JP2019203447A - Valve opening/closing timing controller - Google Patents

Abstract

To provide a valve opening/closing controller capable of controlling valve opening/closing timing accurately.SOLUTION: A valve opening/closing timing controller comprises a valve unit Vb that sets the relative rotational phase of a driving side rotor and a driven side rotor by fluid pressure in a fluid pressure chamber. The valve unit Vb has a spool 55 that is slidably arranged in a direction along the rotational axis X inside the valve unit Vb. The spool 55 has a first land R1, a second land R2, and a third land R3 in order in the direction along the rotational axis X. The fluid is discharged from the fluid chamber into the space between the second land R2 and the third land R3.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a valve opening / closing timing control device.

  Patent Document 1 discloses a drive-side rotator that rotates synchronously with a crankshaft of an internal combustion engine, a driven-side rotator that is arranged coaxially with the rotation axis of the drive-side rotator, and rotates integrally with a valve opening / closing camshaft. In order to connect the driven side rotating body to the camshaft, it is arranged coaxially with the rotational axis and communicates with an advance chamber defined between the driving side rotating body and the driven side rotating body. A connecting bolt having an outer peripheral surface formed with a retarding port communicating with a retarding chamber defined between the driving side rotating body and the driven side rotating body, and an inside of the connecting bolt A valve opening / closing timing control device including a spool that is disposed in the spool chamber and controls supply / discharge of the working fluid to or from the advance port or the retard port from a pump port formed in the connection bolt. Yes. In this valve opening / closing timing control device, the connecting bolt includes a bolt body that is connected to the driven side rotating body, and a sleeve that is externally fitted to the bolt body. The pump port is formed as a through hole extending from the spool chamber to the outer peripheral surface of the bolt body, and the advance port and the retard port are formed as a through hole formed between the bolt body and the sleeve. The spool is formed in a hollow shape, and a drain hole is formed at the protruding end at the outer end of the spool. The spool chamber is formed on the inner surface of the cylinder, accommodates the spool so as to reciprocate along the rotation axis, and a spool spring is disposed between the inner end of the spool and the retainer. As a result, the spool is biased so as to protrude in the direction of the outer end side. It also has a plunger that is arranged coaxially with the rotation axis so as to abut the outer end of the spool. By controlling the power supplied to the internal solenoid, the amount of protrusion of the plunger is set, and the advance angle The spool operating position such as position and retard position is set. For example, in the advance position, the hydraulic oil discharged from the retard chamber is discharged from the retard port to the spool chamber, and further flows through the spool and is discharged from the drain hole.

JP 2017-089477 A

  In the valve opening / closing timing control device described in Patent Document 1, the discharged hydraulic oil flows through the inside of the spool and is discharged from the drain hole at the tip of the spool. At the time of this discharge, a pressure (so-called back pressure) is applied to the spool along the flow of the discharged hydraulic oil toward the outer end side. Due to this pressure, the position of the spool may move, or the spool position may not be accurately controlled by the plunger. In addition, the hydraulic oil may not be discharged quickly due to the resistance of the hydraulic oil flowing through the spool. In such a case, since the valve opening / closing timing control device cannot accurately control the valve opening / closing timing, an improvement is desired.

  The present invention has been made in view of such a situation, and an object thereof is to provide a valve opening / closing timing control device capable of accurately controlling the valve opening / closing timing.

  In order to achieve the above object, the valve opening / closing timing control device according to the present invention has a characteristic configuration in which a driving side rotating body that rotates synchronously with a crankshaft of an internal combustion engine, and a rotational axis center of the driving side rotating body are arranged coaxially. A driven-side rotator that rotates integrally with the valve opening / closing camshaft, an advance chamber and a retard chamber formed between the drive-side rotator and the driven-side rotator, and coaxial with the rotation axis A valve unit that is disposed in the center and controls supply and discharge of fluid to and from the advance chamber and the retard chamber, and an internal space extending in a direction along the rotational axis, and the valve is disposed in the internal space. A cylindrical valve case containing a unit, having an opening at one end in a direction along the rotation axis and having a bottom at the other end, the valve case extending from the outer peripheral surface to the internal space The advance chamber and the retard chamber that are formed communicate with each other. The valve unit has a base end portion fitted on the bottom side of the internal space, and extends along the rotation axis from the base end portion toward the opening side. The fluid supply pipe having a conduit portion having a smaller diameter and a bottom surface than the base end portion, and the rotation in a state guided by the inner peripheral surface of the valve case and the outer peripheral surface of the conduit portion of the fluid supply pipe. A spool having a cylindrical portion that is slidably arranged in a direction along the axis, and the spool is formed on the outer periphery of the cylindrical portion in order from the opening side toward the bottom side. A land, a second land, and a third land, wherein the fluid is discharged from the advance chamber or the retard chamber into a space between the second land and the third land.

  According to the above configuration, the pressure of the fluid discharged from the advance chamber or the retard chamber to the outer peripheral side of the cylindrical portion of the spool is relatively relative to the second land on the opening side in the direction along the rotation axis. In addition, they act in opposite directions to both the third land on the bottom side. Therefore, the force generated by the pressure acting on the second land and the force generated by the pressure acting on the third land cancel each other. Thereby, when fluid is discharged from the advance chamber or the retard chamber to the outer peripheral side of the cylindrical portion of the spool, no force in the direction along the rotation axis is applied to the spool. Therefore, when the fluid is discharged from the advance chamber or the retard chamber to the outer peripheral side of the cylindrical portion of the spool, the position of the spool moves or the position of the spool can be accurately controlled by the pressure of the discharged fluid. There will be no inconvenience that will be lost.

  Moreover, according to the said structure, the area | region where the fluid discharged | emitted flows can be restrict | limited to the area | region between a 2nd land and a 3rd land in the internal space of a valve case. Therefore, the influence of the discharged fluid (for example, the pressure generated by the flow) is not given to other components of the valve timing control apparatus related to the movement of the spool.

  Therefore, according to the said structure, the valve opening / closing timing control apparatus which can control valve opening / closing timing correctly can be provided.

  The valve opening / closing timing control device according to the present invention is further characterized in that the spool has an operation end at a front end of the tube portion on the opening side, and the operation end portion and the pipe inside the tube portion. There exists an elastic member which urges | biases the said operation end part toward the said opening side with respect to the said pipe line part between the said bottom faces of a road part.

  The elastic member that urges the spool toward the opening side affects the control of the position and movement of the spool. However, according to the above configuration, the elastic member does not directly contact the fluid to be discharged. Therefore, the discharged fluid does not affect the control of the position and movement of the spool. In addition, since the elastic member does not come into direct contact with the fluid to be discharged, for example, it is possible to suppress deterioration over time such that the elastic member such as a coil spring is worn by the flow of the fluid. Accordingly, it is possible to provide a valve opening / closing timing control device capable of accurately controlling the valve opening / closing timing.

  A further characteristic configuration of the valve opening / closing timing control device according to the present invention is that the valve unit has a space communication path having one end opened in the space on the opening side and disposed in a direction along the rotation axis. The space between the third land and the base end is connected to the space communication path.

  According to the above configuration, even when the fluid leaks to the bottom side in the direction along the rotation axis from the third land, the leaked fluid is discharged to the space on the opening side, that is, the external space through the space communication path. can do. As a result, it is possible to avoid the problem that the leaked fluid affects the operation of the spool. Therefore, it is possible to provide a valve opening / closing timing control device that can accurately control the valve opening / closing timing.

  A further characteristic configuration of the valve opening / closing timing control device according to the present invention includes a sleeve provided in contact with an inner peripheral surface of the valve case, and the spool is connected to the valve case via an inner peripheral surface of the sleeve. The sleeve is formed of a first drain hole communicating with the outside from a space between the second land and the third land, and the third land and the base end portion. A second drain hole communicating from the space between the first drain hole and the second drain hole, and the first drain hole and the second drain hole differ in a circumferential direction centering on a direction along the rotation axis of the sleeve. A plurality of the space communication passages are arranged in phase, and a plurality of the space communication passages are formed between the valve case and the sleeve, and each of the space communication passages includes the first drain hole and the second drain hole. Contact with each of Capable in that provided.

  According to the above configuration, a space communication path can be formed between the valve case and the sleeve. The space between the second land and the third land communicates with the external space that is the space on the opening side through the first drain hole and the space communication path. The space between the third land and the base end and the external space communicate with each other through the second drain hole and the space communication path.

  Further, according to the above configuration, the plurality of formed space communication paths can be connected to each of the first drain hole and the second drain hole that are arranged in the sleeve in different phases in the circumferential direction. That is, each of the plurality of space communication paths is compatible in terms of connection with the first drain hole and the second drain hole. Therefore, when the sleeve is attached to the valve case, it is not necessary to distinguish the positions of the first drain hole and the second drain hole with respect to each space communication path. That is, each space communication path can be connected to both the first drain hole and the second drain hole, and workability is improved when the sleeve is mounted on the valve case.

  The valve opening / closing timing control device according to the present invention is further characterized in that the sleeve includes an advance communication hole communicating from the inner peripheral surface of the sleeve to the advance port, and the retard port from the inner peripheral surface. The spool is formed at an intermediate position between the first land and the second land, and is moved from the inner peripheral surface of the cylindrical portion by sliding movement of the spool. An intermediate hole portion that can communicate with a corner communication hole or a retard communication hole is provided, and the fluid supply pipe is provided on an outer periphery of a distal end portion of the pipe line portion, and supplies the fluid to the intermediate hole portion from the inside. It has a supply port.

  According to the above configuration, from the supply port of the fluid supply pipe to the advance chamber or the retard chamber through the advance hole and the advance port or the advance port and the retard port through the intermediate hole portion of the spool. Fluid can be supplied. At this time, the fluid can be supplied to either the advance chamber or the retard chamber by causing the intermediate hole portion to communicate with the advance communication hole or the retard communication hole by the sliding movement of the spool.

Sectional drawing which shows the whole structure of a valve timing control apparatus II-II sectional view of FIG. Sectional view of valve unit with spool in advanced position Cross section of valve unit with spool in neutral position Cross section of valve unit with spool in retarded position Exploded perspective view of valve unit Front view of valve plate Perspective view of support part The figure explaining arrangement | positioning of a 1st drain hole, a 2nd drain hole, and a groove part

  Hereinafter, a specific example of the valve timing control apparatus according to the present invention will be described with reference to FIGS.

[Basic configuration]
As shown in FIG. 1 to FIG. 3, the valve includes an external rotor 20 as a driving side rotating body, an internal rotor 30 as a driven side rotating body, and an electromagnetic control valve V that controls the working oil as a working fluid. An opening / closing timing control device A is configured.

  The internal rotor 30 (an example of a driven-side rotator) is disposed coaxially with the rotation axis X of the intake camshaft 5 (an example of a camshaft), and the connecting bolt 40 ( It is connected to the intake camshaft 5 by an example of a valve case. The external rotor 20 (an example of a drive-side rotator) is disposed coaxially with the rotational axis X and rotates synchronously with the crankshaft 1 of the engine E as an internal combustion engine. The external rotor 20 includes the internal rotor 30, and the external rotor 20 and the internal rotor 30 are supported so as to be relatively rotatable.

  The electromagnetic control valve V includes an electromagnetic unit Va supported by the engine E and a valve unit Vb accommodated in the internal space 40R of the connecting bolt 40.

  The electromagnetic unit Va includes a solenoid unit 50 and a plunger 51 that is arranged coaxially with the rotation axis X and arranged coaxially with the rotation axis X so as to be moved back and forth by drive control of the solenoid unit 50. Yes. In the valve unit Vb, a spool 55 that controls supply and discharge of hydraulic oil (an example of a fluid) is arranged coaxially with the rotation axis X.

  With this configuration, the protrusion amount of the plunger 51 is set by controlling the electric power supplied to the solenoid unit 50, and the spool 55 is operated in the direction along the rotation axis X in conjunction with this. As a result, the hydraulic oil is controlled by the spool 55, the relative rotational phase between the external rotor 20 and the internal rotor 30 is determined, and the opening / closing timing of the intake valve 5V is controlled. The configuration of the electromagnetic control valve V and the control mode of hydraulic oil will be described later.

[Engine and valve timing control device]
An engine E (an example of an internal combustion engine) in FIG. 1 is provided in a vehicle such as a passenger car. The engine E is configured in a four-cycle type in which a piston 3 is accommodated inside a cylinder bore of the cylinder block 2 at an upper position, and the piston 3 and the crankshaft 1 are connected by a connecting rod 4. An upper portion of the engine E is provided with an intake camshaft 5 that opens and closes an intake valve 5V and an exhaust camshaft (not shown).

  A supply flow path 8 for supplying hydraulic oil from a hydraulic pump P driven by the engine E is formed in the engine constituent member 10 that rotatably supports the intake camshaft 5. The hydraulic pump P supplies the lubricating oil stored in the oil pan 11 of the engine E to the electromagnetic control valve V as working oil (an example of fluid) through the supply flow path 8.

  The timing chain 7 is wound around the output sprocket 6 formed on the crankshaft 1 of the engine E and the timing sprocket 22S of the external rotor 20. As a result, the external rotor 20 rotates in synchronization with the crankshaft 1. A sprocket is also provided at the front end of the exhaust camshaft on the exhaust side, and the timing chain 7 is wound around this sprocket.

  As shown in FIG. 2, the external rotor 20 rotates in the driving rotation direction S by the driving force from the crankshaft 1. The direction in which the inner rotor 30 rotates relative to the outer rotor 20 in the same direction as the drive rotation direction S is referred to as an advance angle direction Sa, and the opposite direction is referred to as a retard angle direction Sb. In this valve opening / closing timing control device A, when the relative rotational phase is displaced in the advance direction Sa, the intake compression ratio is increased as the displacement amount is increased, and when the relative rotational phase is displaced in the retard direction Sb, the displacement amount is increased. The relationship between the crankshaft 1 and the intake camshaft 5 is set so as to reduce the intake compression ratio as it increases.

  In this embodiment, the valve opening / closing timing control device A provided in the intake camshaft 5 is shown, but the valve opening / closing timing control device A may be provided in the exhaust camshaft. Further, the valve opening / closing timing control device A may be provided on both the intake camshaft 5 and the exhaust camshaft.

  As shown in FIGS. 1 and 2, the external rotor 20 has an external rotor main body 21, a front plate 22, and a rear plate 23, which are integrated by fastening a plurality of fastening bolts 24. A timing sprocket 22 </ b> S is formed on the outer periphery of the front plate 22. Further, the annular member 9 is fitted into the inner periphery of the front plate 22, and the bolt head 42 of the connecting bolt 40 is pressed against the annular member 9, whereby the annular member 9, the inner rotor main body 31, and the like. The intake camshaft 5 is integrated.

[External rotor, internal rotor]
As shown in FIG. 2, the outer rotor main body 21 is integrally formed with a plurality of protruding portions 21 </ b> T that protrude inward in the radial direction. The inner rotor 30 includes a cylindrical inner rotor body 31 that is in close contact with the protruding portion 21T of the outer rotor body 21 and an outer side in the radial direction from the outer periphery of the inner rotor body 31 so as to contact the inner peripheral surface of the outer rotor body 21. And four vane portions 32 projecting from each other.

  In this way, the outer rotor 20 includes the inner rotor 30, and a plurality of fluid pressure chambers C are formed on the outer peripheral side of the inner rotor body 31 at an intermediate position between the protrusions 21 T adjacent in the rotation direction. Is partitioned by the vane portion 32, and the advance chamber Ca and the retard chamber Cb are partitioned. Further, the internal rotor 30 is formed with an advance passage 33 that communicates with the advance chamber Ca and a retard passage 34 that communicates with the retard chamber Cb.

  As shown in FIGS. 1 and 2, the relative rotational phase between the external rotor 20 and the internal rotor 30 (hereinafter referred to as the relative rotational phase) is advanced by applying an urging force in the advance direction Sa from the most retarded phase. A torsion spring 28 that assists displacement in the direction Sa is provided across the outer rotor 20 and the annular member 9.

  As shown in FIGS. 1 and 2, the valve timing control apparatus A includes a lock mechanism L that holds the relative rotational phase between the external rotor 20 and the internal rotor 30 at the most retarded angle phase. The lock mechanism L includes a lock member 25 that is supported so as to be movable in and out along the rotational axis X with respect to one vane portion 32, a lock spring 26 that projects and urges the lock member 25, and a rear plate 23. And a lock recess 23a formed in the above. The lock mechanism L may be configured to guide the lock member 25 so as to move along the radial direction.

  In the lock mechanism L, when the relative rotational phase reaches the most retarded phase, the lock member 25 is engaged with the lock recess 23a by the urging force of the lock spring 26 and reaches the locked state. Further, the lock mechanism L is unlocked by applying the hydraulic oil pressure acting on the advance passage 33 to the lock member 25 in the unlocking direction.

[Connection bolt]
As shown in FIGS. 3 to 6, the connecting bolt 40 has a bolt head portion 42 formed on the outer end portion (side facing the electromagnetic unit Va) of a bolt main body 41 that is generally cylindrical. A cylindrical internal space 40R that penetrates in the direction along the rotation axis X and starts from the opening of the rotation axis X and the coaxial axis in the bolt head 42 is formed inside the connection bolt 40. The bolt head portion 42 has a male screw portion 41S (an example of a screw portion) formed on the outer periphery of the other end portion. In the direction along the rotation axis X of the inner circumferential surface of the internal space 40R, the above-mentioned opening projects to the other end side in a direction close to the rotation axis X, and the bottom wall 44 (end point of the internal space 40R becomes the end point) An example of the bottom portion is formed. The space on the front side of the internal space 40R is expanded with the step 45 as a boundary compared to the space on the rear side. The step portion 45 has a surface facing the front side.

  Hereinafter, when the direction and relative positional relationship of each part of the valve opening / closing timing control device A are described, the bolt head 42 side of the bolt body 41 in the direction along the rotation axis X, that is, the starting point of the internal space 40R. The opening side that becomes is sometimes referred to as the front side. Further, in the direction along the rotational axis X, the side of the male screw portion 41S of the bolt main body 41, that is, the bottom side having the bottom wall 44 serving as the end point of the internal space 40R may be referred to as the rear side. These rear side and front side respectively correspond to the upstream side and the downstream side in the flow direction of the hydraulic oil supplied via the supply flow path 8.

  As shown in FIG. 1, the intake camshaft 5 is formed with a shaft inner space 5R centered on the rotation axis X, and a female screw portion 5S is formed on the inner periphery of the shaft inner space 5R. The shaft inner space 5R communicates with the supply flow path 8 described above.

  With this configuration, in a state where the bolt body 41 is inserted through the annular member 9, the external rotor 20, and the internal rotor 30, the male screw portion 41 </ b> S is screwed into the female screw portion 5 </ b> S of the intake camshaft 5, and the bolt head 42. The inner rotor 30 is fastened to the intake camshaft 5 by the rotation operation. By this fastening, the annular member 9 and the inner rotor 30 are fixed to the intake camshaft 5, and the shaft inner space 5 </ b> R and the connecting bolt 40 communicate with each other.

  As shown in FIG. 2, four drain grooves D (an example of a spatial communication path) are formed in a posture along the rotation axis X in a region reaching the front end from the intermediate position on the inner peripheral surface of the connection bolt 40. The These drain grooves D are formed by shifting the phase by 90 degrees in the circumferential direction around the rotation axis X.

  As shown in FIG. 1, the bolt main body 41 includes an advance port 41 a that communicates with the advance channel 33 and a retard port 41 b that communicates with the retard channel 34 from the outer peripheral surface to the internal space 40 </ b> R. Is formed.

(Valve unit)
As shown in FIGS. 3 to 6, the valve unit Vb is coaxial with the rotation axis X and the sleeve 53 that is fitted in close contact with the inner peripheral surface of the bolt body 41 in the inner space 40 </ b> R of the connection bolt 40. The fluid supply pipe 54 accommodated in the inner space 40R, the inner peripheral surface of the sleeve 53, and the outer peripheral surface of the conduit portion 54T of the fluid supply pipe 54 are slidable in the direction along the rotational axis X while being guided. And a spool 55 to be arranged.

  Further, the valve unit Vb filters a spool spring 56 (an example of an elastic member) as an urging member that urges the spool 55 in the protruding direction, a check valve CV, and hydraulic oil flowing into the check valve CV. The filter part F and the front-end | tip ring 61 are provided.

  The check valve CV includes an opening plate 57 as a valve seat member and a valve plate 58 having a valve body 58a.

  The filtration part F includes a filter unit 59 and a support part 60 of the filter unit 59.

  The tip ring 61 has an outer cylinder part 61a that fits in the inner space 40R, and a wall part 61b that intersects the rotation axis X perpendicularly on the rear side of the outer cylinder part 61a. The wall 61b is formed with an opening 61c centered on the rotation axis X.

[Valve unit: Sleeve]
As shown in FIGS. 3 to 6, the sleeve 53 is a cylindrical member with the rotation axis X as the center. The sleeve 53 is formed with two engaging protrusions 53T protruding outward in the radial direction. Further, the sleeve 53 is bent at the rear side in a posture orthogonal to the rotational axis X, and the end wall 53W is formed by drawing or the like.

  When the engagement protrusion 53T is fitted in the drain groove D, the posture of the sleeve 53 around the rotation axis X is determined, and a state in which a first drain hole 53c and a second drain hole 53d, which will be described later, communicate with the drain groove D. Maintained (see FIG. 9).

  The sleeve 53 has a plurality of advance communication holes 53a that allow the advance port 41a to communicate with the internal space 40R, a plurality of retard communication holes 53b that allow the internal space 40R to communicate with the retard port 41b, and the operation of the internal space 40R. A plurality of first drain holes 53c and second drain holes 53d that discharge oil to the outer surface side of the sleeve 53 are formed in a square hole shape (rectangular shape).

  The advance communication hole 53a and the retard communication hole 53b are formed in parallel in the direction along the rotation axis X at four positions shifted in phase by 90 degrees in the circumferential direction around the rotation axis X. Yes.

  The first drain hole 53c is formed on the rear side in the direction along the rotational axis X in the sleeve 53 with respect to the advance communication hole 53a or the retard communication hole 53b. The first drain holes 53c are formed at two locations in the circumferential direction around the rotation axis X and having different phases between the advance communication hole 53a and the retard communication hole 53b. The two first drain holes 53c are arranged at a phase (position facing each other across the rotation axis X) shifted by 180 degrees in the circumferential direction (hereinafter simply referred to as the circumferential direction) around the rotation axis X. Has been.

  The second drain hole 53d has two different phases in the circumferential direction centering on the direction along the rotation axis X with the advance communication hole 53a, the retard communication hole 53b, and the first drain hole 53c in the circumferential direction. Is formed. The first drain hole 53c and the second drain hole 53d are arranged with a phase shifted by 90 degrees in the circumferential direction (see FIG. 9). The second drain hole 53d is disposed on the rear side in the direction along the rotation axis X with respect to the first drain hole 53c. The two second drain holes 53d are arranged with a phase shifted by 180 degrees in the circumferential direction.

  The engagement protrusion 53T described above is disposed on an extension line in the direction along the rotation axis X with reference to the positions of the two first drain holes 53c facing each other across the rotation axis X.

  With this configuration, the advance communication hole 53a and the advance port 41a communicate with each other by fitting the sleeve 53 with the engagement protrusion 53T being along the drain groove D. Further, the retard communication hole 53b and the retard port 41b communicate with each other. Further, the state where the first drain hole 53c and the second drain hole 53d communicate with the drain groove D is maintained. The second drain hole 53d communicates with a drain groove D different from the drain groove D with which the first drain hole 53c communicates.

[Valve unit: Fluid supply pipe]
As shown in FIGS. 3 to 6, the fluid supply pipe 54 has a base end portion 54S fitted into the internal space 40R and a diameter smaller than the base end portion 54S, and extends from the base end portion 54S toward the front side in the internal space 40R. The exiting pipe line portion 54T is integrally formed. A supply port 54a is formed on the outer periphery of the distal end portion of the pipe line portion 54T. The distal end of the pipe line portion 54T has a bottom surface 54b.

  The base end portion 54S is formed in a fitting cylinder portion 54Sa having a diameter that fits in the internal space 40R with the rotation axis X as a center, and a region extending from the fitting cylinder portion 54Sa to the pipe line portion 54T. The intermediate wall 54Sb and the check valve CV are orthogonal to each other.

  The three supply ports 54a formed on the outer periphery of the distal end portion of the pipe line portion 54T are elongated holes extending in the direction along the rotation axis X, and the four intermediate hole portions 55c formed in the spool 55 are circular. It is. The number of supply ports 54a is different from the number of intermediate hole portions 55c formed in the spool 55, and the opening width in the circumferential direction of the supply port 54a is an intermediate portion of the supply ports 54a adjacent in the circumferential direction (tubes). Since the width of the portion of the passage portion 54T is larger than the width between the supply ports 54a and 54a adjacent to each other in the circumferential direction), the hydraulic oil from the conduit portion 54T reliably operates with respect to the intermediate hole portion 55c. Oil can be supplied.

[Valve unit: spool, spool spring]
As shown in FIGS. 3 to 6, the spool 55 has a cylindrical body 55 a with an operation end 55 s formed at the tip, three land portions R formed in a protruding state on the outer periphery, and a spool 55. A plurality of (four) intermediate hole portions 55c that communicate with the inside are formed. The three land portions R have a first land R1, a second land R2, and a third land R3 in order from the front side to the rear side in the direction along the rotation axis X. The thickness of the third land R3 in the direction along the rotational axis X is relatively thinner than the thickness of the first land R1 or the second land R2.

  The intermediate hole portion 55c is provided at an intermediate position between the first land R1 and the second land R2. Hereinafter, the first land R1 and the second land R2 are collectively referred to as a pair of land portions on the front side. Further, the second land R2 and the third land R3 are collectively referred to as a pair of rear lands.

  A second abutting end 55r that abuts against the end wall 53W and determines an operating limit when the spool 55 is operated in the pushing direction is provided at a rear end of the spool 55 that is opposite to the operation end 55s. Is formed integrally with the third land R3. The second contact end portion 55r is configured to have a smaller diameter than the land portion R at the end portion of the region where the spool body 55a is extended.

  The spool spring 56 is a compression coil type spring. The spool spring 56 is disposed on the front side of the bottom surface 54 b of the pipe line portion 54 </ b> T inside the spool 55. The spool spring 56 urges the operation end portion 55s of the spool 55 from the inside of the spool 55 toward the front with respect to the duct portion 54T with the bottom surface 54b as a fulcrum. Due to the action of this urging force, the spool 55 is maintained at the advance position Pa shown in FIG. 3 with the first land R1 abutting against the wall portion 61b in a state where power is not supplied to the solenoid portion 50 of the electromagnetic unit Va. The first land R1 has a first contact end 55f extending toward the wall 61b, and the first contact end 55f contacts the wall 61b.

  Further, in the valve unit Vb, the positional relationship is set such that the end wall 53W of the sleeve 53 and the intermediate wall 54Sb of the fluid supply pipe 54 are in contact with each other in the direction along the rotational axis X. The end wall 53W and the intermediate wall 54Sb are configured as a seal portion H that prevents the flow of hydraulic oil by increasing the planar accuracy of the end wall 53W and the intermediate wall 54Sb that are in contact with each other.

  In this configuration, the position of the base end portion 54 </ b> S of the fluid supply pipe 54 is fixed by the support portion 60. Therefore, this base end part 54S functions as a retainer.

  Further, the urging force of the spool spring 56 acts on the fluid supply pipe 54 from the bottom surface 54b. As a result, the fluid supply pipe 54 is urged rearward.

〔Check valve〕
As shown in FIGS. 6 and 7, the opening plate 57 and the valve plate 58 constituting the check valve CV are formed of a metal material having the same outer diameter, and supply direction of hydraulic oil (direction from the rear side to the front side) An opening plate 57 is disposed on the upstream side of the valve plate, and a valve plate 58 is disposed on the downstream side of the opening plate 57 at a position in contact with the opening plate 57. In particular, a spring plate material is used for the valve plate 58.

  The opening plate 57 is formed in an annular region around the rotation axis X in a circular arc shape with a pair of flow ports 57a symmetrical about the rotation axis X with a pair of opening beam portions 57c therebetween. In addition, a plurality of groove portions 57b having an arc shape around the rotation axis X are formed in a region surrounding the flow port 57a on the surface (downstream surface) of the opening plate 57 that faces the valve plate 58. .

  The valve plate 58 has a circular valve body 58a centered on the rotation axis X at the center position, an annular portion 58b centered on the rotation axis X on the outer periphery, and the valve body 58a and the annular portion. A spiral spring portion 58 s is provided so as to connect 58 b. The valve body 58a has a larger diameter on the outer diameter side than the annular area where the flow port 57a is formed, and an opening 58c smaller in diameter than the annular area on the inner diameter side. In this configuration, the opening 58 c is formed in a circular shape centered on the rotation axis X. Thereby, the valve body 58a can block | close the flow port 57a, when it closely_contact | adheres to the flow port 57a.

  The valve plate 58 is fixed in the internal space 40R by sandwiching the annular portion 58b between the fitting cylindrical portion 54Sa of the base end portion 54S and the opening plate 57.

  With this configuration, when assembling the check valve CV, the valve plate 58 and the opening plate 57 are simply fitted into the internal space 40R of the connecting bolt 40, and each has an optimum positional relationship. Work becomes unnecessary.

  In the check valve CV, when hydraulic oil is supplied, as shown in FIGS. 3 and 5, the spring 58s is elastically deformed, so that the valve body 58a is separated from the flow port 57a. Allow distribution of hydraulic oil. The valve body 58a swings back and forth in the range up to the intermediate wall 54Sb along the rotation axis X, and allows the hydraulic oil to flow.

  In the check valve CV, when the pressure on the front side which is the downstream side of the check valve CV is relatively higher than the pressure on the rear side which is the upstream side, or the spool 55 is set to the neutral position Pn. In this case, as shown in FIG. 4, the valve body 58a is in close contact with the flow port 57a of the opening plate 57 by the elastic force of the spring portion 58s to close the flow port 57a. As a result, backflow from the downstream side to the upstream side is prevented. In particular, when the flow port 57a is closed by the valve body 58a, since the groove portion 57b is formed in the opening plate 57, the inconvenience that the spring portion 58s is in close contact with the opening plate 57 and is not easily separated is suppressed.

  Since the check valve CV is configured in this way, the size can be reduced. In addition, as shown in FIG. 3, when the check valve CV is in an open state, the hydraulic oil that has flowed through the pair of flow ports 57a formed in the opening plate 57 passes through the opening 58c of the valve body 58a. I can pass. As a result, in the vicinity of the rotational axis X that has passed through the opening 58c, the hydraulic oil flows along the rotational axis X, so that, for example, the hydraulic oil comes into contact with the inner wall of the pipe line portion 54T of the fluid supply pipe 54 to cause pressure loss. The supply of hydraulic oil in a state where pressure loss is suppressed is realized.

  Further, since the opening plate 57 is formed with a pair of flow ports 57a having a symmetric shape with respect to the rotation axis X, the valve body 58a is reliably opened by applying a pressure without bias to the valve body 58a. At the same time, the hydraulic oil that has passed through the pair of flow ports 57a can be fed into the opening 58c of the valve body 58a.

  In particular, since the check valve CV is accommodated in the internal space 40R of the connecting bolt 40, for example, the flow path configuration is simplified compared to the configuration provided outside the connecting bolt 40, and the check valve CV is advanced. Since it is arranged in the vicinity of the flow path communicating with the corner chamber Ca and the retard chamber Cb, the closing operation can be performed with good responsiveness.

〔filter〕
As shown in FIG. 6, the filter unit 59 of the filtration unit F includes a filter medium 59 b made of a net-like member in which a central part of an annular frame body 59 a having an outer diameter equal to that of the opening plate 57 and the valve plate 58 allows hydraulic oil to flow. It is configured with.

  As shown in FIG. 8, the support part 60 of the filtration part F shares an axis center with the rotation axis X (see FIG. 6), and an annular seat part 60 a that is a cylindrical part with an outer diameter that fits into the internal space 40 </ b> R; It is a ring-shaped retainer having a beam portion 60b that divides the opening portion 60e across the opening portion 60e of the annular seat portion 60a. The annular seat portion 60a and the beam portion 60b have the same thickness in the direction along the rotation axis X.

  The support part 60 is formed symmetrically in the thickness direction, that is, in the direction along the rotation axis X. That is, the support part 60 has no distinction between the front and back in the direction along the rotation axis X.

  In the present embodiment, the beam part 60 b is horizontally mounted from one end of the annular seat part 60 a to the other end with respect to the axis of the support part 60 so as to pass through the axis of the support part 60. In the present embodiment, two beam portions 60b orthogonal to each other divide the opening 60e into four division portions.

  The beam portion 60b has a recess 60c provided by cutting out a surface intersecting with the flow direction of the hydraulic oil in the beam portion 60b, that is, the direction along the rotation axis X in the present embodiment. The recess 60c is provided by cutting out in a direction intersecting with the flow direction of hydraulic oil.

  In this embodiment, the recessed part 60c is formed in the rectangular hollow shape each provided in the both sides of the direction along the rotating shaft center X of the beam part 60b. The concave portion 60c is disposed at an intermediate position between the root portion 60f on the annular seat portion 60a side of the beam portion 60b and the intersection 60x where the beam portion 60b intersects the other beam portion 60b. In the present embodiment, a total of eight concave portions 60c are provided on both surfaces of the support portion 60 (beam portion 60b).

  In the present embodiment, the recess 60c is provided by cutting out a region having an area that is approximately half the area of the surface orthogonal to the direction along the rotational axis X of the beam portion 60b between the root portion 60f and the intersection 60x. It has been. Moreover, the recessed part 60c is a recessed part notched by the depth of 1/3 of the thickness of the beam part 60b in the direction in alignment with the rotating shaft center X. As shown in FIG.

  Thus, by providing the recessed part 60c in the beam part 60b, adjacent opening part 60e is connected by the recessed part 60c. Therefore, for example, when the supply of the working fluid to one of the partitioned openings 60e decreases as a result of a part of the filter medium 59b clogging and the working fluid flowing through the filter unit 59, the opening The working fluid is supplied to the opening 60e from the adjacent opening 60e through the recess 60c. As a result, the working fluid can reach each part of the divided opening 60e, and a uniform flow can be formed again.

  The annular seat portion 60a has a recess 60d provided by cutting out a surface intersecting with the flow direction of the hydraulic oil from the inner peripheral side to the outer peripheral side (outward in the radial direction).

  In the present embodiment, the recess 60d is formed as a rectangular depression at each of the intermediate positions of the adjacent root portions 60f in the annular seat 60a. In the present embodiment, recesses that extend from one side in the direction along the rotation axis X toward the other side, extending from the inner peripheral side to the outer peripheral side on both surfaces of the support portion 60 (annular seat portion 60a). One or more 60d are provided (in this embodiment, a total of four on one side and eight on both sides). As the valve unit Vb rotates, the dust contained in the working fluid receives a centrifugal force and moves radially outward. Therefore, by providing the recess 60d, a liquid pool in which the working fluid stays is formed, and a part of the dust contained in the working fluid can be trapped.

  The support portion 60 is fitted into the internal space 40 </ b> R of the connecting bolt 40 between the opening plate 57 and the filter unit 59.

  At this time, the annular seat portion 60a contacts the frame body 59a located on the outer peripheral portion of the filter unit 59 from the downstream side, and supports the filter unit 59 via the frame body 59a. Further, the beam portion 60b contacts and supports the filter medium 59b from the downstream side. Accordingly, even if the working fluid flows into the filter unit 59 and flows through the filter medium 59b, the filter medium 59b of the filter unit 59 is deformed, such as a dent, toward the downstream side due to pressure loss caused by the flow of the working fluid. Absent. Since the filtration part F is comprised in this way, size reduction is attained.

[Assembly of valve unit, check valve and filter fixing]
As shown in FIG. 6, first, the filter unit 59 is inserted from the front side of the internal space 40 </ b> R and brought into contact with the bottom wall 44. Thereafter, the support portion 60, the opening plate 57, the valve plate 58, and the fluid supply pipe 54 are inserted into the internal space 40R in this order and brought into contact with each other.

  In this embodiment, when the support portion 60 and the opening plate 57 are inserted into the internal space 40 </ b> R, one of the two beam portions 60 b of the support portion 60 is connected to the pair of opening plates 57. The opening beam portion 57c and the rotation axis X may be overlapped in the direction view. This is because the flow resistance of the working fluid can be reduced.

  Further, the engagement protrusion 53T of the sleeve 53 is fitted into the drain groove D, the sleeve 53 is inserted into the internal space 40R, and the end wall 53W of the sleeve 53 is brought into contact with the intermediate wall 54Sb of the fluid supply pipe 54.

  Further, the spool spring 56 is inserted into the spool 55 in advance. The spool 55 in a state where the spool spring 56 is inserted is fitted from the outside of the pipe line portion 54T of the fluid supply pipe 54. As a result, the spool 55 and the spool spring 56 are inserted into the internal space 40R.

  Finally, the tip ring 61 is press-fitted into the internal space 40R with the rear side facing. During the press-fitting, the spool body 55a of the spool 55 is inserted into the opening 61c of the tip ring 61, the first contact end 55f is pressed against the wall 61b of the tip ring 61, and the front side of the spool body 55a is pressed. It is assumed that the tip portion protrudes forward from the tip ring 61. Then, the front end ring 61 is press-fitted until it abuts against the stepped portion 45 of the internal space 40R while resisting the biasing force of the spool spring 56 that biases the spool 55 toward the front side.

  When the press-fitting of the tip ring 61 is completed, the tip ring 61 presses the front side end portion of the sleeve 53 to the rear side in the direction along the rotation axis X. At this time, the end wall 53W which is the rear side end portion of the sleeve 53 is in close contact with the intermediate wall 54Sb in a state of pressing the intermediate wall 54Sb, and this portion is configured as the seal portion H.

  In a state where the press-fitting of the tip ring 61 is completed, the spool 55, the spool spring 56, the sleeve 53, the fluid supply pipe 54, and the check are arranged between the tip ring 61 and the bottom wall 44 from the front side to the rear side. The valve CV, the support part 60, and the filter unit 59 are positioned in the internal space 40R. This completes the assembly of the valve unit Vb.

  With the assembly completed, the operation end 55s of the spool 55 is urged rearward along the rotational axis X against the urging force of the spool spring 56, and the urging is released after being urged. Thus, the spool 55 can move rearward or forward along the rotational axis X while sliding the outer periphery of the land portion R to the inner periphery of the sleeve 53.

[Control form of hydraulic oil]
[Advance position]
In this valve opening / closing timing control device A, when power is not supplied to the solenoid unit 50 of the electromagnetic unit Va, the pressing force does not act on the spool 55 from the plunger 51, and the urging force of the spool spring 56 as shown in FIG. Thus, the spool 55 is maintained at a position where the first contact end portion 55f contacts the wall portion 61b.

  The position of the spool 55 is an advance angle position Pa. From the positional relationship between the three land portions R and the advance communication holes 53a and the retard communication holes 53b, the intermediate hole 55c of the spool 55 and the advance communication holes 53a Communicates with each other through a space between the pair of front land portions, and the retard communication hole 53b communicates with a space between the pair of rear land portions.

  As a result, the hydraulic oil supplied from the hydraulic pump P flows from the supply port 54a of the fluid supply pipe 54 through the intermediate hole 55c of the spool 55, the advance communication hole 53a, and the advance port 41a. The supply will begin.

  At the same time, the hydraulic oil in the retard chamber Cb is discharged from the retard port 41b to the space between the pair of rear lands through the retard communication hole 53b.

  The hydraulic oil discharged into the space between the pair of rear lands flows into the first drain hole 53c and is discharged to the outside through the drain groove D from the front end of the connecting bolt 40. At this time, the back pressure of the hydraulic oil discharged to the space between the pair of rear lands acts as a force for urging the second land R2 toward the front side, and against the third land R3. It acts as a force that urges toward the rear side. That is, the force acting on the second land R2 and the force acting on the third land R3 act in opposite directions in the direction along the rotation axis X, and thus cancel each other. Thereby, the spool 55 is not affected by the back pressure of the hydraulic oil discharged into the space between the pair of rear lands. For example, the spool 55 does not receive a force in the direction along the rotation axis X due to the back pressure.

  Further, when the hydraulic oil discharged into the space between the pair of rear land portions flows into the first drain hole 53c and is discharged to the outside from the front end portion of the connecting bolt 40 via the drain groove D, The hydraulic oil and the spool spring 56 are not in direct contact. Therefore, it is possible to suppress deterioration over time such that the spool spring 56 is worn by the flow of the hydraulic oil.

  As a result of supplying and discharging the hydraulic oil, the relative rotational phase is displaced in the advance angle direction Sa.

  In particular, when the lock mechanism L is in the locked state, the hydraulic oil is supplied by setting the spool 55 to the advance position Pa, whereby a part of the hydraulic oil supplied to the advance chamber Ca is advanced. 33 is supplied to the lock mechanism L, and the lock member 25 is detached from the lock recess 23a to realize unlocking.

  In addition, the hydraulic oil discharged into the space between the pair of rear lands is from the gap between the outer periphery of the third land R3 and the inner periphery of the sleeve 53 to the space on the rear side of the third land R3 in the internal space 40R ( Hereinafter, it may leak to the rear side space). However, the hydraulic oil leaking to the rear space flows into the second drain hole 53d and is discharged to the outside through the drain groove D from the front end portion of the connecting bolt 40. Therefore, the hydraulic oil leaking to the rear space does not have any influence on the spool 55. For example, the hydraulic oil leaking to the rear space does not hinder the rearward movement of the spool 55 in the direction along the rotational axis X.

[Neutral position]
By supplying a predetermined electric power to the solenoid unit 50 of the electromagnetic unit Va, the plunger 51 protrudes and the spool 55 can be set to the neutral position Pn shown in FIG. 4 against the urging force of the spool spring 56. It is.

  When the spool 55 is set to the neutral position Pn, the pair of front-side lands have a positional relationship in which the advance communication hole 53a and the retard communication hole 53b of the sleeve 53 are closed. That is, the first land R1 closes the advance communication hole 53a, and the second land R2 closes the retard communication hole 53b. Thereby, hydraulic oil is not supplied and discharged to the advance chamber Ca and the retard chamber Cb, and the relative rotation phase is maintained.

(Delay position)
By supplying electric power exceeding the predetermined electric power described above to the solenoid unit 50 of the electromagnetic unit Va, the plunger 51 further protrudes and the spool 55 can be set to the retard position Pb shown in FIG.

  In this retard angle position Pb, the intermediate hole portion 55c of the spool 55 and the retard angle communication hole 53b have a pair of front land portions because of the positional relationship between the three land portions R and the advance communication holes 53a and the retard communication holes 53b. The advance communication hole 53a is connected to the space between the outer periphery of the spool body 55a and the rear side of the wall portion 61b of the tip ring 61, the outer periphery of the spool body 55a, and the opening 61c. It communicates with the external space through a gap between them.

  As a result, the hydraulic oil supplied from the hydraulic pump P enters the retard chamber Cb from the supply port 54a of the fluid supply pipe 54 via the intermediate hole 55c of the spool 55, the retard communication hole 53b, and the retard port 41b. Supplied.

  At the same time, the hydraulic oil in the advance chamber Ca is discharged from the advance port 41a to the space between the outer periphery of the spool body 55a and the rear side of the wall portion 61b through the advance communication hole 53a.

  The hydraulic oil discharged to the space between the outer periphery of the spool body 55a and the rear side of the wall portion 61b is discharged to the outside through a gap between the outer periphery of the spool body 55a and the opening 61c.

  As a result of supplying and discharging the hydraulic oil, the relative rotational phase is displaced in the retarding direction Sb.

  As described above, it is possible to provide a valve opening / closing timing control device that can accurately control the valve opening / closing timing.

[Another embodiment]

(1) In the above-described embodiment, the connecting bolt 40 has a bolt head 42 formed at the outer end of the bolt main body 41 that is generally cylindrical, and the bolt head 42 of the bolt main body 41 is the other end. The case where the external thread part 41S was formed in the outer periphery of this part was demonstrated. Then, in a state where the bolt body 41 of the connecting bolt 40 is inserted through the annular member 9, the external rotor 20, and the internal rotor 30, the male screw portion 41 </ b> S is screwed into the female screw portion 5 </ b> S of the intake camshaft 5, and the bolt head The case where the internal rotor 30 is fastened to the intake camshaft 5 by rotating the portion 42 has been described.

  However, the connecting bolt 40 does not necessarily require the male screw portion 41S to be formed, and the internal rotor 30 and the intake camshaft 5 are fastened to the male screw portion 41S of the connecting bolt 40 and the intake camshaft 5. It is not restricted to the aspect by screwing of female thread part 5S.

  For example, the connecting bolt 40 is formed with a bolt head 42 having an edge extending outward in the radial direction at the outer end of a bolt main body 41 that is generally cylindrical. 41 can be inserted through the annular member 9, the outer rotor 20, and the inner rotor 30. In this case, the connection (fastening) between the internal rotor 30 and the intake camshaft 5 is, for example, penetrating through the edge of the bolt head 42, the annular member 9, and the internal rotor 30 in the direction along the rotational axis X. A hole is provided, and a female screw portion in the direction along the rotation axis X is provided at a position corresponding to the through hole of the intake camshaft 5, and a fastening bolt (cam bolt) is connected to the edge of the bolt head 42, an annular member 9 and the through hole of the internal rotor 30 are inserted in this order and screwed into the female thread portion of the intake camshaft 5, and the bolt head portion 42 of the connection bolt 40 is crimped to the annular member 9. The annular member 9, the inner rotor main body 31, and the intake camshaft 5 can also be integrated. That is, the internal rotor 30 can be connected to the intake camshaft 5 by the fastening bolt. A plurality of fastening bolts (for example, three) can be used for connection.

(2) In the above embodiment, the first drain hole 53c and the second drain hole 53d are arranged with a phase shifted by 90 degrees in the circumferential direction, and the second drain hole 53d is more than the first drain hole 53c. Also, the case where it is arranged on the rear side in the direction along the rotation axis X has been described.

  However, the first drain hole 53c and the second drain hole 53d are not limited to being provided separately. For example, the first drain hole 53c and the second drain hole 53d can be integrally formed. Specifically, the first drain hole 53c is formed in a long hole whose long axis extends in the direction along the rotation axis X. Then, the movement range in the direction along the rotation axis X of the third land R3 is set within a range overlapping with the elongated hole in the radial direction view. In this way, the space between the pair of rear lands at the advance angle position Pa communicates with the drain groove D through the elongated hole. In the neutral position Pn or the retard position Pb, the rear space communicates with the drain groove D through the elongated hole. Therefore, it is possible to obtain the same effect as the above embodiment.

(3) In the above embodiment, the case where the advance port 41a communicates with the advance channel 33 and the retard port 41b communicates with the retard channel 34 has been described.

  However, the relationship between the advance port 41a and the retard port 41b can be interchanged. When the relationship between the advance port 41a and the retard port 41b is switched, the relationship between the advance position Pa and the retard position Pb is switched.

  Note that the configurations disclosed in the above-described embodiments (including other embodiments, the same applies hereinafter) can be applied in combination with the configurations disclosed in the other embodiments as long as no contradiction arises. The embodiment disclosed in this specification is an exemplification, and the embodiment of the present invention is not limited to this, and can be appropriately modified without departing from the object of the present invention.

  The present invention can be applied to a valve opening / closing timing control device.

1: Crankshaft 5: Intake camshaft (camshaft)
20: External rotor (drive-side rotator)
30: Internal rotor (driven rotor)
33: Advance channel 34: Slag channel 40: Connection bolt (valve case)
40R: Internal space 41: Bolt body 41a: Advance port 41b: Delay port 44: Bottom wall (bottom)
51: Plunger 53: Sleeve 53a: Advance communication hole 53b: Delay communication hole 53c: First drain hole 53d: Second drain hole 54: Fluid supply pipe 54S: Base end part 54T: Pipe line part 54a: Supply port 54b : Bottom surface 55: Spool 55c: Intermediate hole 55s: Operation end 56: Spool spring (elastic member)
A: Valve opening / closing timing control device Ca: Advance chamber Cb: Delay chamber D: Drain groove (space communication passage)
R: Land portion R1: First land R2: Second land R3: Third land Vb: Valve unit X: Rotational axis

Claims (5)

A drive-side rotating body that rotates synchronously with the crankshaft of the internal combustion engine;
A driven-side rotator that is arranged coaxially with the rotational axis of the drive-side rotator and rotates integrally with a valve opening / closing camshaft;
An advance chamber and a retard chamber formed between the drive-side rotor and the driven-side rotor,
A valve unit that is arranged coaxially with the rotation axis and controls supply and discharge of fluid to and from the advance chamber and the retard chamber;
A cylinder having an internal space extending in a direction along the rotation axis, accommodating the valve unit in the internal space, having an opening at one end in the direction along the rotation axis, and having a bottom at the other end A valve case, and
The valve case has an advance port and a retard port communicating with each of the advance chamber and the retard chamber formed from the outer peripheral surface to the internal space,
The valve unit has a base end portion fitted into the bottom side of the internal space, and extends from the base end portion toward the opening side along the rotation axis, and has a smaller diameter and a bottom surface than the base end portion. A fluid supply pipe having a conduit section, and a slide supply arrangement in a direction along the rotation axis in a state guided by the inner peripheral surface of the valve case and the outer peripheral surface of the conduit section of the fluid supply pipe A spool having a cylindrical portion to be
The spool has a first land, a second land, and a third land formed on the outer periphery of the cylindrical portion in order from the opening side toward the bottom side,
A valve opening / closing timing control device for discharging the fluid from the advance chamber or the retard chamber into a space between the second land and the third land. The spool has an operation end at a tip on the opening side of the cylindrical portion,
The elastic member which urges | biases the said operation end part toward the said opening side with respect to the said pipe line part between the said operation end part in the inside of the said cylinder part, and the said bottom face of the said pipe line part. 2. The valve opening / closing timing control device according to 1. The valve unit has a space communication path that is open at one end in the space on the opening side and disposed in a direction along the rotation axis.
The valve opening / closing timing control device according to claim 1 or 2, wherein a space between the third land and the base end is connected to the space communication path. A sleeve provided in contact with the inner peripheral surface of the valve case;
The spool is guided to the inner peripheral surface of the valve case via the inner peripheral surface of the sleeve,
The sleeve has a first drain hole communicating with the outside from the space between the second land and the third land, and a second communicating with the outside from the space between the third land and the base end portion. A drain hole, and
A plurality of the first drain holes and the second drain holes are arranged in different phases in the circumferential direction around the direction along the rotation axis in the sleeve,
A plurality of the space communication passages are formed between the valve case and the sleeve, and each of the space communication passages is provided so as to be connectable to each of the first drain hole and the second drain hole. The valve opening / closing timing control device according to claim 3. The sleeve has an advance communication hole communicating with the advance port from the inner peripheral surface of the sleeve, and a retard communication hole communicating with the retard port from the inner peripheral surface,
The spool is formed at an intermediate position between the first land and the second land, and can be communicated with the advance communication hole or the retard communication hole from the inner peripheral surface of the cylindrical portion by sliding movement of the spool. An intermediate hole,
The valve opening / closing timing control device according to claim 4, wherein the fluid supply pipe has a supply port that is provided on an outer periphery of a distal end portion of the pipe line portion and supplies the fluid from the inside to the intermediate hole portion.

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