JP2019132265A - Valve opening/closing timing controller - Google Patents

Abstract

To provide a valve opening/closing timing controller capable of circulating hydraulic oil between an advance chamber and a retard chamber in a simple structure.SOLUTION: A valve opening/closing timing controller comprises a valve unit Vb configured to set a relative rotation phase between a driving side rotor and a driven side rotor with fluid pressure of a fluid pressure chamber. The valve unit Vb comprises: a fluid supply pipe 54 housed in an internal space 40R of a connection bolt 40; a spool 55 slidably arranged in a state of being guided to an inner peripheral surface of the connection bolt 40 and an outer peripheral surface of a pipe conduit part 54T of the fluid supply pipe 54; and a first check valve CV1. The first check valve CV1 circulates to the fluid supply pipe 54 hydraulic oil discharged from the fluid pressure chamber to a space between the spool 55 and a sleeve 53.SELECTED DRAWING: Figure 3

Description

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

  Patent Document 1 has a hydraulic piston provided with at least two cylinder chambers (advancing and retarding chambers) acting in opposite directions, and external force is applied to the cylinder chamber alternately or in one direction. In addition, there is disclosed a vehicle hydraulic circuit with a prime mover configured such that the hydraulic piston moves due to a differential pressure between the cylinder chambers, and the differential pressure is generated from a hydraulic source such as a hydraulic pump. The hydraulic circuit is used in a camshaft timing adjuster (valve opening / closing timing control device), and in addition to the hydraulic load by the switching device, out of the alternately acting external force, the negative side generated by opening at least one check valve A hydraulic load caused by a force acting on the hydraulic piston is used to move the hydraulic piston.

  The valve opening / closing timing control device described in Patent Document 1 is provided with a check valve in each of the return paths of hydraulic oil from the cylinder chambers acting in opposite directions, and the downstream side of the check valve is connected to the cylinder chamber. It is connected to a pressure supply pipe that supplies hydraulic oil. By providing a check valve, the valve opening / closing timing control device can circulate the hydraulic oil from one cylinder chamber to the other cylinder chamber, and can quickly move the hydraulic oil to the cylinder chamber. it can.

  U.S. Patent No. 6,057,031 can be operated using pressure generated by camshaft torque energy to transmit fluid from one working chamber to another, or at the same time as one working chamber is filled. Describes a variable camshaft timing device (valve opening / closing timing control device) that can be operated through a pressure source of an external fluid to drain the contents in the working chamber, or can be operated using both modes simultaneously Has been.

  The valve opening / closing timing control device described in Patent Document 2 is a spool valve in which a control valve has a spool, and the spool has a cylindrical land that is slidably received in a sleeve inside a bore of a center bolt. And the sleeve has a recess for connecting the plurality of ports to each other. The spool of the valve timing control device has a central passage, and the central passage is divided into a working central passage and an inlet central passage by a recirculation check valve and an inlet check valve provided in the central passage. Has been. This valve opening / closing timing control device can reduce the package size of the valve opening / closing timing control device by providing a recirculation check valve in the central passage.

Special table 2009-530526 gazette JP 2017-048793 A

  The valve opening / closing timing control device described in Patent Document 1 requires a check valve corresponding to each cylinder chamber (advance angle chamber and retard angle chamber) acting in opposite directions, and thus has a complicated structure. This is a problem. The valve opening / closing timing control device described in Patent Document 2 has a complicated structure because a check valve (recirculation check valve and inlet check valve) is arranged inside the spool. In addition, since it is arranged in a narrow space inside the spool, it is inconvenient because the size and shape of the check valve are restricted under the restriction of the space.

  The present invention has been made in view of such a situation, and an object of the present invention is to make the advance chamber and the retard angle with a simple structure in order to quickly move the hydraulic oil to the advance chamber and the retard chamber. An object of the present invention is to provide a valve opening / closing timing control device that realizes circulation of hydraulic oil to and from a chamber.

  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 for controlling fluid supply to and discharge from the advance chamber and the retard chamber, and having an internal space extending in a direction along the rotation axis, the internal space A cylindrical valve case having an opening opened to the outside at one end in a direction along the rotation axis and having a bottom at the other end, the valve unit comprising: The base end portion accommodated on the bottom side of the internal space and the front from the base end portion A fluid supply pipe that extends along the rotational axis toward the opening side and has a conduit portion having a bottom surface that is smaller in diameter than the base end portion, and an inner peripheral surface of the valve case and the fluid supply pipe A spool that is slidably movable in a direction along the rotation axis while being guided by the outer peripheral surface of the pipe line portion, and the valve case is formed from the outer peripheral surface to the inner space. The advance chamber and the retard chamber communicate with the advance chamber and the retard chamber, respectively, and the spool includes a plurality of land portions formed on an outer periphery and a pair of adjacent lands. An intermediate hole portion that is formed at an intermediate position of the portion and can communicate with the advance port or the retard port from the inside by sliding movement of the spool, and the fluid supply pipe is a tip of the pipe portion From the inside The intermediate hole has a supply port for supplying the fluid, and is supplied with fluid from the other side of the base end to the conduit, and the valve case is located on the bottom side of the valve case. At least a part of the fluid discharged from the advance chamber or the retard chamber to the space between the valve case and the spool from the space rather than the base end portion in the internal space. It is in the point which has the 1st check valve which distribute | circulates to the space of the bottom part side.

  According to the above configuration, the spool is disposed in the internal space on the opening side of the valve case as viewed from the base end portion of the fluid supply pipe (hereinafter may be referred to as the opening-side internal space), and is advanced or retarded. The fluid discharged from the corner chamber is discharged into the space between the valve case and the spool, that is, the internal space on the opening side of the valve case as seen from the base end portion of the fluid supply pipe.

  Further, according to the above configuration, the valve case prevents backflow of the fluid discharged from one of the advance chamber or the retard chamber into the space between the valve case and the spool via the first check valve. , It can be returned to the space closer to the bottom than the base end in the internal space.

  Here, the fluid supply pipe receives a supply of fluid to be supplied to the advance chamber or the retard chamber from the space on the bottom side of the base end portion (hereinafter sometimes referred to as the bottom side space) to the pipeline. Therefore, as described above, the fluid discharged from one of the advance chamber or the retard chamber is returned to the bottom side space, that is, circulated to supply the fluid to the other of the advance chamber or the retard chamber. Can be used. Therefore, it is possible to sufficiently supply the fluid to the fluid supply pipe. As a result, the valve opening / closing timing can be switched by quickly displacing the relative phase of the driven-side rotator in the advance direction or the retard direction.

  In particular, when the relative rotational phase can be displaced in the advance direction or retard direction using the rotational energy (so-called cam torque) transmitted from the camshaft, the fluid supply is insufficient. The valve opening / closing timing can be switched by quickly displacing the relative phase of the driven-side rotator in the advance direction or the retard direction while avoiding the above.

  A further characteristic configuration of the valve timing control device according to the present invention is that the internal space is provided from the outside to the camshaft, and the bottom portion is disposed on the camshaft side.

  According to the above configuration, the first check valve is disposed in the internal space (bottom side space) on the camshaft side that is opposite to the internal space (opening side internal space) in which the spool is disposed as viewed from the base end. Is done. Therefore, the size and shape of the check valve are not limited by the shape of the spool, and the structure can be simplified. Further, as described above, since the fluid discharged from the advance chamber or the retard chamber is discharged to the opening side internal space, by providing the first check valve on the camshaft side at the base end portion, A check valve corresponding to each advance chamber or retard chamber is not required, and it can be circulated by one check valve through the opening side internal space.

  In the valve opening / closing timing control device according to the present invention, the base end portion has a supply pipe opening for supplying the fluid from the bottom side toward the inside of the fluid supply pipe, The check valve is configured to supply the fluid from the space between the valve case and the spool to the space on the bottom side of the base end in the internal space through the supply pipe opening. It is in the point where it flows through the inside of the pipe.

  According to the above configuration, the first check valve circulates the fluid discharged to the opening side internal space to the bottom side space, and further circulates the circulated fluid from the bottom side space to the base end portion of the fluid supply pipe. The fluid is supplied to the inside of the fluid supply pipe through the opening. As a result, together with the fluid newly supplied from the bottom side toward the inside of the fluid supply pipe, the fluid discharged from one of the advance chamber or the retard chamber is transferred to the other of the advanced chamber or the retard chamber. Can be supplied.

  The valve opening / closing timing control device according to the present invention is further characterized in that the valve unit includes a space between the valve case and the spool in the internal space, and the bottom portion of the internal space. A space communication path communicating with the space on the side, the space communication path being in communication with the outside of the internal space.

  According to the above configuration, the space communication path communicates with the opening side internal space, the bottom side space, and the outside of the internal space (hereinafter referred to as external space). Thereby, the fluid can be discharged from the opening side internal space to the external space via the space communication path. In addition, the fluid can be circulated from the opening side internal space to the bottom side space via the space communication path and the first check valve.

  The valve opening / closing timing control device according to the present invention is further characterized in that the spool has a valve body that is switched between a state in which the internal space and the outside communicate with each other and a state in which the outside does not communicate with each other by sliding movement of the spool. It is in the point which has in the tip part of the side.

  According to the above configuration, a state in which fluid can be discharged from the opening-side internal space to the external space via the space communication path and the fluid from the opening-side internal space to the external space via the space communication path by slide movement of the spool. It is possible to switch between a state where discharge is not allowed. In addition, in a state where fluid is not allowed to be discharged from the opening-side internal space to the external space via the space communication path, the fluid from the opening-side internal space to the bottom side space via the space communication path and the first check valve It becomes possible to promote the circulation.

  A further characteristic configuration of the valve timing control device according to the present invention includes a second check valve that allows the fluid to flow from the bottom side toward the fluid supply pipe, and the second check valve includes It exists in the point arrange | positioned rather than the said 1st check valve in space in the said bottom part side.

  According to the above configuration, the fluid discharged from the advance chamber or the retard chamber, and the fluid that has passed through the first check valve flows back to the upstream side (bottom side as viewed from the second check valve), It is possible to prevent the fluid supplied to the conduit portion of the fluid supply pipe from flowing back to the upstream side (the bottom side as viewed from the second check valve).

  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 a valve in which an internal space is formed in the direction along the rotation axis from the outside to the camshaft A case, wherein the valve unit is accommodated in the internal space, and the valve unit is fitted to the camshaft side in the internal space and from the base end to the outside in the internal space. Towards the side And a fluid supply pipe having a pipe section having a diameter smaller than that of the base end, and an inner peripheral surface of the valve case and an outer peripheral surface of the pipe section of the fluid supply pipe. The valve case communicates with each of the advance chamber and the retard chamber formed from the outer peripheral surface to the internal space. The spool has an advance port and a retard port, and the spool is formed at a midpoint between a pair of land portions formed on the outer periphery and the pair of land portions, and the advancement from the inside by the sliding movement of the spool. An intermediate hole portion that can communicate with the square port or the retard port, and the fluid supply pipe receives fluid from the camshaft side of the base end portion to the pipe portion, The supply pipe is the tip of the pipe section A supply port that is provided on the outer periphery and supplies the fluid to the intermediate hole portion from the inside, and a space provided between the valve chamber and the spool from the advance chamber or the retard chamber provided in the base end portion. And a first check valve that causes at least a part of the fluid discharged to flow from the outside side of the base end portion to the camshaft side.

  According to the above configuration, the spool is disposed in the internal space on the outer side of the valve case as viewed from the base end portion of the fluid supply pipe (hereinafter sometimes referred to as the external side internal space), and the advance chamber or the slow chamber is arranged. The fluid discharged from the corner chamber is discharged into the space between the valve case and the spool, that is, the internal space on the outer side of the valve case as seen from the base end portion of the fluid supply pipe.

  Further, according to the above configuration, the first check valve for allowing fluid to flow from the outside to the camshaft side at the base end portion of the fluid supply pipe, that is, allowing fluid to flow from the outside to the camshaft side is allowed. A first check valve that shuts off the flow of fluid from the camshaft side to the outside side is provided. As a result, the fluid discharged from one of the advance chamber and the retard chamber is prevented from flowing back through the first check valve provided at the base end portion, and the interior of the valve case is viewed from the base end portion. It can be returned to the camshaft side of the space.

  Here, the fluid supply pipe supplies fluid to be supplied to the advance chamber or retard chamber from the space on the camshaft side of the base end portion (hereinafter sometimes referred to as camshaft side space) to the pipeline section. As described above, the fluid discharged from one of the advance chamber or the retard chamber is viewed from the base end portion and returned to the camshaft side of the valve case, that is, the fluid is advanced by circulating the fluid. It can be used for supply to the other of the chamber or the retarded chamber. Therefore, it is possible to sufficiently supply the fluid to the fluid supply pipe. As a result, the valve opening / closing timing can be switched by quickly displacing the relative phase of the driven-side rotator in the advance direction or the retard direction.

  In particular, when the relative rotational phase can be displaced in the advance direction or retard direction using the rotational energy (so-called cam torque) transmitted from the camshaft, the fluid supply is insufficient. The valve opening / closing timing can be switched by quickly displacing the relative phase of the driven-side rotator in the advance direction or the retard direction while avoiding the above.

  A further characteristic configuration of the valve timing control apparatus according to the present invention is that the first check valve is provided on the camshaft side in the base end portion.

  According to the above configuration, the first check valve is disposed in the internal space on the camshaft side, which is the opposite side to the internal space in which the spool is disposed, when viewed from the base end portion. Therefore, the size and shape of the check valve are not limited by the shape of the spool, and the structure can be simplified. Further, as described above, since the fluid discharged from the advance chamber or retard chamber is discharged to the internal space on the outer side, the first check valve is provided on the camshaft side at the base end portion to advance the fluid. A check valve corresponding to each corner chamber or retard chamber is not required, and it can be circulated by one check valve via the internal space on the outer side.

  In the valve opening / closing timing control device according to the present invention, the base end portion includes a base end partition wall that partitions the external side and the camshaft side in the internal space, and the base end partition The wall has a circulation hole that communicates the external side and the camshaft side, the circulation hole is provided along an outer periphery of the pipe line portion, and the first check valve includes the circulation hole. It has an annular valve plate that closes.

  According to the above configuration, the internal space is partitioned by the base end portion into the external side space and the external side space with the base end portion partition wall and the camshaft side space on the other side.

  Furthermore, according to the said structure, since a base end part partition wall is provided along the outer periphery of a pipe line part, a circulation hole is provided along the outer periphery of a pipe line part. Thereby, the opening part of a circulation hole is arrange | positioned, for example in cyclic | annular form, or is formed as a slit-shaped opening which makes a part of cyclic | annular form or circular arc.

  For this reason, the first check valve is an annular valve plate having an opening corresponding to the pipe line portion and having a simple shape that is formed in a plate shape that closes the circulation hole. In addition, fluid circulation can be realized.

  A further characteristic configuration of the valve opening / closing timing control device according to the present invention is that a second check valve for allowing the fluid to flow from the camshaft side toward the fluid supply pipe is provided.

  According to the above configuration, the fluid discharged from the advance chamber or the retard chamber, and the fluid that has passed through the first check valve flows back upstream or is supplied to the conduit portion of the fluid supply pipe. It is possible to prevent the fluid from flowing back to the upstream side.

  A further characteristic configuration of the valve timing control device according to the present invention is that the valve unit is disposed in both the space on the camshaft side and the space on the external side with respect to the pair of land portions in the internal space. There is a space communication path that communicates, and the space communication path is in communication with the outside of the internal space.

  According to the above configuration, the space communication path communicates with both the space on the camshaft side in the internal space and the space on the external side with respect to the internal space, and further communicates with the outside of the internal space. The space on the camshaft side in the internal space and the space on the external side in the internal space can be communicated with the outside of the internal space via the space communication path.

  As a result, fluid can be exchanged between the two spaces, and the fluid discharged from the advance chamber or retard chamber can be discharged to either the camshaft side space or the external space of the pair of land portions. In this case, the fluid can be used for circulation.

  According to the above configuration, the fluid that has been discharged into the space between the valve unit, the valve casing, and the spool and has not been circulated can be discharged to the outside via the space communication path. .

  A further characteristic configuration of the valve opening / closing timing control device according to the present invention includes a sleeve provided on an inner peripheral surface of the internal space, and the sleeve communicates with the advance port from the inside, and an advance communication hole. A retard communication hole communicating with the retard port from the inside, and the spool is guided to the inner peripheral surface of the valve case via the inner peripheral surface of the sleeve, and the intermediate hole portion is The advance communication port communicates with the advance port, the retard communication port communicates with the retard port, and the space communication path is formed between the valve case and the sleeve. There is in point.

  According to the above configuration, a space communication path can be formed between the valve case and the sleeve. The space communication path can communicate with both the space on the camshaft side in the internal space and the space on the external side in the internal space. Furthermore, since it communicates with the outside of the internal space, the space on the camshaft side in the internal space and the space on the external side in the internal space can be communicated with the outside of the internal space via the space communication path. .

  A further characteristic configuration of the valve opening / closing timing control device according to the present invention includes, as the valve case, a connection bolt that is arranged coaxially with the rotation axis and connects the driven rotary body to the camshaft by a screw portion. The internal space is formed so as to penetrate from the threaded portion of the connecting bolt toward the head.

  According to the above configuration, the valve opening / closing timing control device can be made compact by using the connecting bolt that connects the driven side rotating body to the camshaft as the valve case.

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 the first valve plate Front view of the second valve plate Sectional view of the valve unit of the second embodiment in which the spool is in the advanced position Sectional view of the valve unit of the second embodiment in which the spool is in the neutral position Sectional view of the valve unit of the second embodiment in which the spool is in the retard position Sectional drawing which shows the whole structure of the valve timing control apparatus of 3rd embodiment. Cross section of valve unit with spool in first advance position Cross section of valve unit with spool in second advance position Cross section of valve unit with spool in neutral position Cross section of valve unit with spool in second retard position Cross section of valve unit with spool in first retard position Exploded perspective view of the valve unit of the third embodiment The perspective view of the valve seat of the third check valve of the third embodiment The perspective view of the circulation valve of the third check valve of the third embodiment Explanatory drawing of the modification of 3rd embodiment

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

[First embodiment]
Hereinafter, a first embodiment of a 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 rotating body) is disposed coaxially with the rotation axis X of the intake camshaft 5 and is connected to the intake camshaft 5 by a connecting bolt 40 (an example of a valve case). Connected to the intake camshaft 5. 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. The plunger 51 is arranged coaxially with the rotation axis X so as to be moved out and out by drive control of the solenoid unit 50. 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. In addition, a male screw portion 41S (an example of a screw portion) is formed on the outer periphery of the other end of the bolt main body 41 with respect to the bolt head 42.

  A cylindrical internal space 40 </ b> R that penetrates in the direction along the rotation axis X is formed inside the connecting bolt 40. Thereby, the connecting bolt 40 can accommodate the valve unit Vb in the internal space 40R as a valve case.

  Hereinafter, when the direction and relative positional relationship of each part of the valve opening / closing timing control device A will be described, the male screw part 41S side of the bolt body 41 in the direction along the rotation axis X, that is, the intake camshaft 5 side. May be referred to as the threaded portion side. Further, in the direction along the rotational axis X, the head side is the side facing the electromagnetic unit Va which is the bolt head 42 side of the bolt body 41, that is, the other end side of the intake camshaft 5 side via the connecting bolt 40. Sometimes referred to as the side. Note that the threaded portion side and the head portion side correspond to an upstream side and a downstream side, respectively, in the flow direction of hydraulic oil supplied via the supply flow path 8.

  If it demonstrates based on the structure of the connection bolt 40, the side of the large diameter part 40Rb mentioned later and the side in which the control wall 44 is provided correspond to the screw part side (upstream side) and the head side (downstream side).

  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 FIGS. 4 to 6, a large-diameter portion 40 </ b> Rb is formed on the head side portion of the inner peripheral surface of the internal space 40 </ b> R of the connecting bolt 40.

  Of the inner peripheral surface of the internal space 40R of the connecting bolt 40, the end on the screw portion side in the direction along the rotational axis X projects in a direction close to the rotational axis X (toward the inside of the internal space 40R). A restricting wall 44 is formed. The regulation wall 44 is provided as an annular wall on the inner peripheral surface.

  At the inner periphery of the connecting bolt 40, a plurality (four) of drain grooves D (an example of a space communication path) are positioned along the rotation axis X in a region reaching from the intermediate position to the tip of the large-diameter portion 40 </ b> Rb (connecting bolt 40). Formed with.

  In the bolt main body 41, an advance port 41a communicating with the advance channel 33 and a retard port 41b communicating with the retard channel 34 are formed from the outer peripheral surface to the internal space 40R.

(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 includes a spool spring 56 as a biasing member that biases the spool 55 in the protruding direction, a first check valve CV1, a second check valve CV2, a filter 59, and a fixing ring 60. And a tip ring 61.

  The first check valve CV1 includes a first valve plate 52 having a fluid supply pipe 54, a circulation hole 54b included therein, and an annular valve plate 52a.

  The second check valve CV2 includes an opening plate 57 as a valve seat member and a second valve plate 58 having a valve body 58a.

  The fixing ring 60 includes an outer cylindrical portion 60a that fits in the inner space 40R, an inner cylindrical portion 60b that has a smaller inner diameter than the cylindrical outer cylindrical portion 60a, and an intermediate position in the direction along the rotational axis X in the fixing ring 60. And a wall portion 60c perpendicularly intersecting the rotation axis X. A circular opening 60d centered on the rotation axis X is formed in the wall 60c.

  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 screw part 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 a plurality (two) of engaging protrusions 53 </ b> T protruding from the outer periphery of the cylinder of the sleeve 53 in a direction intersecting with the direction along the rotational axis X from the outer periphery of the sleeve 53. Further, the sleeve 53 is formed by bending the end portion wall 53W by bending the screw portion side in a posture orthogonal to the rotational axis X.

  When the engagement protrusion 53T is fitted into the drain groove D, the posture of the sleeve 53 around the rotation axis X is determined, and a state in which a drain hole 53c and a drain hole 53d, which will be described later, communicate with the drain groove D is maintained.

  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 drain holes 53c for discharging oil to the outer surface side of the sleeve 53 are formed in a square hole shape (rectangular shape). The drain hole 53 c is formed on the screw portion side of the sleeve 53.

  The sleeve 53 has a drain hole 53d on the head side.

  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 locations in the circumferential direction around the rotation axis X.

  The drain holes 53c are formed at four locations having different phases in the advance communication hole 53a and the retard communication hole 53b in the circumferential direction around the rotation axis X.

  The drain holes 53d are formed at four locations that have different phases in the advance communication hole 53a and the retard communication hole 53b in the circumferential direction around the rotation axis X.

  In the circumferential direction, each drain hole 53c and drain hole 53d are provided in pairs in the same phase. That is, the pair of drain holes 53c and the drain holes 53d are arranged side by side in the direction along the rotation axis X.

  The engagement protrusions 53T described above are arranged on an extension line in the direction along the rotation axis X with reference to two of the four drain holes 53c at positions facing each other with the rotation axis X interposed therebetween.

  With this configuration, by fitting the sleeve 53 into the internal space 40R of the connecting bolt 40 with the engaging protrusion 53T being along the drain groove D, the drain groove D of the connecting bolt 40 as a valve case is connected to the connecting bolt 40. 40 and the sleeve 53, and a space communication path surrounded by the inner peripheral surface of the drain groove D and the outer peripheral surface of the sleeve 53 is formed between the connecting bolt 40 and the sleeve 53. it can. Since the drain groove D is formed so as to reach a region reaching the tip of the connection bolt 40, the space communication path is formed to communicate with the outside of the connection bolt 40.

  Further, the advance communication hole 53a and the advance port 41a communicate with each other. Further, the retard communication hole 53b and the retard port 41b communicate with each other. Further, the state in which the drain hole 53c and the drain hole 53d communicate with the drain groove D is maintained.

  Thus, in the valve unit Vb, the space between the sleeve 53 and the spool 55 (the space on the intake camshaft 5 side with respect to the pair of land portions 55b), the spool 55 (the outer periphery of the spool body 55a), and the wall portion 61b. A space between the intake camshaft 5 side (a space on the side facing the electromagnetic unit Va rather than the pair of land portions 55 b) is a drain as a space communication path formed between the connecting bolt 40 and the sleeve 53. It communicates with the groove D.

[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 is directed from the base end portion 54S toward the head side in the internal space 40R. A pipe part 54T that extends in an integrated manner is formed integrally, and a supply port 54a is formed on the outer periphery of the tip part of the pipe part 54T.

  The base end portion 54S has a circular shape with a diameter that fits in the internal space 40R with the rotation axis X as the center, and an intermediate wall 54Sb (an example of a base end partition wall) that is perpendicular to the rotation axis X, and a second reverse It consists of a stop valve CV2. The base end portion 54 </ b> S has a supply pipe opening 54 </ b> Sa that supplies hydraulic oil from the screw portion side toward the inside of the fluid supply pipe 54.

  The three supply ports 54a formed on the outer periphery of the distal end portion of the pipe line portion 54T have a long hole shape extending in the direction along the rotation axis X. Further, the four intermediate hole portions 55c formed in the spool 55 are circular. 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). Of the portion of the path portion 54T, it is formed larger than the width of the portion adjacent to the supply ports 54a, 54a adjacent in the circumferential direction. Thereby, the hydraulic oil from the pipe line part 54T can be reliably supplied with respect to the intermediate hole part 55c.

  A circulation hole 54b that forms a part of the second check valve CV2 is formed in the intermediate wall 54Sb. The circulation hole 54b has a pair of through-holes arranged in a circular arc shape symmetric about the rotation axis X in an annular region centered on the rotation axis X and along the outer periphery of the pipe line portion 54T. . In the present embodiment, the circulation hole 54b is two slit-shaped through holes formed in an arc shape. Details of the second check valve CV2 will be described later.

[Valve unit: spool, spool spring]
As shown in FIGS. 3 to 6, the spool 55 is formed in a cylindrical shape. The spool 55 has a spool body 55a having an operation end 55s formed at the tip. A pair of land portions 55b formed in a protruding state are formed on the outer periphery of the spool body 55a. In addition, a plurality of (four) intermediate hole portions 55c are formed on the outer periphery of the spool body 55a to communicate the intermediate position between the pair of land portions 55b and the inside of the spool 55. A drain through hole 55h that passes through the spool body 55a in a direction intersecting the rotation axis X (orthogonal in the present embodiment) between the operation end 55s and the side of the pair of land portions 55b facing the electromagnetic unit Va. Is provided.

  On the opposite side of the operation end 55s of the spool 55, an abutment end 55r that abuts against the end wall 53W and determines the operation limit when the spool 55 is operated in the pushing direction is integrated with the land portion 55b. It is formed. The contact end portion 55r is configured to have a smaller diameter than the land portion 55b at the end portion of the region where the spool body 55a is extended.

  The spool spring 56 is a compression coil type, and is disposed between the inner land portion 55 b and the end wall 53 </ b> W of the sleeve 53. By the action of this urging force, the spool 55 is maintained at the advance position Pa shown in FIG. 3 with the land portion 55b on the head side contacting the wall portion 61b. The land portion 55b on the head side has a small diameter portion 55d extending toward the wall portion 61b, and the small diameter portion 55d contacts the wall portion 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.

  Note that the end wall 53W is provided apart from the outer peripheral surface of the pipe line portion 54T, and a gap is formed. From the clearance, the hydraulic oil discharged from the advance chamber Ca or the retard chamber Cb to the space between the sleeve 53 and the spool 55 can flow through the circulation hole 54b.

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

  Further, since the biasing force of the spool spring 56 acts on the end wall 53W of the sleeve 53, the end wall 53W presses the intermediate wall 54Sb of the base end 54S.

  Accordingly, by setting the postures so that the end wall 53W and the intermediate wall 54Sb can be in close contact with each other, the biasing force of the spool spring 56 is used to bring the end wall 53W into close contact with the intermediate wall 54Sb. The seal portion H is configured.

[First check valve]
As shown in FIGS. 6 and 7, the base end portion 54S and the first valve plate 52 constituting the first check valve CV1 are formed of a metal material having the same outer diameter, and the intermediate wall is formed on the screw portion side of the intermediate wall 54Sb. The first valve plate 52 is disposed at a position in contact with 54Sb. In particular, a spring plate material is used for the first valve plate 52.

  The first valve plate 52 has an annular annular valve plate 52a centered on the rotation axis X at the center position, an annular portion 52b centered on the rotation axis X on the outer periphery, and the annular valve plate. A spiral spring portion 52s is provided so as to connect 52a and the annular portion 52b. The annular valve plate 52a has an outer diameter side formed with an opening 52c having a larger diameter than the annular region where the circulation hole 54b described above is formed, and an inner diameter side having a smaller diameter than the annular region. In this configuration, the opening 52c is formed in a circular shape with the rotation axis X as the center. Thereby, the annular valve plate 52a can close the circulation hole 54b when the annular valve plate 52a comes into close contact with the circulation hole 54b.

  As shown in FIGS. 3 to 6, the first valve plate 52 is fixed in the internal space 40 </ b> R by sandwiching the annular portion 52 b between the outer cylindrical portion 60 a of the fixing ring 60 and the intermediate wall 54 </ b> Sb.

  With this configuration, when the first check valve CV1 is assembled, the first valve plate 52 is simply fitted into the internal space 40R of the connecting bolt 40 between the fluid supply pipe 54 and the fixing ring 60. Each has an optimal positional relationship, and operations such as positioning become unnecessary.

  As shown in FIGS. 3 and 5, the first check valve CV <b> 1 is shown in FIG. 3 and FIG. 5 when the pressure on the threaded portion side downstream of the first check valve CV <b> 1 is lower than the space between the sleeve 53 and the spool 55. In addition, the spring portion 52s (see FIG. 6) is elastically deformed, so that the annular valve plate 52a is separated from the circulation hole 54b to allow the hydraulic oil to flow. The annular valve plate 52a oscillates back and forth within the inner cylinder portion 60b of the fixed ring 60 along the rotation axis X to the wall portion 60c of the fixed ring 60 to allow the hydraulic oil to flow.

  When the pressure on the screw portion side increases or when the spool 55 is set to the neutral position Pn, the first check valve CV1 is an annular valve by the elastic force of the spring portion 52s as shown in FIG. The plate 52a is in close contact with the circulation hole 54b so as to close the circulation hole 54b. As a result, backflow from the screw portion side to the head portion side is prevented.

  Further, the intermediate wall 54Sb is formed with a pair of circulation holes 54b that are symmetrical with respect to the rotational axis X, so that an even pressure is applied to the annular valve plate 52a to ensure the annular valve plate 52a. The hydraulic fluid that has passed through the pair of intermediate walls 54Sb and has flowed into the screw side space of the intermediate wall 54Sb is sent (circulated) to the fluid supply pipe 54 through the opening 52c of the annular valve plate 52a. It becomes possible.

  By comprising in this way, the 1st non-return valve CV1 can be reduced in size and accommodated in the internal space 40R of the connection bolt 40, using a spring board material. Further, for example, the flow path configuration can be simplified as compared with a configuration in which a check valve is provided outside the connection bolt 40. Further, since the first check valve CV1 is disposed in the vicinity of the flow path communicating with the advance chamber Ca and the retard chamber Cb, the first check valve CV1 can be closed with good response.

(Second check valve)
As shown in FIGS. 6 and 8, the opening plate 57 and the second valve plate 58 constituting the second check valve CV2 are formed of a metal material having the same outer diameter, and are opened upstream in the hydraulic oil supply direction. The plate 57 is disposed, and the second valve plate 58 is disposed at a position in contact with the opening plate 57 on the downstream side. In particular, a spring plate material is used for the second valve plate 58.

  The opening plate 57 is formed in a circular arc shape in which a pair of flow ports 57 a are symmetrical about the rotation axis X in an annular region centered on the rotation axis X. A plurality of groove portions 57b having an arc shape centering on the rotation axis X are formed in a region surrounding the circulation port 57a on the surface of the opening plate 57 facing the second valve plate 58.

  The second 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. A spiral spring portion 58s is provided so as to connect the annular portion 58b. 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 second valve plate 58 is fixed in the internal space 40 </ b> R by sandwiching the annular portion 58 b between the outer cylindrical portion 60 a of the fixing ring 60 and the opening plate 57.

  With this configuration, when the second check valve CV2 is assembled, the second 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. No operation such as positioning is required.

  In the second check valve CV2, when hydraulic oil is supplied, as shown in FIGS. 3 and 5, the spring portion 58s is elastically deformed so that the valve body 58a is separated from the flow port 57a. Thus, the distribution of hydraulic oil is allowed. The valve body 58a swings back and forth inside the inner cylinder portion 60b of the fixing ring 60 along the rotation axis X and up to the wall portion 60c of the fixing ring 60 to allow the hydraulic oil to flow.

  In the second check valve CV2, when the pressure on the head side, which is the downstream side of the second check valve CV2, is increased, when the discharge pressure of the hydraulic pump P is decreased, or when the spool 55 is in the neutral position Pn. 4, the valve body 58a is brought into 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 shown in FIG. 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.

〔filter〕
Further, the filter 59 includes a filtering portion 59b formed of a net-like member in which a central portion of an annular frame body 59a having an outer diameter equal to that of the opening plate 57 and the second valve plate 58 allows hydraulic fluid to flow. .

  The filter 59 is fitted into the internal space 40 </ b> R of the connection bolt 40 with an annular support member 59 c interposed between the opening plate 57 and the filter 59.

  Since the second check valve CV2 is configured in this way, the size can be reduced. Moreover, as shown in FIGS. 3 and 5, when the second check valve CV2 is in an open state, the hydraulic oil that has flowed through the pair of flow ports 57a formed in the opening plate 57 is removed from the valve body 58a. Through the opening 58c and the opening 60d. As a result, at a position in the vicinity of the rotation axis X that has passed through the opening 58c, the hydraulic oil flows along the rotation axis X, so that, for example, the hydraulic oil contacts the inner wall of the pipe line portion 54T of the fluid supply pipe 54, causing 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 second check valve CV2 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 this second check valve is provided. Since the valve CV2 is disposed in the vicinity of the flow path communicating with the advance chamber Ca and the retard chamber Cb, the closing operation can be performed with good responsiveness.

(Valve unit, first check valve, second check valve and filter fixing)
As shown in FIG. 6, first, the filter 59 is inserted from the head side of the internal space 40 </ b> R and brought into contact with the regulation wall 44. Thereafter, the support member 59c, the opening plate 57, the second valve plate 58, the fixing ring 60, the first valve plate 52, and the fluid supply pipe 54 are inserted into the internal space 40R in this order and brought into contact with each other.

  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 and the spool 55 are fitted in this order from the outside of the pipe line portion 54T of the fluid supply pipe 54 and inserted into the internal space 40R.

  Finally, the tip ring 61 is press-fitted into the internal space 40R toward the screw portion side. At the time of this press-fitting, the spool body 55a of the spool 55 is inserted into the opening 61c of the tip ring 61, the land portion 55b at the head side position is pressed against the wall portion 61b of the tip ring 61, and the head of the spool body 55a It is assumed that the distal end portion on the part side protrudes toward the head side from the distal end ring 61. The tip ring 61 is press-fitted into the internal space 40 </ b> R while resisting the biasing force of the spool spring 56 that biases the land portion 55 b at the screw portion side position toward the head side.

  When 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, the first portion between the tip ring 61 and the regulation wall 44 from the head side toward the screw portion side. The check valve CV1, the fixing ring 60, the second check valve CV2, and the filter 59 are positioned in the internal space 40R.

[Control form of hydraulic oil]
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 land portion 55b of the outer side position abuts against the wall portion 61b.

  The position of the spool 55 is an advance angle position Pa. From the positional relationship between the pair of land portions 55b, the advance communication hole 53a and the retard communication hole 53b, the intermediate hole 55c of the spool 55 and the advance communication hole 53a The retard communication hole 53b communicates with the space inside the sleeve 53 (internal space 40R).

  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 sleeve 53 and the spool 55 through the retard communication hole 53b.

  Part of the hydraulic oil discharged to the space between the sleeve 53 and the spool 55 is circulated to the fluid supply pipe 54 via the first check valve CV1. The circulated hydraulic oil is supplied to the advance chamber Ca together with the hydraulic oil supplied from the hydraulic pump P. Due to the circulation of the hydraulic oil, the hydraulic oil is rapidly supplied to the advance chamber Ca.

  The remainder of the hydraulic oil discharged to the space between the sleeve 53 and the spool 55 flows into the drain hole 53c and is discharged to the outside through the drain groove D from the end portion on the head side of the connecting bolt 40.

  As a result of the supply and discharge and circulation of the hydraulic oil, the relative rotational phase is quickly displaced in the advance 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.

  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 land portions 55b are in a positional relationship in which the advance communication hole 53a and the retard communication hole 53b of the sleeve 53 are closed, and the advance chamber Ca and the retard chamber Cb. At the same time, the hydraulic oil is not supplied and discharged and the relative rotational phase is maintained.

  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 the retard position Pb, the intermediate hole portion 55c of the spool 55 and the retard communication hole 53b communicate with each other because of the positional relationship between the pair of land portions 55b, the advance communication hole 53a, and the retard communication hole 53b. Further, the advance communication hole 53a extends from the space between the outer periphery of the spool body 55a and the wall 61b of the tip ring 61 to the intake camshaft 5 side via the drain hole 53d, the drain groove D, and the drain hole 53c. It communicates with the space between the sleeve 53 and the spool 55. At the same time, the advance communication hole 53a communicates with the external space through the drain hole 53d and the drain groove D from the space between the outer periphery of the spool body 55a and the wall portion 61b on the intake camshaft 5 side.

  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. Supply begins.

  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 wall portion 61b on the intake camshaft 5 side via the advance communication hole 53a.

  Part of the hydraulic oil discharged into the space between the outer periphery of the spool body 55a and the wall portion 61b on the intake camshaft 5 side passes through the drain hole 53d, the drain groove D, and the drain hole 53c. It flows into the space between the sleeve 53 and the spool 55. Part of the hydraulic oil that has flowed into the space between the sleeve 53 and the spool 55 is circulated to the fluid supply pipe 54 via the first check valve CV1. The circulated hydraulic oil is supplied to the retard chamber Cb together with the hydraulic oil supplied from the hydraulic pump P. Due to the circulation of the hydraulic oil, the hydraulic oil is quickly supplied to the retard chamber Cb.

  The remainder of the hydraulic fluid discharged to the space between the outer periphery of the spool body 55a and the wall portion 61b on the intake camshaft 5 side is discharged to the outside through the drain hole 53d and the drain groove D.

  As a result of the supply and discharge and circulation of the hydraulic oil, the relative rotational phase is quickly displaced in the retarding direction Sb.

[Second Embodiment]
Hereinafter, a second embodiment of the valve timing control apparatus according to the present invention will be described.

  The second embodiment is different from the first embodiment in that the valve unit Vb does not use the sleeve 53. Moreover, it differs in that the spool 55 has a drain path DL (another example of a space communication path) instead of the drain groove D that the sleeve 53 has in the first embodiment.

  Furthermore, the second embodiment is different from the first embodiment in the shape of the inner peripheral surface of the internal space 40R. In addition, the valve unit Vb includes a rear end ring 62 instead of the front end ring 61, whereby the method and mode of fixing the valve unit Vb and the like are different from those of the first embodiment.

  Other configurations of the second embodiment are the same as those of the first embodiment. Below, these differences are demonstrated and description of a common structure is abbreviate | omitted.

  As shown in FIGS. 9 to 11, a large-diameter portion 40 </ b> Rc is formed in the portion on the screw portion side of the inner peripheral surface of the internal space 40 </ b> R of the connecting bolt 40.

  A restriction wall 45 that protrudes in the direction close to the rotation axis X is formed at the threaded portion side end of the large-diameter portion 40Rb in the connecting bolt 40. The restriction wall 45 is provided on the same plane (same position in the direction along the rotation axis X) as one or a plurality of arc-shaped walls on the inner peripheral surface.

  The rear end ring 62 has an outer cylinder part 62a that fits in the inner space 40R, and a wall part 62b that intersects the rotation axis X perpendicularly on the screw part side of the outer cylinder part 62a. The wall 62b is formed with an opening 62c centered on the rotation axis X.

  As shown in FIGS. 9 to 11, the drain path DL is provided in the spool body 55 a of the spool 55. The drain path DL is a side of the rotational axis X of the spool body 55a that is closer to the electromagnetic unit Va than the pair of land portions 55b than the pair of land portions 55b from the intake camshaft 5 side. It is provided extending until it reaches.

  The drain path DL is a space between the drain hole 93c communicating with the space on the intake camshaft 5 side of the pair of land portions 55b in the internal space 40R, and the spool 55 and the wall portion 61b on the intake camshaft 5 side. A drain hole 93d that communicates with the drain hole 93d.

  In the present embodiment, the drain passage DL is opposed to the operation end 55s and the electromagnetic unit Va of the pair of land portions 55b from a drain hole 93c provided at the end of the spool body 55a of the spool 55 on the intake camshaft 5 side. It is provided in a range up to the drain hole 93d provided in the inner wall of the drain through hole 55h provided between the side and the drain side. The drain hole 93d communicates with the space between the spool 55 and the wall portion 61b on the side of the intake camshaft 5 through the drain through hole 55h.

  That is, the drain path DL communicates with the space on the intake camshaft 5 side of the internal space 40R through the drain hole 93c with respect to the pair of land portions 55b. Moreover, it communicates with the space between the spool 55 and the intake camshaft 5 side of the wall portion 61b in the internal space 40R through the drain hole 93d. The drain channel DL is a tubular channel having the drain hole 93c and the drain hole 93d as open ends.

  Thereby, the space between the pair of land portions 55b on the intake camshaft 5 side and the space between the spool 55 and the wall portion 61b on the intake camshaft 5 side communicate with each other via the drain path DL. Further, the space on the intake camshaft 5 side with respect to the pair of land portions 55b and the space between the spool 55 and the wall portion 61b on the intake camshaft 5 side communicate with the outside via the drain path DL. It has become.

(Valve unit, first check valve, second check valve and filter fixing)
Unlike the case shown in FIG. 6, the spool 55, the spool spring 56, and the fluid supply pipe 54 are inserted into the internal space 40R in this order from the screw portion side. At the time of this insertion, the pair of land portions 55b of the spool 55 abuts against the restriction wall 45 on the screw portion side. Thereby, the spool 55 is prevented from being detached from the head side of the internal space 40R.

  Thereafter, the first valve plate 52, the fixing ring 60, the second valve plate 58, the opening plate 57, the support member 59c, and the filter 59 are inserted in this order from the screw portion side into the large diameter portion 40Rc of the internal space 40R.

  Thereafter, the rear end ring 62 is press-fitted into the large-diameter portion 40Rc from the screw portion side, and the spool 55 and the spool spring are arranged between the regulation wall 45 and the rear end ring 62 from the head side toward the screw portion side. 56, the fluid supply pipe 54, the first check valve CV1, the fixing ring 60, the second check valve CV2, and the filter 59 are positioned in the internal space 40R.

[Control form of hydraulic oil]

  As shown in FIG. 9, when the position of the spool 55 is the advance position Pa, the intermediate hole 55c and the advance angle of the spool 55 are determined from the positional relationship between the pair of land portions 55b and the advance port 41a and the retard port 41b. The port 41a communicates, and the retard port 41b communicates with the space closer to the intake camshaft 5 than the pair of land portions 55b in the internal space 40R.

  Further, at the advance position Pa, the drain through hole 55h of the spool body 55a in the spool 55 communicates only with the outside.

  As a result, hydraulic oil supplied from the hydraulic pump P is started to be supplied from the supply port 54a of the fluid supply pipe 54 to the advance chamber Ca through the intermediate hole 55c of the spool 55 and the advance port 41a.

  At the same time, the hydraulic oil in the retard chamber Cb is discharged from the retard port 41b to the space closer to the intake camshaft 5 than the pair of land portions 55b in the internal space 40R.

  Part of the hydraulic oil discharged into the space closer to the intake camshaft 5 than the pair of land portions 55b in the internal space 40R is circulated to the fluid supply pipe 54 via the first check valve CV1. The circulated hydraulic oil is supplied to the advance chamber Ca together with the hydraulic oil supplied from the hydraulic pump P. Due to the circulation of the hydraulic oil, the hydraulic oil is rapidly supplied to the advance chamber Ca.

  The remainder of the hydraulic oil discharged to the space closer to the intake camshaft 5 than the pair of land portions 55b in the internal space 40R flows into the drain hole 93c of the drain path DL. The remainder of the discharged hydraulic oil further flows from the drain hole 94c to the drain through hole 55h, and is discharged to the outside from the head side end of the connecting bolt 40.

  As shown in FIG. 10, when the spool 55 is set to the neutral position Pn, the pair of land portions 55b are in a positional relationship to close the advance port 41a and the retard port 41b of the bolt body 41, and the advance chamber The hydraulic oil is not supplied to and discharged from Ca and the retard chamber Cb, and the relative rotational phase is maintained.

  As shown in FIG. 11, when the spool 55 is set to the retard position Pb, the intermediate hole portion 55c of the spool 55 is determined from the positional relationship between the pair of land portions 55b and the advance port 41a and the retard port 41b. And the retard port 41b communicate with each other. Further, the advance port 41a extends from the space between the outer periphery of the spool body 55a and the wall portion 61b of the tip ring 61 to the intake camshaft 5 side through the drain hole 93d, the drain path DL, and the drain hole 93c. The space 40R communicates with the space closer to the intake camshaft 5 than the pair of land portions 55b.

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

  Further, the drain through hole 55h of the spool body 55a in the spool 55 communicates with a space between the outer periphery of the spool body 55a and the wall portion 61b on the intake camshaft 5 side.

  Therefore, in the retard position Pb, the advance port 41a passes through the drain through hole 55h, the drain hole 93d, and the drain path DL from the space between the outer periphery of the spool body 55a and the wall portion 61b on the intake camshaft 5 side. It communicates with the external space through.

  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 wall portion 61b on the intake camshaft 5 side.

  Part of the hydraulic oil discharged into the space between the outer periphery of the spool body 55a and the wall 61b on the intake camshaft 5 side is drain drain hole 55h, drain hole 93d, drain path DL, and drain. The air flows into the space closer to the intake camshaft 5 than the pair of land portions 55b in the internal space 40R through the hole 93c.

  Part of the hydraulic oil that has flowed into the space closer to the intake camshaft 5 than the pair of land portions 55b in the internal space 40R is circulated to the fluid supply pipe 54 via the first check valve CV1. The circulated hydraulic oil is supplied to the retard chamber Cb together with the hydraulic oil supplied from the hydraulic pump P. Due to the circulation of the hydraulic oil, the hydraulic oil is quickly supplied to the retard chamber Cb.

  The remainder of the hydraulic fluid discharged to the space between the outer periphery of the spool body 55a and the wall portion 61b on the intake camshaft 5 side is discharged to the outside through the gap between the spool 55 and the connecting bolt 40.

  As described above, the valve opening / closing timing control device according to the present embodiment can realize the circulation of the hydraulic oil between the advance chamber and the retard chamber with a simple structure.

[Third embodiment]
Hereinafter, a third embodiment of the valve timing control apparatus according to the present invention will be described. The third embodiment will be described with reference to FIGS.

[Basic configuration]
Compared with the configuration of the valve unit Vb of the first embodiment, the configuration of the valve unit Vb of the third embodiment mainly includes a sleeve 53, a fluid supply pipe 54, a spool 55, a spool spring 56, a first check valve CV1, and a first check valve CV1. The form of the two check valve CV2 is different. Further, instead of the tip ring 61, a first tip ring 63 and a second tip ring 64 are provided. In particular, the control form of the hydraulic oil differs depending on the form of the spool 55.

  Below, the structure corresponding to 1st check valve CV1 of 1st embodiment is described as 3rd check valve CV3 (an example of 1st check valve). Similarly, a configuration corresponding to the second check valve CV2 is described as a fourth check valve CV4 (an example of a second check valve).

  In this embodiment, the side where the regulation wall 44 is provided in the connecting bolt 40 (an example of a valve case) is the bottom. A large-diameter portion 40Rb on the other end side of the bottom in the direction along the rotation axis X of the connecting bolt 40 is an opening. The screw part side (upstream side) and the head part side (downstream side) of the connecting bolt 40 are a large diameter part 40Rb side (an example of an opening side) and a side on which a regulation wall 44 is provided (an example of a bottom part side). Corresponds.

  Other configurations of the valve timing control device A of the third embodiment are the same as those of the first embodiment. Below, these differences are demonstrated and description of a common structure is abbreviate | omitted.

(Valve unit)
As shown in FIGS. 12 to 17, the valve unit Vb is coaxial with the rotation axis X and the sleeve 53 fitted in a state of being 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 includes a spool spring 56 as a biasing member that biases the spool 55 in the protruding direction, a third check valve CV3, a fourth check valve CV4, a filter 59, a first tip ring. 63 and a second tip ring 64. Unlike the first embodiment, the spool spring 56 is housed inside the cylinder of the spool 55. The mode of the spool spring 56 will be described later.

  As shown in FIGS. 19 and 20, the third check valve CV <b> 3 includes a valve seat 70, a circulation valve 71, and a spring 73.

  The fourth check valve CV4 includes a support plate 65 as a valve seat member and a second valve plate 58 having a valve body 58a.

  The valve seat 70 includes an outer cylinder part 70a that fits in the inner space 40R, and a head side in the direction along the rotation axis X of the outer cylinder part 70a (hereinafter simply referred to as the head side as in the first embodiment). An inner cylinder part 70b having a smaller inner diameter than a cylindrical outer cylinder part 70a that is reduced in diameter from the end part and extends toward the head part, and a head of the inner cylinder part 70b that extends from the head side of the inner cylinder part 70b. And a support leg 70c extending to the part side. Three support legs 70c are provided at equal intervals in the circumferential direction of the rotation axis X (hereinafter simply referred to as the circumferential direction).

  The first tip ring 63 includes an outer ring 63a that fits into the large-diameter portion 40Rb in the inner space 40R, an inner ring 63b that is formed inside the outer ring 63a, and a rotational axis X on the head side of the first tip ring 63. A surface portion 63c that is a surface that intersects the outer ring 63a and the inner ring 63b, and a plurality of tip ring drain holes 63d that are a plurality of through holes that penetrate the surface portion 63c. Six tip ring drain holes 63d are provided at equal intervals in the circumferential direction.

  The second tip ring 64 is an annular cylindrical portion 64a that fits into the large-diameter portion 40Rb in the internal space 40R, and a surface that extends radially inward from the inner peripheral surface of the annular cylindrical portion 64a and is along the rotational axis X. And an annular lid portion 64b which is an annular surface having a through hole in the direction.

[Valve unit: Sleeve]
As shown in FIGS. 13 to 17, the sleeve 53 is a cylindrical member centering on the rotation axis X. The sleeve 53 is formed by drawing the end wall 53w by bending the screw part side in a posture orthogonal to the rotational axis X.

  In the third embodiment, the drain groove D is formed to a position where it can communicate with the end space 53w and the internal space 40R on the screw portion side with respect to an intermediate wall 54Sb described later. A drain hole 53c, a second drain hole 53g, and a recess 53e, which will be described later, communicate with the drain groove D.

  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 drain holes 53c and second drain holes 53g for discharging oil to the outer surface side of the sleeve 53 are formed in a square hole shape (rectangular shape). Further, the sleeve 53 is formed with four tip convex portions 53f extending from the cylindrical portion of the sleeve 53 to the head side along the rotational axis X, and a concave portion 53e is formed between the tip convex portions 53f. Is formed. The tip convex portion 53f and the concave portion 53e are arranged in the same shape and at equal intervals in the circumferential direction.

  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 drain hole 53 c is formed on the screw portion side of the sleeve 53. The drain hole 53c is formed closer to the threaded portion in the direction along the rotational axis X in the sleeve 53 than the advance communication hole 53a to the retard communication hole 53b. The drain holes 53c are formed at two locations in the circumferential direction centering on the rotation axis X and having different phases between the advance communication hole 53a and the retard communication hole 53b. The two drain holes 53c are arranged at phases (positions facing each other across the rotation axis X) shifted by 180 degrees in the circumferential direction around the rotation axis X (hereinafter simply referred to as the circumferential direction). Yes.

  The second drain holes 53g are formed at two locations having different phases in the circumferential direction between the advance communication hole 53a, the retard communication hole 53b, and the drain hole 53c. The second drain holes 53g are arranged in different phases in the circumferential direction centering on the direction along the drain hole 53c and the rotation axis X. The drain hole 53c and the second drain hole 53g are arranged with a phase shifted by 90 degrees in the circumferential direction. The second drain hole 53g is disposed closer to the screw portion in the direction along the rotational axis X than the drain hole 53c. The two second drain holes 53g are arranged with a phase shifted by 180 degrees in the circumferential direction.

  From this configuration, by fitting the sleeve 53, the advance communication hole 53a and the advance port 41a communicate with each other. Further, the retard communication hole 53b and the retard port 41b communicate with each other. Further, the state in which the opening portion by the drain hole 53c, the second drain hole 53g, and the recess 53e communicates with the drain groove D is maintained. The opening part by the recessed part 53e is mentioned later. The second drain hole 53g communicates with a drain groove D different from the drain groove D with which the drain hole 53c communicates.

[Valve unit: Fluid supply pipe]
As shown in FIGS. 13 to 17, the fluid supply pipe 54 has an intermediate wall 54Sb inserted on the screw portion side in the internal space 40R and a smaller diameter than the intermediate wall 54Sb, and from the intermediate wall 54Sb to the head side in the internal space 40R. A pipe line portion 54T extending toward the front is integrally formed. A supply port 54a is formed on the outer periphery of the distal end portion of the pipe line portion 54T. At the tip of the pipe line portion 54T, a bottomed cylindrical projection 54t having a cylindrical portion in the direction along the rotation axis X and having a bottom surface on the head side is formed.

[Valve unit: spool, spool spring]
As shown in FIG. 13 to FIG. 17, the spool 55 has a cylindrical main body 55 a having 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. It has four intermediate hole portions 55c for communicating with the inside, and a tip valve 55v (an example of a valve body) formed between the operation end portion 55s and the land portion R.

  The three land portions R have a first land R1, a second land R2, and a third land R3 in order from the head side to the screw portion 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 tip valve 55v is formed in a rib shape extending radially outward on the outer periphery of the spool body 55a. The rib of the tip valve 55v is formed in an annular surface shape. The tip valve 55v is an annular plate that intersects the rotational axis X. The shape of the outer periphery of the rib of the tip valve 55v is a shape that follows the shape of the inner periphery of the annular lid portion 64b.

  Between the operation end 55s and the side of the first land R1 facing the electromagnetic unit Va, there is a drain through-hole 55h that penetrates the spool body 55a in a direction intersecting with the rotation axis X (orthogonal in the present embodiment). Is provided.

  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 adjacent to the first land R1 are collectively referred to as a pair of land portions on the head side. The pair of front land portions correspond to the pair of land portions 55b of the first embodiment. The second land R2 and the third land R3 are collectively referred to as a pair of land portions on the screw portion side.

  At the head side end of the spool 55 opposite to the operation end 55s, there is a contact end 55r that contacts the end wall 53w and determines the operation limit when the spool 55 is operated in the pushing direction. It is formed integrally with the third land R3. The 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 inside the spool 55 on the head side of the protrusion 54t of the pipe line portion 54T. A protrusion 54t is inserted inside the coil on the screw portion side of the spool spring 56. The spool spring 56 urges the operation end portion 55s of the spool 55 from the inside of the spool 55 toward the head side with respect to the duct portion 54T with the protrusion 54t as a fulcrum. In the state where electric power is not supplied to the solenoid unit 50 of the electromagnetic unit Va by the action of the urging force, the surface of the spool 55 on the head side of the tip valve 55v comes into contact with the end of the threaded portion of the inner ring 63b. The first advance angle position Pa1 shown in FIG.

  Further, in this valve unit Vb, the positional relationship is set so that the end wall 53w of the sleeve 53 and the intermediate wall 54Sb of the base end 54S of the fluid supply pipe 54 abut each other in the direction along the rotational axis X. ing. 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 contact in this way. Note that the threaded portion side of the intermediate wall 54Sb is in contact with the support 70c of the valve seat 70. Further, the urging force of the spool spring 56 acts on the fluid supply pipe 54 from the protrusion 54t. As a result, the fluid supply pipe 54 is urged toward the screw portion.

[Third check valve]
As shown in FIGS. 14 to 17, the third check valve CV <b> 3 includes a valve seat 70, a circulation valve 71, and a spring 73. The third check valve CV3 has a configuration in which the circulation valve 71 is biased toward the head side by a spring 73 fitted outside the inner cylindrical portion 70b of the valve seat 70.

  The circulation valve 71 has a cylindrical portion 71a that can be fitted and slid in the internal space 40R, and a front surface portion 71b that extends in a planar shape radially inward from the head side of the cylindrical portion 71a. The front surface portion 71b contacts the screw portion side of the intermediate wall 54Sb in a state where the circulation valve 71 is urged most toward the head side. The circulation valve 71 closes the threaded portion side end of the drain groove D with the cylindrical portion 71a and the front surface portion 71b in a state where the front surface portion 71b is in close contact with the threaded portion side of the intermediate wall 54Sb, and The internal space 40R closer to the screw portion than 53w and an intermediate wall 54Sb to be described later is closed. In this state, the hydraulic oil does not flow from the inner space 40R closer to the screw portion than the end wall 53w and the intermediate wall 54Sb described later to the drain groove D.

  In the third check valve CV3, the pressure of the hydraulic oil in the internal space 40R on the screw portion side of the end wall 53w and the intermediate wall 54Sb on the downstream side of the third check valve CV3 is the pressure of the hydraulic oil in the drain groove D. 14 and 16, the hydraulic oil in the drain groove D urges the circulation valve 71 against the urging force of the spring 73 toward the threaded portion. As a result, the circulation valve 71 moves backward toward the screw portion side, and allows the hydraulic oil to flow from the drain groove D to the inner space 40R on the screw portion side from the end wall 53w and an intermediate wall 54Sb described later.

  As will be described later, in the third check valve CV3, when the pressure on the screw portion side increases, or the spool 55 is set to the neutral position Pn, the first advance position Pa1, and the first retard position Pb1. In this case, as shown in FIGS. 13, 15, and 17, the circulation valve 71 closes the drain groove D by the elastic force of the spring 73. As a result, backflow from the screw portion side to the head portion side is prevented.

[Fourth check valve]
As shown in FIGS. 13 to 18, the fourth check valve CV4 is different from the second check valve CV2 of the first embodiment, and includes the opening plate 57 and the support member 59c instead of including the opening plate 57 and the support member 59c. The support plate 65 has a configuration in which the member 59c is formed integrally with the member 59c.

  As shown in FIG. 18, the support plate 65 has an arcuate shape in which a pair of flow ports 57 a are symmetrical about the rotation axis X in an annular region centered on the rotation axis X as in the case of the opening plate 57. It is made. 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 (head side surface) of the support plate 65 facing the second valve plate 58. Has been. On the screw part side of the support plate 65, a support member 59c is provided so as to extend in a rib shape from the outer periphery of the support plate 65 to the screw part side.

  The second valve plate 58 is the same as that of the second valve plate 58 (FIG. 8) of the first embodiment, but the annular portion 58b includes the outer cylinder portion 70a of the valve seat 70, the support plate 65, and the like. It is different in that it is sandwiched by and fixed in the internal space 40R. The valve body 58a swings back and forth inside the outer cylindrical portion 70a of the valve seat 70, and allows the hydraulic oil to flow.

  In the fourth check valve CV4, when the pressure on the head side which is the downstream side of the fourth check valve CV4 is relatively increased, or when the spool 55 is set to the neutral position Pn, FIG. As shown in FIG. 5, the valve body 58a is brought into close contact with the elastic force of the spring portion 58s so as to close the flow port 57a of the support plate 65, thereby closing the flow port 57a.

(Valve unit, first check valve, second check valve and filter fixing)
As shown in FIG. 18, first, the filter 59 is inserted from the head side of the internal space 40 </ b> R and brought into contact with the regulation wall 44. Thereafter, the support plate 65, the second valve plate 58, the valve seat 70, the spring 73, the circulation valve 71, and the fluid supply pipe 54 are inserted into the internal space 40R in this order and brought into contact with each other.

  Further, 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.

  Next, the second tip ring 64 is fitted into the large diameter portion 40Rb. At this time, the tip convex portion 53 f is brought into contact with the screw portion side of the annular lid portion 64 b of the second tip ring 64.

  Finally, the first tip ring 63 is press-fitted into the large diameter portion 40Rb toward the screw portion side. At the time of this press-fitting, the spool body 55a of the spool 55 is inserted into the inner ring 63b of the first tip ring 63, and the tip valve 55v of the spool 55 is pressed against the end surface of the inner ring 63b on the threaded portion side. The operation end 55s is accommodated inside the inner ring 63b of the first tip ring 63 in the direction along the rotation axis X. Then, while resisting the biasing force of the spool spring 56 that biases the spool 55 toward the head, the first tip ring 63 is moved to the large-diameter portion 40Rb until the second tip ring 64 hits the back of the large-diameter portion 40Rb. Press fit into.

  When the press-fitting of the first tip ring 63 is completed, the second tip ring 64, the spool 55, the spool spring 56, between the first tip ring 63 and the restriction wall 44 from the head side toward the screw portion side, The sleeve 53, the fluid supply pipe 54, the third check valve CV3, the fourth check valve CV4, and the filter 59 are positioned in the internal space 40R.

[Control form of hydraulic oil]
In the third embodiment, a predetermined power is supplied to the solenoid portion 50 of the electromagnetic unit Va to cause the plunger 51 to project and move the spool 55 to the screw portion side against the urging force of the spool spring 56. Thus, as will be described later, the first advance position Pa1, the second advance position Pa2, the neutral position Pn, the second retard position Pb2, and the first retard position Pb1 can be arbitrarily switched.

[Advance position]
[First advance angle position]
In this valve opening / closing timing control device A, in the state where electric 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 tip valve 55v comes into contact with the end surface of the inner ring 63b on the screw portion side.

  The position of the spool 55 is a first advance angle position Pa1, and the intermediate hole portion 55c of the spool 55 and the advance angle communication hole are determined from the positional relationship between the three land portions R and the advance angle communication holes 53a and the retard angle communication holes 53b. 53a communicates with the space between the pair of front lands, and the retard communication hole 53b communicates with the space between the pair of rear lands.

  In the first advance angle position Pa1, the tip valve 55v is located on the head side with respect to the annular lid portion 64b. Further, the annular lid portion 64b and the tip valve 55v do not overlap when viewed in the radial direction. That is, the space between the annular lid portion 64b and the tip valve 55v is open. Accordingly, the hydraulic oil can flow between the annular lid portion 64b and the tip valve 55v in the direction along the rotation axis X.

  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 start.

  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.

  The hydraulic oil discharged into the space between the pair of rear lands flows into the drain hole 53c, and further, the drain groove D, an opening formed by the recess 53e and the annular lid 64b from the drain groove D, the annular lid It flows through the gap between 64b and the tip valve 55v, and is discharged to the outside from the end on the head side of the connecting bolt 40. At this time, the back pressure of the hydraulic oil discharged into the space between the pair of rear lands acts as a force for urging the second land R2 toward the head, and against the third land R3. It acts as a force that urges toward the screw 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 to the space between the pair of rear lands flows into the 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 is discharged. 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 the first advance angle position Pa1, the hydraulic oil discharged into the space between the pair of rear lands is the first in the internal space 40R through the gap between the outer periphery of the third land R3 and the inner periphery of the sleeve 53. In some cases, leakage may occur in the space on the screw portion side of the three lands R3 and the space on the head side of the end wall 53w (hereinafter simply referred to as the screw portion side space). However, the hydraulic oil leaking to the screw side space flows into the second drain hole 53g and is discharged to the outside from the end portion on the head side of the connecting bolt 40 through the drain groove D and the like. Therefore, the hydraulic oil leaking into the screw portion side space does not have any influence on the movement of the spool 55. For example, the movement of the spool 55 in the direction along the rotational axis X of the spool 55 to the screw portion side is not hindered by the hydraulic oil leaking to the screw portion side space.

(Second advance position)
By supplying a predetermined power to the solenoid unit 50 of the electromagnetic unit Va, the plunger 51 is slightly protruded from the first advance angle position Pa1, and the spool 55 is screwed against the urging force of the spool spring 56. The second advance angle position Pa2 shown in FIG. 14 can be set.

  In the second advance angle position Pa2, the annular lid portion 64b and the tip valve 55v overlap in the radial direction, and the annular lid portion 64b and the tip valve 55v are closed. Accordingly, the hydraulic oil cannot flow between the annular lid portion 64b and the tip valve 55v in the direction along the rotation axis X. Note that, at the second advance position Pa2, the tip valve 55v is located slightly on the head side with respect to the annular lid portion 64b.

  Similarly to the first advance position Pa1, the second advance angle position Pa2 also advances from the intermediate hole 55c of the spool 55 from the positional relationship between the three land portions R and the advance communication holes 53a and the retard communication holes 53b. The corner communication hole 53a communicates with the space between the pair of front land portions, and the retard communication hole 53b communicates with the 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.

  The hydraulic oil discharged into the space between the pair of rear lands flows into the drain hole 53c and flows out into the drain groove D. The hydraulic fluid that has flowed out flows through the drain groove D toward the internal space 40R closer to the screw portion than the end wall 53w and the intermediate wall 54Sb.

  If the pressure (back pressure) of the hydraulic oil flowing through the drain groove D is higher than the pressure of the hydraulic oil flowing through the internal space 40R on the screw portion side than the end wall 53w and the intermediate wall 54Sb, the drain groove D Based on the differential pressure between the hydraulic pressure of the flowing hydraulic oil and the hydraulic pressure of the hydraulic oil flowing through the internal space 40R closer to the screw portion than the end wall 53w and the intermediate wall 54Sb, the circulation valve 71 is used as the biasing force of the spring 73. A force for urging against the screw portion is generated. Thereby, the circulation valve 71 is separated from the screw portion side of the intermediate wall 54Sb, and the drain groove D communicates with the end space 53w and the internal space 40R on the screw portion side of the intermediate wall 54Sb. Then, the hydraulic oil flowing through the drain groove D is supplied to the fluid supply pipe 54 through the supply pipe opening 54Sa. That is, the hydraulic oil discharged into the space between the pair of rear lands is circulated to the fluid supply pipe 54. The circulated hydraulic oil is supplied to the advance chamber Ca together with the hydraulic oil supplied from the hydraulic pump P. Due to the circulation of the hydraulic oil, the hydraulic oil is rapidly supplied to the advance chamber Ca.

  Further, when the hydraulic oil discharged into the space between the pair of rear lands flows into the drain hole 53c and is circulated to the fluid supply pipe 54 via the drain groove D, the hydraulic oil and the spool spring 56 are directly connected to each other. Do not touch. Therefore, it is possible to suppress deterioration over time such that the spool spring 56 is worn due to the circulation of the hydraulic oil.

  As a result of the supply and discharge of the hydraulic oil and the circulation, the relative rotational phase is displaced in the advance direction Sa.

[Neutral position]
By supplying 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. 15 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 head-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.

  Even at the neutral position Pn, the annular lid 64b and the tip valve 55v overlap in the radial direction, and the annular lid 64b and the tip valve 55v are closed. Accordingly, the hydraulic oil cannot flow between the annular lid portion 64b and the tip valve 55v in the direction along the rotation axis X. In the neutral position Pn, the tip valve 55v and the annular lid portion 64b are approximately at the same position in the direction along the rotation axis X.

(Delay position)
[Second retard 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 is further protruded than in the neutral position Pn, and the spool 55 is moved to the second retard position Pb2 shown in FIG. Can be set.

  In the second retard angle position Pb2, the intermediate hole portion 55c of the spool 55 and the retard angle communication hole 53b are paired with a front pair because of the positional relationship between the three land portions R, the advance angle communication hole 53a, and the retard angle communication hole 53b. The advance communication hole 53a communicates with the space between the first land R1 and the tip valve 55v through the space between the land portions.

  In the second retard position Pb2, the annular lid portion 64b and the tip valve 55v overlap in the radial direction, and the annular lid portion 64b and the tip valve 55v are closed. Accordingly, the hydraulic oil cannot flow between the annular lid portion 64b and the tip valve 55v in the direction along the rotation axis X. Note that, at the second retard angle position Pb2, the tip valve 55v is positioned slightly on the screw portion side with respect to the annular lid portion 64b.

  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 first land R1 and the tip valve 55v through the advance communication hole 53a.

  The hydraulic oil discharged into the space between the first land R1 and the tip valve 55v flows out into the drain groove D through an opening formed by the recess 53e and the annular lid portion 64b. The hydraulic fluid that has flowed out flows through the drain groove D toward the internal space 40R closer to the screw portion than the end wall 53w and the intermediate wall 54Sb.

  If the pressure (back pressure) of the hydraulic fluid flowing through the drain groove D is higher than the pressure of the hydraulic fluid flowing through the internal space 40R on the screw side of the end wall 53w and the intermediate wall 54Sb, the second advance angle As in the case of the position Pa2, the hydraulic oil discharged into the space between the first land R1 and the tip valve 55v is circulated to the fluid supply pipe 54. The circulated hydraulic oil is supplied to the retard chamber Cb together with the hydraulic oil supplied from the hydraulic pump P. Due to the circulation of the hydraulic oil, the hydraulic oil is quickly supplied to the retard chamber Cb.

[First retard 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 than in the case of the second retard position Pb2, and the spool 55 is moved to the first delay shown in FIG. It is possible to set the corner position Pb1.

  In the first retard position Pb1, as in the case of the second retard position Pb2, the intermediate hole portion of the spool 55 is determined from the positional relationship between the three land portions R and the advance communication hole 53a and the retard communication hole 53b. 55c and the retard communication hole 53b communicate with each other via a space between the pair of front land portions, and the advance communication hole 53a communicates with a space between the first land R1 and the tip valve 55v.

  In the first retard position Pb1, the tip valve 55v is located closer to the screw part than the annular lid part 64b. Further, the annular lid portion 64b and the tip valve 55v do not overlap when viewed in the radial direction. That is, the space between the annular lid portion 64b and the tip valve 55v is open. Accordingly, the hydraulic oil can flow between the annular lid portion 64b and the tip valve 55v in the direction along the rotation axis X.

  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 first land R1 and the tip valve 55v through the advance communication hole 53a.

  The hydraulic oil discharged into the space between the first land R1 and the tip valve 55v flows through the gap between the annular lid portion 64b and the tip valve 55v, and is discharged to the outside from the end portion on the head side of the connecting bolt 40. The At this time, the back pressure of the hydraulic oil discharged into the space between the first land R1 and the tip valve 55v acts as a force that urges the tip valve 55v toward the head side, and the first land R1. It acts as a force that urges toward the screw part side. That is, the force acting on the tip valve 55v and the force acting on the first land R1 act in opposite directions in the direction along the rotation axis X, and thus cancel each other. Therefore, the influence of the back pressure that the spool 55 receives from the hydraulic oil discharged into the space between the first land R1 and the tip valve 55v is reduced. For example, the force that the spool 55 receives in the direction along the rotational axis X due to the back pressure is reduced.

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

[Modification of Third Embodiment]
Hereinafter, a modification of the third embodiment of the valve timing control apparatus according to the present invention will be described. This embodiment will be described with reference to FIG.

  In the third embodiment, as the fourth check valve CV4, the second valve plate 58 and the support plate 65 are used, and the annular portion 58b of the second valve plate 58 is replaced with the outer cylinder portion 70a of the valve seat 70 and the support plate 65. The case where it was pinched by and fixed by the internal space 40R was demonstrated. In this embodiment, instead of using the fourth check valve CV4, the fifth check valve CV5 that is housed and mounted inside the cylinder of the outer cylinder part 70a of the valve seat 70 and inside the support leg part 70c in the radial direction is provided. Use. The fifth check valve CV5 corresponds to the second check valve CV2 of the first embodiment, similarly to the fourth check valve CV4.

  The fifth check valve CV5, the third check valve CV3, and the fifth check valve CV5 are accommodated and installed inside the cylinder of the outer cylinder portion 70a of the valve seat 70 and inside the support leg portion 70c in the radial direction. Are in the same position in the direction along the rotational axis X, and the fifth check valve CV5 and the third check valve CV3 overlap in the radial direction. Therefore, the valve unit Vb of this embodiment can shorten the length in the direction along the rotation axis X compared with the valve unit Vb of the third embodiment.

  The fifth check valve CV5 includes a cylindrical portion 81 in the direction along the rotational axis X, a spring seat 80 mounted on the head side of the cylindrical portion 81, and a valve seat mounted on the head side of the cylindrical portion 81. A ball 83 as a valve body that is inserted into the cylinder of the cylinder part 81 and is supported by the spring seat 80 on the head side, and is urged toward the screw part by the spring 82 and closely contacts the valve seat part 83 85.

  In the fifth check valve CV5, when hydraulic oil is supplied from the screw portion side, the ball 85 moves to the head side against the urging force of the spring 82 and moves away from the valve seat portion 83, so that the hydraulic oil is Allow passage through five check valves CV5. On the other hand, when the hydraulic fluid flows backward from the head side, the ball 85 is in close contact with the valve seat 83 and prevents the hydraulic fluid from passing through the fifth check valve CV5.

  Other configurations of the present embodiment are the same as those of the third embodiment.

  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 said embodiment (1st embodiment and 2nd embodiment), the valve unit Vb demonstrated the structure provided with 1st check valve CV1 and 2nd check valve CV2. Moreover, in the said embodiment (3rd embodiment and the modification of 3rd embodiment), the valve unit Vb is provided with 3rd check valve CV3 and 4th check valve CV4 or 5th check valve CV5. Explained the configuration.

  However, the valve unit Vb may be configured not to include the second check valve CV2. Further, the fourth check valve CV4 and the fifth check valve CV5 may be omitted.

(2) In the above embodiment (first embodiment and second embodiment), the intermediate wall 54Sb is formed with a circulation hole 54b that forms part of the second check valve CV2, and the circulation hole 54b is The case where a pair of through-holes are arranged in a circular arc shape symmetric about the rotation axis X in the annular region along the outer periphery of the pipe section 54T with the rotation axis X as the center is illustrated. Moreover, the circulation hole 54b illustrated the case where it was two slit-shaped through-holes formed in circular arc shape.

  However, the circulation holes 54b are not limited to being formed as a pair, and may be formed as one or three or more through holes. Further, the circulation hole 54b is not limited to the two slit-shaped through holes formed in an arc shape, and a plurality of round hole through holes may be arranged in an annular shape.

(3) In the said embodiment (1st embodiment and 2nd embodiment), the case where the drain hole 53c and the drain hole 53d share the drain groove | channel D was illustrated.

  However, the drain hole 53c and the drain hole 53d can be configured to communicate with the independent drain grooves D, respectively.

(4) In the above embodiments (the first embodiment and the second embodiment), the drain groove D is formed in a posture along the rotation axis X in the region reaching the tip from the intermediate position on the inner periphery of the connecting bolt 40. In addition, the case where the tip ring 61 has an outer cylinder portion 61a that fits into the inner space 40R is illustrated. In this case, the hydraulic oil discharged from the drain groove D to the outside is not restricted at all.

  However, the tip ring 61 is provided with a flow rate regulating member that regulates the opening area (cross-sectional area of the groove) in the direction along the rotational axis X in the drain groove D, and the circulation of the hydraulic oil discharged from the drain groove D to the outside. The resistance may be adjusted. By increasing the flow resistance of the hydraulic oil discharged from the drain groove D to the outside, the hydraulic oil discharged to the outside via the drain groove D is circulated from the first check valve CV1 to the fluid supply pipe 54. It may be possible to increase the amount of oil.

(5) In the above-described embodiment, the connecting bolt 40 as the valve case has the bolt head 42 formed at the outer end of the bolt main body 41 that is generally cylindrical, and the bolt head 42 in the bolt main body 41. The case where the male screw portion 41S is formed on the outer periphery of the other end portion has been described.

  Then, in a state where the bolt body 41 of the connecting bolt 40 as the valve case is inserted into 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. The case where the internal rotor 30 (driven rotor) is fastened to the intake camshaft 5 by rotating the bolt head 42 has been described.

  However, the valve case does not necessarily need to be the connection bolt 40 in which the male screw portion 41S is formed, and the internal rotor 30 and the intake camshaft 5 are fastened to the male connection bolt 40 that is the valve case. It is not restricted to the aspect by screwing of the screw part 41S and the internal thread part 5S of the intake camshaft 5.

  For example, in the valve case, a bolt head portion 42 having an edge extending radially outward is formed at an outer end portion of the bolt main body 41 that is generally cylindrical, and the bolt main body 41 of the valve case is formed. The annular member 9, the outer rotor 20, and the inner rotor 30 can be inserted.

  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 42 of the valve case is crimped to the annular member 9, so that the valve case and the annular member 9, the inner rotor body 31 and the intake camshaft 5 can be integrated. That is, the inner rotor 30 (driven rotor) 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.

(6) In the above embodiment, as an example of the space communication path, the drain groove D (first embodiment) provided in the inner periphery of the connecting bolt 40 or the tubular flow path provided in the spool body 55 a of the spool 55. A drain path DL (second embodiment) is illustrated.

  However, the space communication path is not limited to the aspect such as the drain groove D or the drain path DL. For example, the cylindrical portion of the sleeve 53 described in the first embodiment can be provided so as to penetrate in the direction along the rotation axis X. Similarly to the case of the drain groove D, the outer surface of the sleeve 53 can be provided. It can also be a groove-like channel provided in

(7) 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 in the first embodiment and the second embodiment is switched. In the third embodiment, the first advance position Pa1 and the first retard position Pb1 are interchanged, and the second advance position Pa2 and the second retard position Pb2 are interchanged.

  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. The embodiment 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 that has a drive-side rotator and a driven-side rotator, and that houses a valve unit in a connecting bolt that connects the driven-side rotator to a camshaft.

1: Crankshaft 5: Intake camshaft (camshaft)
20: External rotor (drive-side rotator)
30: Internal rotor (driven rotor)
40: Connection bolt (valve case)
40R: Internal space 40Rb: Large diameter portion (internal space, opening)
40Rc: Large diameter part (internal space)
41: Bolt body 41S: Male thread portion 41a: Advance port 41b: Retarded port 42: Bolt head 44: Restriction wall (bottom)
52: first valve plate 52a: annular valve plate 53: sleeve 53a: advance communication hole 53b: retard communication hole 53c: drain hole 53d: drain hole 54: fluid supply pipe 54S: base end 54Sa: supply pipe opening 54T: Pipe portion 54a: Supply port 54b: Circulation hole 55: Spool 55b: Land portion 55c: Intermediate hole portion 55v: Tip valve (valve element)
56: Spool spring 57: Opening plate 57a: Flow port 58: Second valve plate A: Valve opening / closing timing control device CV1: First check valve CV2: Second check valve CV3: Third check valve (first check valve) Stop valve)
CV4: Fourth check valve (second check valve)
CV5: Fifth check valve (second check valve)
Ca: advance chamber Cb: retard chamber D: drain groove (space communication path)
DL: Drain road (space connection road)
R: Land part R1: First land (land part)
R2: Second land (land part)
R3: Third land (land part)
Vb: Valve unit X: Center of rotation

Claims (13)

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,
An internal space extending in a direction along the rotation axis; the valve unit is accommodated in the internal space; an opening opened to the outside at one end in the direction along the rotation axis; and the other end A cylindrical valve case having a bottom on
The valve unit includes a base end portion accommodated on 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 pipe line section, and a sliding movement in a direction along the rotation axis while being guided by an inner peripheral surface of the valve case and an outer peripheral surface of the pipe path section of the fluid supply pipe. And a spool arranged,
The valve case has an advance port and a retard port that are formed from the outer peripheral surface to the internal space and communicate with the advance chamber and the retard chamber, respectively.
The spool is formed at an intermediate position between a plurality of land portions formed on the outer periphery and a pair of adjacent land portions, and can communicate with the advance port or the retard port from the inside by sliding movement of the spool. An intermediate hole portion,
The fluid supply pipe is provided on an outer periphery of a distal end portion of the pipe line portion, has a supply port for supplying the fluid from the inside to the intermediate hole portion, and extends from the other side of the base end portion to the pipe line portion. Receiving fluid supply,
The valve case is provided on the bottom side of the valve case, and at least a part of the fluid discharged from the advance chamber or the retard chamber into the space between the valve case and the spool, A valve opening / closing timing control device having a first check valve that circulates from space to the space on the bottom side of the base end in the internal space. The internal space is provided from the outside to the camshaft,
The valve opening / closing timing control device according to claim 1, wherein the bottom portion is disposed on the camshaft side.   The base end portion has a supply pipe opening for supplying the fluid from the bottom side toward the inside of the fluid supply pipe, and the first check valve is disposed between the valve case and the spool. 3. The valve according to claim 1, wherein the fluid circulated from the space to the space closer to the bottom side than the base end portion in the internal space is caused to flow into the fluid supply pipe through the supply pipe opening. Open / close timing control device. The valve unit has a space communication path that communicates a space between the valve case and the spool in the internal space and a space on the bottom side of the base end in the internal space;
4. The valve opening / closing timing control device according to claim 1, wherein the space communication passage communicates with the outside of the internal space. 5.   5. The spool according to claim 1, wherein the spool has a valve body at a distal end portion on the opening side that is switched between a state in which the internal space and the outside communicate with each other by sliding movement of the spool. The valve opening / closing timing control device according to claim 1.   A second check valve that circulates the fluid from the bottom side toward the fluid supply pipe; and the second check valve is disposed closer to the bottom than the first check valve in the internal space. The valve opening / closing timing control device according to any one of claims 1 to 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 valve case in which an internal space is formed in a direction along the rotation axis from the outside to the camshaft,
The valve unit is accommodated in the internal space,
The valve unit includes a base end portion that is fitted on the camshaft side in the internal space, a pipe portion that extends from the base end portion toward the outside in the internal space and has a smaller diameter than the base end portion. A fluid supply pipe, and a spool that is slidably arranged in a direction along the rotation axis while being guided by an inner peripheral surface of the valve case and an outer peripheral surface of the pipe section of the fluid supply pipe. Have
The valve case has an advance port and a retard port that are formed from the outer peripheral surface to the internal space and communicate with the advance chamber and the retard chamber, respectively.
The spool is formed at an intermediate position between a pair of land portions formed on an outer periphery and a pair of the land portions, and is capable of communicating from the inside to the advance port or the retard port by sliding movement of the spool. Having a hole,
The fluid supply pipe receives supply of fluid from the camshaft side of the base end part to the pipe line part,
The fluid supply pipe is provided on an outer periphery of a distal end portion of the pipe line portion, and is provided in a supply port for supplying the fluid from the inside to the intermediate hole portion, and in the base end portion, and the advance chamber or the delay chamber A first check valve that circulates at least a part of the fluid discharged from a corner chamber into the space between the valve case and the spool from the outside side of the base end portion to the camshaft side. Valve opening / closing timing control device.   The valve opening / closing timing control device according to claim 7, wherein the first check valve is provided on the camshaft side in the base end portion. The base end portion includes a base end partition wall that partitions the external side and the camshaft side in the internal space,
The base end partition wall has a circulation hole that communicates the external side and the camshaft side,
The circulation hole is provided along the outer periphery of the pipe line part,
The valve opening / closing timing control device according to claim 8, wherein the first check valve has an annular valve plate that closes the circulation hole. The valve unit has a space communication passage communicating with both the space on the camshaft side and the space on the outer side with respect to the pair of land portions in the internal space,
The valve opening / closing timing control device according to any one of claims 7 to 9, wherein the space communication passage communicates with the outside of the internal space. Comprising a sleeve provided on the inner peripheral surface of the internal space;
The sleeve has an advance communication hole that communicates with the advance port from the inside, and a retard communication hole that communicates with the retard port from the inside,
The spool is guided to the inner peripheral surface of the valve case via the inner peripheral surface of the sleeve, and the intermediate hole portion communicates with the advance port through the advance communication hole. Communicating with the retardation port through a corner communication hole,
The valve opening / closing timing control device according to claim 10, wherein the space communication path is formed between the valve case and the sleeve.   The valve opening / closing timing control device according to any one of claims 7 to 11, further comprising a second check valve that causes the fluid to flow from the camshaft side toward the fluid supply pipe. As the valve case, provided with a connecting bolt that is arranged coaxially with the rotation axis and connects the driven side rotating body to the camshaft by a threaded portion,
The valve opening / closing timing control device according to any one of claims 1 to 12, wherein the internal space is formed so as to penetrate from the threaded portion of the connecting bolt toward the head.

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