)

A tubular valve body formed with a plurality of ports;
A cylindrical spool valve provided inside the valve body so as to be slidable in the axial direction, and performing switching between opening and closing of the plurality of ports according to a sliding position;
Holding portions respectively formed on both axial end faces of the spool valve;
An urging member having one end portion held by one of the holding portions and urging the spool valve toward one side in the axial direction of the valve body;
A solenoid portion that is provided on one axial end side of the valve body and moves the spool valve to the other axial side of the valve body against the biasing force of the biasing member;
One end portion in the axial direction is held by the holding portion on the other side of the two holding portions of the spool valve, and the other end portion is in contact with the movable iron core of the solenoid portion from the axial direction so that the movable iron core and the spool valve are A linkage member linked from the axial direction;
With
The solenoid valve is characterized in that the spool valve is formed in a symmetric shape with a radial line extending in a direction perpendicular to the center of the axis of the spool valve as a center . The solenoid valve according to claim 1,
The electromagnetic valve, wherein the linking member is formed of a synthetic resin material. The solenoid valve according to claim 1,
The electromagnetic valve, wherein the holding part is a concave part. The solenoid valve according to claim 3 ,
The pair of recesses are formed so as to be able to be held at either one end of the biasing member or one end of the linkage member. The solenoid valve according to claim 1,
The linking member has a passage portion communicating with an oil passage formed therethrough along the internal axial direction of the spool valve, and a first communicating with one of the plurality of ports on the peripheral wall of the one end portion. A communication hole is formed in a penetrating manner, and a second communication hole that communicates the passage portion and the outside is formed through the peripheral wall of the other end portion. The solenoid valve according to claim 1,
The solenoid unit energizes the movable iron core to one side in the axial direction by a magnetic force when energized, and forms a magnetic circuit together with the movable iron core in a state in which a magnetic field is generated in the coil. A fixed iron core that sucks the iron core in the axial direction;
The valve body has a cylindrical magnetic member fixed in a state surrounding the linkage member on one end side in the axial direction,
The magnetic member is composed of a fixed portion fixed to one end side of the valve body, and a fitting portion fitted and arranged on the inner peripheral side of the fixed iron core. The solenoid valve according to claim 6 ,
A solenoid valve, wherein a gap passage is formed between an inner peripheral surface of the fixed portion of the magnetic member and an outer peripheral surface of one end portion having a large diameter of the linkage member. The solenoid valve according to claim 7 ,
The electromagnetic valve characterized in that the one end portion of the linking member is fixed in a recess on the other side of the spool valve, and the other end portion is in contact with one axial end surface of the movable iron core. . The solenoid valve according to claim 8 ,
An electromagnetic valve characterized in that the fitting portion of the magnetic member is formed in a bottomed cylindrical shape, and an insertion hole through which the other end portion having a small diameter of the linking member is inserted is formed in the bottom wall. . The electromagnetic valve according to claim 9,
The second communication hole of the linking member is located at the movable iron core side in the axial direction away from the outer surface of the bottom wall of the magnetic member at the position where the spool valve has moved to the maximum in the solenoid part direction. A solenoid valve characterized by that. The solenoid valve according to claim 10 ,
The spool valve has two cylindrical land portions that open and close the ports at both ends, and a cylindrical annular groove is formed on the outer periphery of the small-diameter shaft portion between the land portions. An electromagnetic valve characterized by

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