JP5105187B2 - Valve timing control device - Google Patents

Description

  The present invention relates to a valve opening / closing timing control device that controls a relative rotation phase of a driven side rotating member with respect to a driving side rotating member that rotates in synchronization with a crankshaft of an internal combustion engine.

  Conventionally, there has been a valve timing control device in which a valve that enables fluid supply to an advance chamber or retard chamber is arranged coaxially with respect to an internal rotor from the side opposite to the camshaft ( Reference document 1). According to this technique, the valve is fixedly arranged outside the internal combustion engine even when there is not enough space in the internal combustion engine to mount the valve.

  Also, an adjustment valve for adjusting the fluid pressure supplied to the phase change mechanism that changes the phase between the advance angle direction and the retard angle direction, and the adjustment valve that is attached to the internal combustion engine and moves by electromagnetic force pushes the adjustment valve. There is a valve opening / closing timing control device that includes an electromagnetic drive mechanism having a pusher member, and an adjustment member that can adjust the amount of axial movement of the adjustment valve between the pusher member and the adjustment valve (Patent Document) 2). According to this technique, even if the electromagnetic drive mechanism is not removed from the internal combustion engine, the adjustment member can be moved relative to the front cover by loosening a small amount of the mounting bolt of the electromagnetic drive mechanism. In this way, it is easy to change the adjustment member for adjusting the amount of axial movement of the adjustment valve. Therefore, it was supposed that the assembling property of the valve opening / closing timing control device to the internal combustion engine was improved.

JP 2004-340142 A Japanese Patent No. 4013364

  However, since the technology of Patent Document 1 is configured to supply fluid to the valve from the direction of the rotation axis of the camshaft via the camshaft, fluid supply is provided between the internal rotor on the camshaft side and the valve. There is a risk that repulsive force in the direction of the rotation axis proportional to the fluid pressure pulsation may be generated in the gap between the internal rotor and the valve. Further, the fluid leaking from each flow path may stay in the gap and the repulsive force may be generated. For this reason, there is a possibility that vibration may occur or the valve malfunctions and accurate control by the valve opening / closing timing control device cannot be performed. Furthermore, because of the above-described configuration, the fluid advances from the fluid storage portion which is a stationary body, the camshaft which is a rotating body, the valve body which is a stationary body, and the inner rotor and the outer rotor which are rotating bodies. Supplied to the corner chamber or retard chamber. Thus, since the fluid is supplied three times between the stationary body and the rotating body, there is a possibility that the amount of fluid leakage increases.

  Moreover, in the technique of patent document 2, since the pushing member which is a stationary non-rotating body pushes the adjustment valve which is a rotating body, both cannot be joined. For this reason, depending on an assembly error or the like, the relative positional relationship between the adjustment valve and the pushing member may change, and the two may not be joined. In this case, the adjustment member can adjust the axial movement amount of the adjustment valve and join them together. However, since the number of assembly parts of the internal combustion engine is considerably large, individual assembly errors accumulate and the adjustment valve and the push valve are pushed together. The positional relationship with the moving member is changed, and there is a possibility that adjustment by the adjusting member must be frequently performed.

  In view of the above circumstances, an object of the present invention is to provide a valve opening / closing timing control device that is easy to assemble and hardly causes malfunction.

  A first characteristic configuration of an intake air control device according to the present invention is a drive-side rotation member that rotates synchronously with a crankshaft of an internal combustion engine, and is arranged coaxially with respect to the drive-side rotation member. A driven-side rotating member that rotates synchronously with the opening and closing camshaft; a fluid pressure chamber formed in one of the drive-side rotating member and the driven-side rotating member; and the fluid pressure chamber as an advance chamber and a retard angle A partition provided on the other of the driving side rotating member and the driven side rotating member so as to partition the chamber, and a side opposite to the camshaft with respect to the driving side rotating member or the driven side rotating member A fluid control valve mechanism that is inserted in a relatively rotatable manner and is stationary and fixed, and controls supply or discharge of fluid via the relative rotating portion with respect to the advance chamber or the retard chamber, and the fluid control valve Mechanism and drive In that a rotary member or discharge channel to always open to the outside air gap between the driven side rotational member is.

  According to this configuration, the fluid control valve mechanism and the driving side rotating member or the driven side rotating member are provided with the discharge channel that always opens the clearance between the fluid control valve mechanism and the driving side rotating member or the driven side rotating member to the outside air. Fluid does not collect in the gap with the member. For this reason, an unexpected repulsive force in the rotation axis direction of the driving side rotating member or the driven side rotating member does not occur between the fluid control valve mechanism and the driving side rotating member or the driven side rotating member. Therefore, the fluid control valve mechanism is inserted so as to be relatively rotatable with respect to the driving side rotating member or the driven side rotating member, and fixed to a stationary member different from the driving side rotating member or the driven side rotating member. Thus, it is possible to obtain a valve opening / closing timing control mechanism that is less prone to vibration and that has few malfunctions.

  Further, the fluid control valve mechanism may be inserted so as to be relatively rotatable with respect to the driving side rotating member or the driven side rotating member, and fixed to a stationary member different from the driving side rotating member or the driven side rotating member. Since the fluid regulating valve mechanism is inserted so as to be relatively rotatable, fine adjustment of the position of the fluid control valve mechanism is simple. Therefore, it is possible to obtain a valve opening / closing timing control device with good assemblability.

  Further, since the fluid control valve mechanism controls the supply or discharge of the fluid to or from the advance chamber or the retard chamber through the relative rotating portion, the repulsive force in the direction of the rotation axis of the camshaft is supplied when the fluid is supplied or discharged. Is unlikely to occur.

  A second characteristic configuration of the intake control device according to the present invention is that the fluid control valve mechanism includes the discharge passage.

  According to this configuration, since the discharge flow path is provided in the fluid control valve mechanism, the functions can be concentrated in the fluid control valve mechanism, and a complicated mounting operation is not required during assembly. For this reason, it can be set as the valve opening / closing timing control apparatus with sufficient assembly property. Further, even if the structure of the camshaft side including the driving side rotating member and the driven side rotating member is complicated and the discharge flow path cannot be provided in the driving side rotating member and the driven side rotating member, The fluid that has flowed into the gap can be reliably discharged to the outside.

  A third characteristic configuration of the intake air control device according to the present invention is that the drive-side rotation member or the driven-side rotation member is provided with the discharge flow path.

  According to this configuration, since the discharge flow path is provided in the driving side rotating member or the driven side rotating member, the gap can be directly opened to the outside air without using other components. Therefore, the fluid that has flowed into the gap can be reliably discharged to the outside only by performing simple processing on the driving side rotating member or the driven side rotating member.

  According to a fourth characteristic configuration of the intake control device of the present invention, the fluid supply portion is provided on a side opposite to the camshaft with respect to the driving side rotating member or the driven side rotating member of the fluid control valve mechanism. It is in the point.

  According to this configuration, since the fluid control valve mechanism that is a stationary body is provided with the fluid supply unit, the fluid is supplied to the advance chamber or the retard chamber without using a rotating body such as a camshaft. The fluid can be supplied easily and reliably. Since the camshaft is not interposed, it is possible to adopt a configuration in which fluid does not easily leak into the gap.

  A fifth characteristic configuration of the intake control device according to the present invention is a phase displacement restriction that creates a restriction state that restricts a displacement of a relative rotation phase of the driven rotation member with respect to the driving side rotation member and a release state that releases the restriction. In addition to providing a mechanism, the fluid control valve mechanism includes a restriction flow path for supplying or discharging the fluid to or from the phase displacement restriction mechanism.

  According to this configuration, the functions can be integrated into the fluid control valve mechanism, and a complicated mounting operation is not required during assembly. For this reason, it can be set as the valve opening / closing timing control apparatus with sufficient assembly property. In addition, since there is a restriction flow path dedicated to the phase displacement restriction mechanism, the restriction state and the release state can be switched reliably.

  An embodiment in which a valve timing control device according to the present invention is applied to an automobile engine will be described with reference to the drawings.

(overall structure)
As shown in FIG. 1, the valve opening / closing timing control device 1 includes an external rotor 3 and a front plate 4 as “drive side rotating members” that rotate synchronously with an engine crankshaft (not shown), and an external rotor 3. On the other hand, it is provided with an internal rotor 5 as a “driven rotation member” that is arranged coaxially and rotates synchronously with a camshaft 8 for opening and closing the valve of the engine.

  The internal rotor 5 is integrally assembled at the tip of a camshaft 8 that constitutes a rotating shaft of a cam (not shown) that controls opening and closing of an intake valve or an exhaust valve of the engine. A concave portion 14 is provided on the inner diameter side of the inner rotor 5, and a fixing hole 12 penetrating the camshaft 8 side is formed on the bottom surface thereof. Bolts 13 are passed through the fixing holes 12 to fix the internal rotor 5 to the camshaft 8. The camshaft 8 is rotatably assembled to a cylinder head (not shown) of the engine.

  The outer rotor 3 is integrated with the front plate 4 and is externally mounted so as to be rotatable relative to the inner rotor 5 within a predetermined range. A sprocket portion 11 is formed on the outer periphery of the external rotor 3. A power transmission member (not shown) such as a timing chain or a timing belt is installed between the sprocket portion 11 and a gear (not shown) attached to the crankshaft.

  When the crankshaft is rotationally driven, rotational power is transmitted to the sprocket portion 11 via the power transmission member, and the external rotor 3 is rotationally driven. As the external rotor 3 is driven to rotate, the inner rotor 5 is driven to rotate and the camshaft 8 is rotated. The cam provided on the camshaft 8 pushes down the intake valve or exhaust valve of the engine to open it.

  As shown in FIG. 5, the outer rotor 3 is formed with a plurality of protrusions protruding in the radial direction so as to be separated from each other along the rotation direction. The fluid pressure chamber 6 is formed by the adjacent protrusions and the inner rotor 5. Is formed. In the present embodiment, four fluid pressure chambers 6 are provided.

  Grooves are formed at locations facing the fluid pressure chambers 6 on the outer peripheral portion of the internal rotor 5, and vanes 7 as “partition portions” are inserted into the grooves. The fluid pressure chamber 6 is partitioned by the vane 7 into an advance chamber 6a and a retard chamber 6b in the relative rotation direction (the directions of arrows S1 and S2 in FIGS. 5 and 6).

  The internal rotor 5 has an advance chamber communication hole 17 and a retard chamber communication hole 18 formed therein. The advance chamber communication hole 17 communicates the cylindrical recess 14 for inserting the fluid control valve mechanism 2 with the advance chamber 6a. The retard chamber communication hole 18 communicates the recess 14 and the retard chamber 6b.

  By supplying or discharging hydraulic oil as “fluid” from a hydraulic circuit (not shown) to the advance chamber 6a or the retard chamber 6b, the relative rotational phase between the internal rotor 5 and the external rotor 3 (hereinafter referred to as “rotational phase”). , Referred to as “relative rotational phase”) in the advance angle direction S1 or the retard angle direction S2. The advance angle direction S1 indicates the direction in which the vane 7 indicated by the arrow S1 in FIGS. 5 and 6 is relatively displaced, and the retard angle direction S2 indicates the direction in which the vane 7 indicated by the arrow S2 is relatively displaced.

  When hydraulic oil is supplied to the advance chamber 6a, the relative rotational phase is displaced in the advance direction S1, and when hydraulic oil is supplied to the retard chamber 6b, the relative rotation phase is displaced in the retard direction S2. The range in which the relative rotational phase can be displaced is the range in which the vane 7 can be displaced inside the fluid pressure chamber 6, and the most retarded angle at which the volume of the retarded chamber 6b is maximum as shown in FIGS. This corresponds to a range between the phase and the most advanced phase (not shown) in which the volume of the advance chamber 6a is maximum.

(Fluid control valve mechanism)
The fluid control valve mechanism 2 controls the supply or discharge of hydraulic fluid to the advance chamber 6a or the retard chamber 6b. The fluid control valve mechanism 2 is inserted into the recess 14 of the internal rotor 5 described above so as to be relatively rotatable, and is fixed to a front cover of the engine or the like. That is, the fluid control valve mechanism 2 remains stationary and does not follow the rotation of the internal rotor 5. According to this configuration, fine adjustment of the position of the fluid control valve mechanism 2 is simplified, and assemblability is improved.

  As shown in FIG. 1, the fluid control valve mechanism 2 includes a solenoid 21, a housing 23, an intermediate housing 24, and a spool valve 25. The spool valve 25 has a bottomed cylindrical shape, and the intermediate valve has a bottomed cylindrical shape having a hollow portion that matches the shape of the spool valve 25. Further, the housing 23 has a hollow shape having a hollow portion that matches the shape of the intermediate housing 24. The hollow portion of the housing 23 passes through both end portions, and an intermediate housing 24 is inserted into the hollow portion. The intermediate housing 24 is shrink-fitted to the housing 23, and the outer peripheral surface thereof is in close contact with the inner peripheral surface 34 of the housing 23 and is always integral with the housing 23. A spool valve 25 is inserted into the hollow portion of the intermediate housing 24 so as to be movable in the direction of the rotational axis of the camshaft 8 (hereinafter referred to as “rotational axis direction”).

  An engagement groove 51 is formed on the camshaft 8 side of the spool valve 25, and a spring 26 is installed across the bottom surface of the intermediate housing 24 and the engagement groove 51. For this reason, the spool valve 25 is always biased to the opposite side of the camshaft 8 with respect to the intermediate housing 24. A solenoid 21 is installed at the end of the intermediate housing 24 opposite to the camshaft 8 so that the spool valve 25 can reciprocate in the direction of the rotational axis. The rod 22 at the tip of the solenoid 21 is in contact with the bottom 52 of the spool valve 25. When the solenoid 21 is energized, the rod 22 is moved to the solenoid as shown in FIG. 1 (FIG. 2) to FIG. 3 (FIG. 4). The spool valve 25 moves to the camshaft 8 side by pressing the bottom 52 extending from 21. When the energization is stopped, the rod 22 retracts toward the solenoid 21, but the spool valve 25 moves toward the solenoid 21 following the movement of the rod 22 by the biasing force of the spring 26 described above.

  As shown in FIGS. 1, 2, and 7, the housing 23 has a cylindrical shape on the side inserted into the inner rotor 5, and has a quadrangular prism shape on the opposite side. On the outer peripheral surface of the cylindrical portion, three annular grooves extending around the outer periphery are formed in parallel, and a seal ring 27 for preventing hydraulic oil leakage is provided in each groove. Between each of the adjacent grooves, an advance outer peripheral groove 31 and a retard outer peripheral groove 32 which are similarly annular grooves are formed. The seal ring 27 can prevent hydraulic fluid from leaking from the advance angle outer peripheral groove 31 and the retard angle outer peripheral groove 32. Further, the quadrangular prism-shaped portion is provided with a supply portion 33 to which hydraulic oil is directly supplied from a hydraulic circuit. Further, a through-hole 35 c that penetrates from the hollow portion of the housing 23 to the outside is formed near the boundary between the portion inserted into the inner rotor 5 of the housing 23 and the portion not inserted.

  The advance angle outer peripheral groove 31 is always in communication with the advance angle chamber communication hole 17 as shown in FIGS. Further, as shown in FIGS. 2, 4, and 6, the retard angle outer peripheral groove 32 is always in communication with the retard chamber communication hole 18.

  As shown in FIGS. 1, 2, and 7, on the outer peripheral surface of the intermediate housing 24, the supply vertical groove 41, the advance vertical groove 42, the retard vertical groove 43, and a discharge Vertical grooves 44 are formed respectively. The supply vertical groove 41 and the advance angle vertical groove 42 are formed on the same straight line. Each longitudinal groove is formed to be dispersed every 90 degrees in the circumferential direction of the intermediate housing 24.

  However, the circumferential separation angle of the vertical grooves is not limited to 90 degrees, and it is preferable that the vertical grooves do not intersect each other. However, by dispersing, it is possible to reduce the risk of hydraulic oil leaking from each vertical groove entering another vertical groove.

  On the inner peripheral surface 48 of the intermediate housing 24, an annular inner peripheral groove 45a and an inner peripheral groove 45b are formed over the inner periphery. A communication hole 46 a penetrating the inner peripheral surface 48 is formed at one end portion of the supply vertical groove 41, and the other end portion of the supply vertical groove 41 extends to the supply portion 33 of the housing 23, It always communicates with the supply unit 33. A communication hole 46 b penetrating the inner circumferential groove 45 b is formed at one end of the advance vertical groove 42, and the other end of the advance vertical groove 42 is the advance outer peripheral groove 31 of the housing 23. And is always in communication with the advancement outer peripheral groove 31 through the through hole 35a. A communication hole 46 c that penetrates the inner circumferential groove 45 a is formed at one end of the retarding vertical groove 43, and the other end of the retarding vertical groove 43 is the retarding outer circumferential groove 32 of the housing 23. And is always in communication with the retarding outer peripheral groove 32 through the through hole 35b. 46d penetrating the inner peripheral surface 48 is formed at one end of the discharge vertical groove 44, and the other end of the discharge vertical groove 44 extends to the through hole 35c. Always communicates with the outside.

  As shown in FIGS. 1, 2, and 7, annular discharge outer peripheral grooves 53 a and 53 b and a supply outer peripheral groove 54 are formed on the outer peripheral surface of the spool valve 25. The discharge outer peripheral grooves 53a and 53b are respectively provided with through holes 55a and 55b penetrating through the hollow portions inside.

  As shown in FIGS. 1 and 2, the positions of the discharge outer peripheral grooves 53 a and 53 b and the supply outer peripheral groove 54 in the direction of the rotation axis are as shown in FIGS. It is determined that the discharge outer circumferential groove 53b communicates only with the inner circumferential groove 45b while communicating with only the 45a. In addition, when the solenoid 21 is energized, the supply outer circumferential groove 54 communicates with only the communication hole 46a and the inner circumferential groove 45b, and the discharge outer circumferential groove 53a communicates with only the inner circumferential groove 45a. However, the discharge outer peripheral groove 53a is always in communication with the communication hole 46d, and the discharge outer peripheral groove 53b is surrounded by the inner peripheral surface 48 when not energized and does not communicate with the flow path on the intermediate housing 24 side.

  At the end of the intermediate housing 24 on the camshaft 8 side, a discharge hole 47 that communicates the hollow portion inside the intermediate housing 24 with the clearance 29 between the tip portion 28 of the fluid control valve device and the bottom portion 15 of the internal rotor 5. Is formed. Therefore, the clearance 29 is always open to the atmosphere via the discharge hole 47, the inside of the spool valve 25, the communication hole 55a, the discharge outer peripheral groove 53a, the communication hole 46d, the discharge vertical groove 44, and the through hole 35c. Yes. This flow path is a “discharge flow path”.

(Operation of valve timing control device)
The operation of the valve timing control apparatus 1 will be described with reference to the drawings.

  When the hydraulic oil is supplied to the advance chamber 6a and the relative rotation phase is displaced in the advance direction S1, the solenoid 21 is energized. At this time, the spool valve 25 is pushed by the rod 22 of the solenoid 21 and moved to the camshaft 8 side as shown in FIGS. In this energized state, when hydraulic oil is supplied from the hydraulic circuit to the supply portion 33 of the housing 23, the hydraulic oil is supplied from the supply portion 33 to the supply vertical groove 41, the communication hole 46a, and the supply outer peripheral groove as indicated by the solid line arrows. 54, the inner peripheral groove 45b, the communication hole 46b, the advance angle vertical groove 42, the through hole 35a, and the advance hole 6a and the communication hole 17 for each advance chamber 6a are pressure-fed to each advance chamber 6a. At this time, the vane 7 relatively moves in the advance direction S1, and the hydraulic oil in each retard chamber 6b is discharged. As indicated by the broken line arrows, the hydraulic oil flows from the retard chambers 6b to the retard chamber communication holes 18, the retard outer peripheral grooves 32, the through holes 35b, the retard vertical grooves 43, the communication holes 46c, and the inner circumference. It is discharged to the outside through the groove 45a, the discharge outer peripheral groove 53a, the communication hole 46d, the discharge vertical groove 44, and the through hole 35c.

  A seal ring 27 is installed between the inner peripheral surface 15 of the inner rotor 5 and the housing 23, but since the fluid control valve mechanism 2 and the inner rotor 5 rotate relative to each other, some hydraulic oil is left in the gap 29. There is a possibility of leakage. However, as described above, since the discharge flow path is provided, even if the hydraulic oil leaks into the gap 29, the hydraulic oil is discharged to the outside through the discharge flow path. Therefore, the hydraulic oil does not collect in the gap 29.

  For this reason, an unexpected repulsive force in the direction of the rotational axis does not act between the fluid control valve mechanism 2 and the internal rotor 5. Accordingly, even when the fluid control valve mechanism 2 is inserted so as to be relatively rotatable with respect to the internal rotor 5 and is fixed to a stationary member different from the internal rotor 5, vibrations are unlikely to occur, and malfunctions may occur. A small valve opening / closing timing control mechanism 1 can be obtained.

  On the other hand, when hydraulic oil is supplied to the retard chamber 6b and the relative rotational phase is displaced in the retard direction S2, the energization of the solenoid 21 is stopped. At this time, the spool valve 25 moves together with the rod 22 of the solenoid 21 toward the solenoid 21 as shown in FIGS. When hydraulic fluid is supplied from the hydraulic circuit to the supply portion 33 of the housing 23 in this non-energized state, the hydraulic fluid is supplied from the supply portion 33 to the supply vertical groove 41, the communication hole 46a, and the supply outer periphery as indicated by the solid line arrows. The gas is supplied to each retarded angle chamber 6b through the groove 54, the inner circumferential groove 45a, the communicating hole 46c, the retarded vertical groove 43, the through hole 35b, and each retarded angle chamber communicating hole 18. At this time, the vane 7 relatively moves in the retarding direction S2, and the hydraulic oil in each advance chamber 6a is discharged. As indicated by the broken line arrows, the hydraulic oil is communicated from each advance chamber 6a to each advance chamber 6a communication hole 17, advance angle outer peripheral groove 31, through hole 35a, advance angle vertical groove 42, communication hole 46b, Via the inner peripheral groove 45b, the discharge outer peripheral groove 53b, the communication hole 55b, the inside of the intermediate housing 24, the communication hole 55a, the discharge outer peripheral groove 53a, the communication hole 46d, the discharge vertical groove 44, and the through hole 35c. And discharged.

  Similarly, since the discharge flow path is provided, even if the hydraulic oil leaks into the gap 29, the hydraulic oil is discharged to the outside through the discharge flow path. Therefore, the hydraulic oil does not collect in the gap 29.

  According to this configuration, since the fluid control valve mechanism 2 is provided with the discharge flow path, the functions can be integrated into the fluid control valve mechanism 2, and a complicated mounting operation is not required during assembly. For this reason, it can be set as the valve opening / closing timing control apparatus 1 with good assembly property.

  According to this configuration, the fluid control valve mechanism 2 supplies the hydraulic oil to the advance chamber 6a or the retard chamber 6b through the relatively rotating cylindrical side surface portion. The repulsive force in the direction of the rotation axis is less likely to occur.

  Further, since the fluid control valve mechanism 2 which is a stationary body is provided with the hydraulic oil supply unit 33, the fluid is supplied to the advance chamber 6a or the retard chamber 6b without using a rotating body such as the camshaft 8 or the like. The hydraulic oil can be supplied easily and reliably. Since the configuration is such that the camshaft 8 is not interposed, the hydraulic oil is unlikely to leak into the gap 29.

  When the structure on the camshaft 8 side such as the internal rotor 5 and the external rotor 3 is not complicated, a discharge passage that communicates the clearance 29 with the outside air is formed as a through-hole to the outside at the corner of the concave portion 14 of the internal rotor 5. It may be provided directly. When the discharge flow path is provided in the internal rotor 5 which is a rotating body, the hydraulic oil discharge efficiency is improved by the centrifugal force caused by the rotation.

  In order to facilitate the processing of the groove, each member of the fluid control mechanism 2 has a cylindrical shape. However, the shape is not limited to this shape as long as it has the above-described functions. Further, if the groove can be processed, the housing 23 and the intermediate housing 24 do not need to be separate members.

(Another embodiment)
An embodiment in which the valve opening / closing timing control device includes a phase displacement restriction mechanism and the fluid control valve mechanism includes a restriction flow path for supplying or discharging hydraulic oil to or from the phase displacement restriction mechanism will be described with reference to the drawings. The description of the same configuration as that of the above-described embodiment is omitted, and the same reference numerals are given to the same configuration.

  The phase displacement restricting mechanism 9 is provided between the outer rotor 3 and the inner rotor 5, and creates a restricting state in which the displacement of the relative rotational phase is restricted to a constant phase and a releasing state in which the restriction is released. In the present embodiment, the displacement of the relative rotational phase is restricted to the most retarded angle phase by the phase displacement restriction mechanism 9.

  As shown in FIG. 9, the phase displacement restricting mechanism 9 includes a restricting storage portion 91, a retracting member 92, a restricting recess 93, and a spring 94. The restricting storage portion 91 is formed in the outer rotor 3, and the restricting recess 93 is formed in the inner rotor 5. The withdrawing / retracting member 92 is displaceable between a restricting state where the retracting member 92 enters the restricting recess 93 and a released state where the retracting member 92 is retracted from the restricting recess 93 to the restricting storage portion 91. The withdrawing / retracting member 92 is always urged so as to enter the restriction recess 93 by a spring 94 installed in the restriction storage part 91. In FIG. 9, the retractable member 92 is in a restricted state.

  As shown in FIG. 8, four annular grooves are formed in parallel on the outer peripheral surface of the cylindrical portion of the housing 23, and a seal ring 27 for preventing hydraulic oil leakage is installed in each groove. Has been. Between the adjacent grooves, in addition to the advance outer peripheral groove 31 and the retard outer peripheral groove 32, a restricting outer peripheral groove 96 is formed. The seal ring 27 can prevent the hydraulic oil from leaking from the advance outer peripheral groove 31, the retard outer peripheral groove 32, and the regulating outer peripheral groove 96.

  The restriction outer circumferential groove 96 is always in communication with a restriction communication hole 95 connected to the restriction recess 93. A regulating vertical groove 99 is formed on the outer peripheral surface of the intermediate housing 24 in parallel with the rotational axis direction. The supply vertical groove 41, the advance vertical groove 42, the retard vertical groove 43, the discharge vertical groove 44, and the regulating vertical groove 99 are formed by being dispersed every 90 degrees in the circumferential direction of the intermediate housing 24. It is.

  One end of the regulating vertical groove 99 is always in communication with the regulating outer circumferential groove 96 through the through hole 98. The other end extends to the regulation supply unit 97 provided in the housing 23 and is always in communication with the regulation supply unit 97. That is, the regulation supply section 97 and the regulation recess 93 are always in communication, and a flow path constituted by the regulation communication hole 95, the regulation outer peripheral groove 96, the through hole 98, and the regulation vertical groove 99 is “ It is a “regulation channel”. When hydraulic oil is supplied from the hydraulic circuit to the regulation supply unit 97, the hydraulic oil is pumped to the regulation recess 93 as indicated by the solid line arrows in FIGS. When the hydraulic oil pressure reaches a certain pressure, the withdrawing / retracting member 92 is retracted from the restricting recess 93 and is released. Thereafter, the relative rotation phase can be controlled by supplying or discharging hydraulic oil to or from the advance chamber 6a or the retard chamber 6b.

  According to this configuration, the functions can be concentrated in the fluid control valve mechanism 2, and a complicated mounting operation is not required during assembly. For this reason, it can be set as the valve opening / closing timing control apparatus 1 with good assembly property. In addition, since there is a dedicated restriction channel for the phase displacement restriction mechanism 9, it is possible to reliably switch between the restricted state and the released state.

  The phase displacement restricting mechanism may be a mechanism that restricts the relative rotational phase to a phase within a certain range. Further, both a phase displacement restricting mechanism that restricts the relative rotational phase to a constant phase and a phase displacement restricting mechanism that restricts the relative rotational phase to a phase in a certain range may be provided. In that case, the hydraulic oil supply part and the outer peripheral groove from the hydraulic circuit may be added to the housing 23, and the vertical groove may be added to the intermediate housing 24. Thus, even if a mechanism to be controlled is added, the flow path can be configured easily.

  In the above-described embodiment, when the valve opening / closing timing control device 1 is provided with the phase displacement regulating mechanism 9, for example, a regulating communication hole that communicates the regulating recess 93 and the advance angle outer peripheral groove 31 may be provided. At this time, the supply or discharge of hydraulic fluid to the advance chamber 6a is controlled, and at the same time, the phase displacement regulating mechanism 9 is controlled.

Sectional view of the rotation axis direction of the valve timing control device when the solenoid is not energized Sectional drawing of the rotating shaft direction of the valve timing control apparatus of the surface orthogonal to the cross section of FIG. Sectional view in the direction of the rotation axis of the valve timing control device when the solenoid is energized FIG. 3 is a cross-sectional view of the valve opening / closing timing control device in a direction perpendicular to the cross section of FIG. Sectional view in the VV direction in FIG. Sectional view in the VI-VI direction in FIG. Exploded perspective view of fluid control valve mechanism, (a) is an upper perspective view, (b) is a lower perspective view Sectional drawing of the rotating shaft direction at the time of solenoid non-energization in another embodiment IX-IX direction sectional view in FIG.

Explanation of symbols

1 Valve opening / closing timing control device 2 Fluid control valve mechanism 3 External rotor (drive-side rotating member)
4 Front plate (drive side rotating member)
5 Internal rotor (driven side rotating member)
6 Fluid pressure chamber 6a Lead angle chamber 6b Delay angle chamber 7 Vane (partition plate)
8 Camshaft 9 Phase displacement regulating mechanism 29 Clearance 33 Supply section 44 Discharge vertical groove (discharge flow path)
46d Communication hole (discharge channel)
47 Discharge hole (discharge flow path)
53a Outer peripheral groove (discharge flow path)
55a Communication hole (discharge channel)
95 Regulated communication hole (regulated flow path)
96 Peripheral groove for regulation (regulation channel)
98 Through hole (regulated flow path)
99 Vertical groove for regulation (regulated flow path)

Claims (5)

A drive-side rotating member that rotates synchronously with the crankshaft of the internal combustion engine;
A driven-side rotating member that is coaxially disposed with respect to the driving-side rotating member and rotates synchronously with a camshaft for opening and closing the valve of the internal combustion engine;
A fluid pressure chamber formed in any one of the driving side rotating member and the driven side rotating member;
A partition provided on the other of the driving side rotating member and the driven side rotating member to partition the fluid pressure chamber into an advance chamber and a retard chamber;
A portion that is inserted into the drive-side rotation member or the driven-side rotation member on the side opposite to the camshaft so as to be rotatable relative to the drive-side rotation member or is stationary and fixed, and that rotates relative to the advance chamber or the retard chamber A fluid control valve mechanism for controlling supply or discharge of fluid via
A valve opening / closing timing control device comprising a discharge passage that constantly opens a gap between the fluid control valve mechanism and the driving side rotating member or the driven side rotating member to the atmosphere.   The valve opening / closing timing control device according to claim 1, wherein the fluid control valve mechanism includes the discharge passage.   The valve opening / closing timing control device according to claim 1, wherein the discharge passage is provided in the driving side rotating member or the driven side rotating member.   4. The fluid supply valve mechanism according to claim 1, further comprising a supply portion of the fluid on a side opposite to the camshaft with respect to the driving side rotation member or the driven side rotation member of the fluid control valve mechanism. 5. Valve opening / closing timing control device. A phase displacement regulation mechanism that creates a regulation state that regulates the displacement of the relative rotation phase of the driven side rotation member with respect to the drive side rotation member and a release state that releases the regulation;
The valve opening / closing timing control device according to any one of claims 1 to 4, wherein the fluid control valve mechanism includes a restriction flow path for supplying or discharging the fluid to or from the phase displacement restriction mechanism.

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