JP6035880B2 - 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.

  In recent years, a valve opening / closing timing control device that can change the opening / closing timings of an intake valve and an exhaust valve in accordance with an operating state of an internal combustion engine (hereinafter also referred to as an engine) has been put into practical use. This valve opening / closing timing control device is, for example, an intake / exhaust valve that opens and closes as the driven side rotating member rotates by changing the relative rotation phase of the driven side rotating member with respect to the rotation of the driven side rotating member caused by the operation of the engine. It has a mechanism to change the opening and closing timing of.

  In general, the optimum opening / closing timing of the intake / exhaust valves varies depending on the operating conditions of the engine such as when the engine is started and when the vehicle is running. Therefore, when the engine is started, the relative rotation phase of the driven-side rotating member with respect to the rotation of the driving-side rotating member is constrained to a predetermined phase, thereby realizing the optimum intake / exhaust valve opening / closing timing for starting the engine. However, hydrocarbon (HC) emissions increase when the relative rotation phase is maintained even when idling after the engine is started. Therefore, when idling after the engine is started, the relative rotation phase is a phase that can suppress the HC emissions. It is desirable to change to

  Patent Document 1 discloses a valve opening / closing timing control device including an internal rotor as a driven side rotating body inside a housing as a driving side rotating body connected to a camshaft. In this valve opening / closing timing control device, a fluid pressure chamber is formed by a housing and an internal rotor, and the fluid pressure chamber is partitioned into a retarded angle chamber and an advanced angle chamber by a vane as a partitioning portion. Also, by selecting one of the retard chamber and the advance chamber and supplying hydraulic fluid as the working fluid, the relative rotation phase of the housing and the internal rotor is moved in the retard phase direction or the advance phase direction. An OCV for rotation is provided. Furthermore, a torsion spring that urges the relative rotational phase to be displaced in the advance direction is provided from the inner rotor to the housing.

  In the valve opening / closing timing control device disclosed in Patent Document 1, a first restricting member and a second restricting member that can be moved back and forth are provided on the housing side, and a first restricting groove that engages with the first restricting member, A second restriction groove that fits into the two restriction members is formed on the inner rotor side. The first restriction member and the second restriction member enter the first restriction groove and the second restriction groove by the biasing force of the spring. On the other hand, the internal rotor has a first series passage for applying hydraulic oil pressure in a direction for retracting the first restricting member, and a second communication passage for applying hydraulic oil pressure in a direction for retracting the second restricting member. Is formed.

  The state in which the first restricting member is engaged with the first restricting groove and the second restricting member and the second restricting groove are engaged is the intermediate lock phase, and the second restricting member is retracted from the second restricting groove and The state in which one restricting member is in contact with the end portion on the retard side of the first restricting groove is the retard side restricting phase.

  In this valve opening / closing timing control device, the first restriction groove and the second restriction groove are provided so that the first restriction member or the second restriction member is independently retracted from the first restriction groove or the second restriction groove. And an OCV for restricting section that supplies hydraulic oil individually. With this restriction part OCV, the relative rotational phase is constrained to an intermediate locking phase with good startability when the engine is started, and the relative rotational phase is set to the retarded side in order to suppress the HC emission amount when idling after the engine is started. The relative rotational phase is regulated to a retard side regulation phase that is retarded from the intermediate lock phase by being displaced.

  Normally, during engine operation, the displacement force in the retard direction and the advance direction based on the torque fluctuation of the camshaft acts on the internal rotor. This displacement force acts on the retard direction on average, and the inner rotor tends to be displaced in the retard direction. Hereinafter, a displacement force obtained by averaging the displacement force in the retard direction and the advance direction based on the torque variation of the camshaft is referred to as “an average displacement force in the retard direction based on the torque variation of the camshaft”. The valve opening / closing timing control device described in Patent Document 1 includes a torsion spring, so that the relative rotational phase can be smoothly and rapidly advanced regardless of the average displacement force in the retard direction based on the torque fluctuation of the camshaft. It is possible to displace to.

JP 2011-1852 A

  Recently, the vehicle has been equipped with an idling stop function for temporarily stopping the operation of the engine even when the vehicle is temporarily stopped due to a red light or the like during traveling due to environmental considerations. When idling is stopped, the engine is stopped with the relative rotational phase set to the most retarded phase. This is because the engine is hot at the time of idling stop, and when starting from the most retarded phase, the engine is started and ignition of the air-fuel mixture is facilitated. Further, when cranking is performed with the relative rotational phase set to the most retarded angle, the crankshaft can be smoothly started with a light load.

  However, if the engine is started when the engine is in a high temperature state, the supply pressure of the hydraulic oil becomes considerably low because the rotational speed of the engine is low and the temperature of the hydraulic oil is high and the viscosity is low. Therefore, the supply pressure of the hydraulic oil is insufficient to stably maintain the relative rotation phase.

  In the valve opening / closing timing control device disclosed in Patent Document 1, the operation of the internal rotor and vane at the start at idling stop is not the hydraulic oil supply pressure, but the retard direction and advance angle based on the torque fluctuation of the camshaft. The displacement force in the direction and the biasing force by the torsion spring become dominant. That is, the average displacement force toward the retard side based on the torque fluctuation of the camshaft is offset by the biasing force toward the advance side by the torsion spring, and it becomes difficult to stably maintain the relative rotational phase. Therefore, in the most retarded phase where no mechanical restraint or regulation is made between the housing and the inner rotor, the inner rotor and the vane oscillate in the retarding direction and the advancing direction, and the vane is in the fluid pressure chamber. There was a possibility that a hitting sound was generated by colliding with the wall surface.

  In view of the above problems, it is an object of the present invention to provide a valve opening / closing timing control device that has high startability of an internal combustion engine, suppresses HC emission during idling, and is stable in starting after idling stop. To do.

In order to solve the above-described problem, the valve opening / closing timing control device according to the present invention includes a drive-side rotation member that rotates in synchronization with a crankshaft of an internal combustion engine, a drive-side rotation member that is coaxial with the drive-side rotation member, A driven-side rotating member that rotates synchronously with a camshaft for opening and closing a valve of an internal combustion engine, a fluid pressure chamber formed by the driving-side rotating member and the driven-side rotating member, the driving-side rotating member, and the driven-side rotating member An advance chamber and a retard chamber formed by partitioning the fluid pressure chamber with a partition provided in at least one of the members, and a fluid control mechanism for controlling supply and discharge of the working fluid to and from the fluid pressure chamber; A first intermediate lock mechanism that restricts or releases the relative rotation phase of the driven side rotation member with respect to the driving side rotation member to a first intermediate lock phase between a most advanced angle phase and a most retarded angle phase; , Relative A rotation delay phase constrained to the most retarded angle lock phase, or a most retarded angle lock mechanism that releases the constraint, and a relative intermediate phase that is a second intermediate between the first intermediate lock phase and the most retarded angle lock phase. A second intermediate lock mechanism that restrains or releases the lock phase ;
The first intermediate lock mechanism, the second intermediate lock mechanism, and the most retarded angle lock mechanism, each having a common flow path that is a common portion for supplying and discharging the working fluid,
When the working fluid is supplied to the first intermediate lock mechanism and the second intermediate lock mechanism, the working fluid reaches the second intermediate lock mechanism rather than the working fluid reaches the first intermediate lock mechanism. It is in the point provided with the delay part which becomes late .

With such a characteristic configuration, the relative rotation phase can be constrained to the first intermediate lock phase between the most advanced angle phase and the most retarded angle phase by the first intermediate lock mechanism. Can be started. In addition, since the relative rotation phase can be constrained to the second intermediate lock phase by the second intermediate lock mechanism, the amount of HC discharged during idling can be suppressed. Furthermore, even in a state where it is difficult to stably maintain the relative rotation phase at the start of idling stop, the relative rotation phase can be constrained to the most retarded angle lock phase by the most retarded angle lock mechanism. It is possible to stably start the internal combustion engine by preventing the partition portion from swinging in the retarding direction and the advancing direction and generating the hitting sound.
In this configuration, it is not necessary to individually form a flow path for each of the first intermediate lock mechanism, the second intermediate lock mechanism, and the most retarded angle lock mechanism. Can be. Further, since the volume occupied by the flow path can be reduced, the valve opening / closing timing control device can be reduced in size.
In this configuration, a two-position switching type that supplies and discharges the working fluid to and from the common flow path, and a release control valve with one output port can be used. Therefore, the configuration of the release control valve is simpler than that having two output ports so that the working fluid is separately supplied to and discharged from the first intermediate lock mechanism and the second intermediate lock mechanism. It is not necessary to form two flow paths for supplying and discharging the working fluid to the first intermediate lock mechanism and the second intermediate lock mechanism.

In order to solve the above-described problem, the valve opening / closing timing control device according to the present invention includes a drive-side rotation member that rotates in synchronization with a crankshaft of an internal combustion engine, a drive-side rotation member that is coaxial with the drive-side rotation member, A driven-side rotating member that rotates synchronously with a camshaft for opening and closing a valve of an internal combustion engine, a fluid pressure chamber formed by the driving-side rotating member and the driven-side rotating member, the driving-side rotating member, and the driven-side rotating member An advance chamber and a retard chamber formed by partitioning the fluid pressure chamber with a partition provided in at least one of the members, and a fluid control mechanism for controlling supply and discharge of the working fluid to and from the fluid pressure chamber; A first intermediate lock mechanism that restricts or releases the relative rotation phase of the driven side rotation member with respect to the driving side rotation member to a first intermediate lock phase between a most advanced angle phase and a most retarded angle phase; The relative A rotation delay phase constrained to the most retarded angle lock phase, or a most retarded angle lock mechanism that releases the constraint, and a relative intermediate phase that is a second intermediate between the first intermediate lock phase and the most retarded angle lock phase. A second intermediate lock mechanism that restrains the lock phase or releases the restraint,
A common flow path for supplying and discharging working fluid to and from the first intermediate lock mechanism and the second intermediate lock mechanism;
The flow path for supplying and discharging the working fluid to the most retarded angle locking mechanism is the same as the flow path for supplying and discharging the working fluid to the advance chamber,
When the working fluid is supplied to the first intermediate lock mechanism and the second intermediate lock mechanism, the working fluid reaches the second intermediate lock mechanism rather than the working fluid reaches the first intermediate lock mechanism. It is in the point provided with the delay part which becomes late.

With such a characteristic configuration, the relative rotation phase can be constrained to the first intermediate lock phase between the most advanced angle phase and the most retarded angle phase by the first intermediate lock mechanism. Can be started. In addition, since the relative rotation phase can be constrained to the second intermediate lock phase by the second intermediate lock mechanism, the amount of HC discharged during idling can be suppressed. Furthermore, even in a state where it is difficult to stably maintain the relative rotation phase at the start of idling stop, the relative rotation phase can be constrained to the most retarded angle lock phase by the most retarded angle lock mechanism. It is possible to stably start the internal combustion engine by preventing the partition portion from swinging in the retarding direction and the advancing direction and generating the hitting sound.
In this configuration, by providing the common flow path, there is no need to individually form the flow path for each of the first intermediate lock mechanism and the second intermediate lock mechanism. Furthermore, since the flow path for supplying and discharging the working fluid to the most retarded angle locking mechanism is the same as the existing flow path for supplying and discharging the working fluid to the advance angle chamber, a new flow path is separately provided for the most retarded angle locking mechanism. There is no need to form. Therefore, it is possible to reduce the cost by reducing the number of processing steps for the flow path of the valve timing control device. Further, since the volume occupied by the flow path can be reduced, the valve opening / closing timing control device can be reduced in size.
In this configuration, a two-position switching type that supplies and discharges the working fluid to and from the common flow path, and a release control valve with one output port can be used. Therefore, the configuration of the release control valve is simpler than that having two output ports so that the working fluid is separately supplied to and discharged from the first intermediate lock mechanism and the second intermediate lock mechanism. It is not necessary to form two flow paths for supplying and discharging the working fluid to the first intermediate lock mechanism and the second intermediate lock mechanism.

In the valve opening / closing timing control device according to the present invention, the first lock member and the second lock member provided on either one of the drive side rotation member and the driven side rotation member, the drive side rotation member, A first concave portion, a second concave portion, and a third concave portion provided together on either one of the driven side rotating member, and at least one of the first locking member and the second locking member is the first concave portion. It is preferable that the relative rotation phase is constrained to the first intermediate lock phase, the second intermediate lock phase, and the most retarded angle lock phase by fitting with at least one of the second recess and the third recess. is there.

With such a characteristic configuration, there is no need to provide a lock member and a recess for each of the first intermediate lock mechanism, the second intermediate lock mechanism, and the most retarded angle lock mechanism. It can be reduced and the cost can be reduced, and the entire apparatus can be reduced in size.

It is a longitudinal section showing the composition of the valve timing control device concerning a 1st embodiment. FIG. 2 is a sectional view taken along line II-II in FIG. 1 and shows a first intermediate lock phase state. It is sectional drawing showing the 2nd intermediate | middle lock | rock phase state of a valve opening / closing timing control apparatus. It is sectional drawing showing the most retarded angle lock phase state of a valve opening / closing timing control apparatus. It is sectional drawing showing the structure of an orifice part. FIG. 6 is a sectional view taken along line VI-VI in FIG. 5. It is a schematic diagram showing the lock mechanism and fluid control mechanism at the time of a 1st intermediate | middle lock phase. It is a schematic diagram showing the lock mechanism and the fluid control mechanism when the relative rotation phase changes from the first intermediate lock phase to the second intermediate lock phase. It is a schematic diagram showing the lock mechanism and fluid control mechanism at the time of a 2nd intermediate | middle lock phase. It is a schematic diagram showing the lock mechanism and fluid control mechanism at the intermediate phase between the second intermediate lock phase and the most retarded lock phase. It is a schematic diagram showing the lock mechanism and fluid control mechanism at the time of the most retarded angle lock phase. It is a time chart of control of a valve timing control device. It is sectional drawing showing the 1st intermediate | middle lock | rock phase state of the valve timing control apparatus which concerns on other embodiment.

1. First embodiment [basic configuration]
Hereinafter, a first embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal sectional view showing the configuration of the valve timing control apparatus 10 according to this embodiment, and FIG. 2 is a sectional view taken along line II-II in FIG. As shown in FIGS. 1 and 2, a valve opening / closing timing control device 10 that sets an opening / closing timing of an intake valve (not shown) of an engine E as an internal combustion engine, and an engine control unit (ECU) 40 that controls the engine E. An internal combustion engine control system including the above is configured.

  The internal combustion engine control system according to the present embodiment realizes idling stop control for stopping the engine E when the vehicle stops due to a signal or the like. This internal combustion engine control system can also be applied to the case where the valve opening / closing timing control device 10 and the engine E are controlled in a vehicle in which the engine E is frequently stopped and started, such as a hybrid vehicle.

  An engine E shown in FIG. 1 is provided in a vehicle such as a passenger car, and includes a starter motor M that transmits driving rotational force to the crankshaft 1, and a fuel control device 5 that controls fuel injection into an intake port or a combustion chamber. , An ignition control device 6 that controls ignition by a spark plug (not shown), and a shaft sensor 1S that detects a rotation angle and a rotation speed of the crankshaft 1 are provided. The valve timing control device 10 is provided with a phase detection sensor 46 that detects the relative rotational phase between the external rotor 11 and the internal rotor 12.

  The ECU 40 includes an engine control unit 41 and a phase control unit 42. The engine control unit 41 automatically starts and stops the engine E, and the phase control unit 42 controls the relative rotation phase of the valve opening / closing timing control device 10 and the lock mechanism. A control configuration and control mode related to the ECU 40 will be described later.

[Valve opening / closing timing control device]
As shown in FIG. 1, the valve opening / closing timing control device 10 opens and closes an external rotor 11 as a drive side rotating member that rotates synchronously with the crankshaft 1 of the engine E, and an intake valve (not shown) in the combustion chamber of the engine E. And an internal rotor 12 as a driven side rotating member connected to the camshaft 3 to be connected by a connecting bolt 13. The internal rotor 12 is disposed coaxially with the axis X of the camshaft 3, and the internal rotor 12 and the external rotor 11 are configured to be relatively rotatable about the axis X.

  The outer rotor 11 and the inner rotor 12 are arranged on the same axis as the axis X, and are fastened by fastening bolts 16 while being sandwiched between the front plate 14 and the rear plate 15. A timing sprocket 15 </ b> S is formed on the outer periphery of the rear plate 15. The central portion of the inner rotor 12 is disposed so as to pass through an opening formed in the central portion of the rear plate 15, and the intake-side camshaft 3 is connected to the end portion of the inner rotor 12 on the rear plate 15 side.

  As shown in FIG. 2, the outer rotor 11 is integrally formed with a plurality of projecting portions 11 </ b> T that project toward the direction of the axis X (inward in the radial direction). The internal rotor 12 is formed in a cylindrical shape having an outer periphery that is in close contact with the protruding ends of the plurality of protruding portions 11T. Thereby, the fluid pressure chamber C is formed between the protrusions 11T adjacent in the rotation direction. A plurality of vanes 17 are provided on the outer periphery of the inner rotor 12 as partitioning portions that are fitted so as to protrude toward the fluid pressure chamber C. The fluid pressure chamber C partitioned by the vane 17 is divided into an advance chamber Ca and a retard chamber Cb in the rotational direction.

  As shown in FIG. 1, relative rotation from the state where the relative rotation phase between the external rotor 11 and the internal rotor 12 (hereinafter referred to as relative rotation phase) is at the most retarded angle across the internal rotor 12 and the front plate 14. A torsion spring 18 is provided for applying a biasing force until the phase reaches the first intermediate lock phase P1. The range in which the urging force of the torsion spring 18 acts may exceed the first intermediate lock phase P1 or may not reach the first intermediate lock phase P1.

  This valve opening / closing timing control device 10 winds the timing chain 8 across the output sprocket 7 provided on the crankshaft 1 of the engine E and the timing sprocket 15S of the external rotor 11, so that the external rotor 11 is connected to the crankshaft. 1 and rotate synchronously. Although not shown in the drawings, the front end of the camshaft 3 on the exhaust side is provided with a device having the same configuration as the valve opening / closing timing control device 10, and the rotational force is transmitted from the timing chain 8 to this device as well. Is done.

  As shown in FIG. 2, in the valve opening / closing timing control device 10, the external rotor 11 rotates in the driving rotation direction S by the driving force from the crankshaft 1. A direction in which the internal rotor 12 rotates in the same direction as the drive rotation direction S with respect to the external rotor 11 is referred to as an advance angle direction Sa, and a rotation direction in the opposite direction is referred to as a retard angle direction Sb. In this valve opening / closing timing control device 10, when the relative rotational phase is displaced in the advance angle 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 camshaft 3 is set so as to reduce the intake compression ratio as it increases.

  Of the fluid pressure chambers C partitioned by the vanes 17, a space that displaces the relative rotational phase in the advance angle direction Sa by supplying hydraulic oil as the working fluid is the advance angle chamber Ca. The space that displaces the relative rotational phase in the retarding direction Sb by supplying hydraulic oil is the retarding chamber Cb. The relative rotational phase in a state where the vane 17 has reached the moving end in the advance direction (the swing end about the axis X) is referred to as the most advanced angle phase, and the vane 17 is moved on the retard side (the axis core). The relative rotational phase in the state of reaching the rocking end centered on X is called the most retarded phase. The most advanced angle phase is a concept including not only the moving end of the vane 17 in the advance direction but also the vicinity thereof. Similarly, the most retarded phase is a concept including not only the moving end of the vane 17 in the retarded direction but also the vicinity thereof.

  The internal rotor 12 has an advance angle control oil passage 21 communicating with the advance angle chamber Ca, a retard angle control oil passage 22 communicated with the delay angle chamber Cb, and a main release oil that supplies hydraulic oil to three lock mechanisms described later. A path 23 is formed. In this valve opening / closing timing control device 10, the lubricating oil stored in the oil pan 1A of the engine E is used as the working oil (working fluid), and this working oil is supplied to the advance chamber Ca or the retard chamber Cb. .

[Valve opening / closing timing control device: Lock mechanism]
The valve opening / closing timing control device 10 includes three lock mechanisms, a first intermediate lock mechanism L1, a second intermediate lock mechanism L2, and a most retarded angle lock mechanism L3. The first intermediate lock mechanism L1 has a function of locking the relative rotation phase between the external rotor 11 and the internal rotor 12 to the first intermediate lock phase P1 shown in FIG. 2 and releasing the lock. The second intermediate lock mechanism L2 has a function of locking the relative rotation phase to the second intermediate lock phase P2 shown in FIG. 3 in the retarding direction Sb from the first intermediate lock phase P1 and releasing the lock. The most retarded angle lock mechanism L3 has a function of locking the relative rotation phase to the most retarded angle lock phase P3 corresponding to the most retarded angle phase shown in FIG. 4 and releasing the lock.

  The first intermediate lock phase P1 is set to a predetermined phase between the most advanced angle phase at which the relative rotational phase becomes the operating end in the advance direction Sa and the most retarded phase at the operating end in the retarded direction Sb. This is a relative rotation phase that can satisfactorily start the engine E in a state. The second intermediate lock phase P2 is a relative rotation phase that can suppress the HC emission amount during idling after the engine E is started. The most retarded angle locking phase P3 is a relative rotation phase for cranking the engine E that is stopped in a high temperature state (the engine E that has not passed time since the stop) with low torque.

  2 to 4, the first intermediate lock mechanism L1, the second intermediate lock mechanism L2, and the most retarded angle lock mechanism L3 include a first lock member 31, a second lock member 32, and a first recess. 35, a second recess 36, and a third recess 37.

  The first lock member 31 and the second lock member 32 are configured by plate-like members, and can be moved back and forth with respect to the external rotor 11 so as to be able to approach and separate in the direction of the axis X in a posture parallel to the axis X. It is supported. The first lock member 31 projects in the direction of the internal rotor 12 by the biasing force of the first spring 31S, and the second lock member 32 projects in the direction of the internal rotor 12 by the biasing force of the second spring 32S.

  The first recess 35 is formed in a groove shape along the axial direction of the outer periphery of the inner rotor 12. The circumferential groove width is wider than the thickness of the first lock member 31. The second recess 36 is formed in a groove shape along the axial direction of the outer periphery of the inner rotor 12. The depth of the groove is shallower than that of the first recess 35, and the second recess 36 is formed at the end in the advance direction. A fitting recess 36A for fitting with the two lock member 32 is formed continuously. The groove depth of the fitting recess 36 </ b> A is the same as the groove depth of the first recess 35. The groove width in the circumferential direction of the entire second recess 36 is wider than the groove width of the first recess 35, and the groove width of the fitting recess 36A is a width that allows the second lock member 32 to be fitted without a gap. The third recess 37 is formed in a groove shape along the axial direction of the inner rotor 12. The circumferential groove width is formed such that the first lock member 31 can be fitted without a gap.

  As shown in FIG. 2, in the first intermediate lock phase P <b> 1, the first lock member 31 fitted to the first recess 35 abuts on the end portion of the inner surface of the first recess 35 in the advance direction Sa, and the second The second lock member 32 fitted to the recess 36 is in contact with the end of the inner surface of the second recess 36 in the retarding direction Sb.

  As described above, the first intermediate lock mechanism L1 is composed of the first lock member 31, the first recess 35, the second lock member 32, and the second recess 36, thereby changing the relative rotation phase to the first intermediate lock phase. Restrain (lock) to P1.

  The second intermediate lock phase P2 is obtained by displacing the relative rotation phase in the retarding direction Sb after the first lock member 31 is retracted from the first recess 35 in a state where the relative rotation phase is at the first intermediate lock phase P1. This is the phase when the second lock member 32 is fitted into the fitting recess 36A. FIG. 3 is a cross-sectional view showing the second intermediate lock phase P2 state of the valve opening / closing timing control device 10. As shown in FIG.

  As described above, the second intermediate lock mechanism L2 includes the second lock member 32 and the second recess 36, particularly the fitting recess 36A, thereby locking the relative rotational phase to the second intermediate lock phase P2.

  In the second intermediate lock phase P2, the configuration in which the second lock member 32 is fitted to the fitting recess 36A of the second recess 36 is not essential. The second intermediate lock mechanism L2 may be configured by the second recess 36 in which only the shallow groove is formed without the fitting recess 36A. Thus, in the configuration not including the fitting recess 36A, the second lock member 32 abuts against the wall surface of the second recess 36 in the retarding direction Sb to restrict the rotation in the second intermediate lock phase P2.

  The most retarded angle lock phase P3 is obtained by moving the second lock member 32 out of the second recess 36 in a state where the relative rotation phase is at the second intermediate lock phase P2, and further displacing the relative rotation phase in the retard angle direction Sb. The phase when the first lock member 31 is fitted in the third recess 37. FIG. 4 is a sectional view showing the state of the most retarded lock phase P3 of the valve opening / closing timing control device 10.

  Thus, in the valve opening / closing timing control device 10, there is no need to provide a dedicated lock member and a recess for each of the first intermediate lock mechanism L1, the second intermediate lock mechanism L2, and the most retarded angle lock mechanism L3. The lock member 31, the second lock member 32, and the first recess 35, the second recess 36, and the third recess 37 are combined. Accordingly, it is possible to reduce the number of components of the valve opening / closing timing control device 10 and reduce the cost, and to reduce the size of the entire device.

[Valve opening / closing timing control device: oil passage configuration]
As shown in FIGS. 2 to 4, the first release oil passage 23 </ b> A for supplying and discharging the hydraulic oil in the main release oil passage 23 (an example of a common flow passage) to the first recess 35, and the hydraulic oil in the main release oil passage 23. Are formed in the inner rotor 12. The second release oil passage 23 </ b> B supplies and discharges the oil to and from the second recess 36, and the third release oil passage 23 </ b> C supplies and discharges the hydraulic oil in the main release oil passage 23 to the third recess 37. .

  In particular, in order to suppress the flow of hydraulic oil supplied from the main release oil passage 23 to the second recess 36 via the second release oil passage 23B, the oil passage system is provided with an orifice portion R as a delay portion. ing. As described above, the fitting recess 36 </ b> A is formed in the second recess 36. An orifice portion R is formed in the second release oil passage 23B connected to the radially inner side of the fitting recess 36A. FIG. 5 is a cross-sectional view illustrating the configuration of the orifice portion R.

  As shown in FIG. 5, the orifice portion R includes a ball 26 movably accommodated in the second release oil passage 23B, a cylindrical seat 27 fitted in the second release oil passage 23B, and a ball 26. A horn-shaped contact surface 27S that is in contact with each other, and a spring 28 that is interposed between the seat 27 and the ball 26 so as to apply a biasing force in a direction in which the ball 26 is separated from the contact surface 27S. The seat 27 is formed with a groove 27A that allows the hydraulic oil to flow even when the ball 26 comes into contact with the contact surface 27S. FIG. 6 is a sectional view taken along line VI-VI in FIG. As shown in FIG. 6, the second release oil when the ball 26 is in contact with the contact surface 27S by making the flow path cross-sectional area of the groove 27A smaller than the flow path cross-sectional area of the first release oil passage 23A. The hydraulic oil flowing through the passage 23B (groove 27A) has a higher flow resistance than the hydraulic oil flowing through the first release oil passage 23A.

  The spring 28 is provided in order to prevent the ball 26 from coming into contact with the contact surface 27S by the centrifugal force generated when the internal rotor 12 is rotated by the biasing force. In addition, a regulation pin 29 that contacts the ball 26 and determines the position of the ball 26 in a state where the urging force is applied is formed inside the second release oil passage 23B.

  With this configuration, when the hydraulic oil is supplied from the main release oil passage 23 to the second lock member 32, the orifice portion R causes the ball 26 to come into contact with the contact surface 27 </ b> S because the pressure of the hydraulic oil exceeds the urging force of the spring 28. In contact with the hydraulic fluid, and the hydraulic fluid flows only through the groove 27A. Thereby, a flow-path cross-sectional area becomes small and the flow of hydraulic fluid is suppressed. When the hydraulic oil is discharged from the second recess 36, the ball 26 is separated from the contact surface 27S by the hydraulic pressure and the urging force of the spring 28, so that the hydraulic oil also flows through the second release oil passage 23B in the orifice portion R. . As a result, the flow resistance at the time of discharge becomes small, and the hydraulic oil discharged through the second release oil passage 23B is discharged in the same manner as the hydraulic oil discharged through the first release oil passage 23A. The

  Thus, by providing the orifice portion R, when hydraulic oil is supplied to the main release oil passage 23 in the first intermediate lock phase P1, the hydraulic fluid is supplied to the first recess 35 in a short time. The first lock member 31 can be retracted from the first recess 35 within a short time. On the other hand, in the supply of the hydraulic oil to the second recess 36, the flow of the hydraulic oil is restricted by the orifice portion R. Therefore, the retraction of the second lock member 32 from the second recess 36 is the first lock member. Slower than leaving 31. That is, when the first lock member 31 is retracted from the first recess 35, the second lock member 32 is still in a state of being fitted with the second recess 36, and the fitting state is maintained for a while thereafter.

  Thus, by utilizing the phenomenon that the withdrawal of the second lock member 32 with respect to the first lock member 31 is delayed, the second lock member 32 and the second recess 36 are securely retracted while the first lock member 31 is reliably retracted. The state which maintains a fitting is realizable. As a result, the transition from the first intermediate lock phase P1 to the second intermediate lock phase P2 can be reliably performed.

  Note that the orifice portion R as the delay portion may be configured by using a poppet valve instead of the ball 26, or by providing an orifice passage in parallel with the passage provided with the ball 26 or the poppet valve. .

  Thus, by providing the main release oil passage 23, it is not necessary to individually form the oil passage for each of the first intermediate lock mechanism L1, the second intermediate lock mechanism L2, and the most retarded angle lock mechanism L3. It is possible to reduce the number of processing steps for the oil passage of the timing control device 10 and reduce the cost. Further, since the volume occupied by the oil passage can be reduced, the valve opening / closing timing control device 10 can be reduced in size.

[Fluid control mechanism of valve timing control device]
As shown in FIG. 1, the engine E includes a hydraulic pump 20 that sucks the lubricating oil in the oil pan 1 </ b> A with the driving force of the engine E and sends it out as hydraulic oil. In the internal combustion engine control system according to the present embodiment, an electromagnetically operated type that supplies hydraulic oil discharged from the hydraulic pump 20 by selectively selecting one of the advance chamber Ca and the retard chamber Cb of the valve timing control device 10. A phase control valve 24 and an electromagnetically operated release control valve 25 that supplies hydraulic oil discharged from the hydraulic pump 20 to the main release oil passage 23 are provided. In particular, the fluid control mechanism of the valve opening / closing timing control device 10 is configured by combining the hydraulic pump 20, the phase control valve 24, the release control valve 25, and the oil passage through which hydraulic oil is supplied and discharged.

  The phase control valve 24 is configured as an electromagnetic valve that can be switched between an advance position, a retard position, and a neutral position by a control signal. That is, at the advance angle position, the hydraulic oil discharged from the hydraulic pump 20 flows through the advance angle control oil passage 21 and is supplied to the advance angle chamber Ca, and the hydraulic oil in the retard angle chamber Cb is retarded. 22 is discharged. In the retard position, the hydraulic oil discharged from the hydraulic pump 20 flows through the retard control oil passage 22 and is supplied to the retard chamber Cb, and the hydraulic oil in the advance chamber Ca passes from the advance control oil passage 21. Discharged. In the neutral position, no hydraulic oil is supplied or discharged in either the advance chamber Ca or the retard chamber Cb. When the phase control valve 24 is energized with 100% duty, the phase control valve 24 is in the advanced position, and when the energization is cut off, it is in the retarded position.

  The release control valve 25 is configured as an electromagnetic valve that can be switched between an unlock position and a lock position by a control signal from the ECU 40. That is, at the unlock position, the hydraulic oil discharged from the hydraulic pump 20 flows through the main release oil passage 23 and is supplied to the first recess 35, the second recess 36, and the third recess 37. In the lock position, the first and second lock members 31 and 32 are discharged through the main release oil passage 23 and the hydraulic oil is discharged from the first recess 35, the second recess 36, and the third recess 37, respectively. Can be fitted into any of the first recess 35, the second recess 36, and the third recess 37, respectively. The release control valve 25 is in the locked position when the release control valve 25 is energized, and the unlock position when the energization is cut off.

[Control configuration]
As shown in FIG. 1, signals from the shaft sensor 1 </ b> S, the ignition switch 43, the accelerator pedal sensor 44, the brake pedal sensor 45, and the phase detection sensor 46 are input to the ECU 40. The ECU 40 outputs signals for controlling the starter motor M, the fuel control device 5, and the ignition control device 6, and outputs signals for controlling the phase control valve 24 and the release control valve 25.

  The ignition switch 43 is configured as a switch for starting the internal combustion engine control system, and starts the engine E by an ON operation and stops the engine E by an OFF operation. Further, when the ON operation is performed, the engine E can be automatically stopped and automatically started by the idling stop control.

  The accelerator pedal sensor 44 detects the amount of depression of an accelerator pedal (not shown), and the brake pedal sensor 45 detects depression of a brake pedal (not shown).

  The engine control unit 41 realizes start and stop of the engine E based on the operation of the ignition switch 43 and realizes idling stop control that temporarily stops the engine E when the engine E stops in an idling state. .

  The phase control unit 42 performs the intake valve timing control by the valve opening / closing timing control device 10 during operation of the engine E, and sets the relative rotation phase of the valve opening / closing timing control device 10 based on the situation when the engine E stops. The transition to the locked state by the lock mechanism is realized.

[Control form: Normal start control]
Next, control modes of the internal combustion engine control system according to the present embodiment will be described with reference to FIGS. The control of the phase control valve 24 from the start of the engine E to the stop of the engine E, the control of the release control valve 25, the displacement of the relative rotational phase, the state of the first intermediate lock mechanism L1, and the state of the second intermediate lock mechanism L2 FIG. 12 shows a time chart of the state of the most retarded angle locking mechanism L3.

  In a state where the engine E is stopped at a low temperature, the relative rotational phase is locked to the first intermediate lock phase P1 by the first intermediate lock mechanism L1. FIG. 7 is a schematic diagram showing the lock mechanism and the fluid control mechanism when the relative rotational phase is the first intermediate lock phase P1.

  When the engine E is stopped at a low temperature, the hydraulic oil is discharged from the advance chamber Ca and the retard chamber Cb. The release control valve 25 is in the unlock position, but hydraulic oil is discharged from any of the first recess 35, the second recess 36, and the third recess 37. The first lock member 31 fitted to the first recess 35 abuts the end portion of the inner surface of the first recess 35 in the advance direction Sa, and the second lock member 32 fitted to the second recess 36 is the second. The inner surface of the recess 36 is in contact with the end of the retarding direction Sb.

  In this state, when the ignition switch 43 is artificially turned on, the engine control unit 41 rotates the starter motor M to supply fuel to the combustion chamber by the fuel control device 5, and the ignition control device 6 ignites the spark plug. As a result, the engine E is started and idling operation (before catalyst warm-up) is started. At this time, the release control valve 25 is energized simultaneously with the ON operation of the ignition switch 43, the release control valve 25 is switched to the lock position, and the state of the first intermediate lock phase P1 by the first intermediate lock mechanism L1 is maintained. Thus, since the relative rotation phase can be constrained to the first intermediate lock phase P1 between the most advanced angle phase and the most retarded angle phase by the first intermediate lock mechanism L1, the engine E can be started stably. Can do.

  Even if the catalyst warm-up is completed, if the relative rotation phase is maintained at the first intermediate lock phase P1, the HC emission amount increases. Therefore, the phase control unit 42 performs control to shift the relative rotation phase to the second intermediate lock phase P2 suitable for idling operation (after catalyst warm-up) and shift to the locked state by the second intermediate lock mechanism L2. Thereby, the HC discharge amount at the time of idling can be suppressed. At the same time, the phase control unit 42 continues the energization disconnection to the phase control valve 24 to maintain the retard position, and performs retard control.

  As a specific operation mode for shifting to the locked state by the second intermediate lock mechanism L2, the phase control unit 42 has a preset time (hereinafter, referred to as “required”) required to retract the first lock member 31 from the first recess 35. The release control valve 25 is energized only for a set time). With this energization, the release control valve 25 is switched from the locked position to the unlocked position, and hydraulic oil is supplied to the main release oil passage 23 for a set time.

  When the hydraulic oil is supplied only for the set time described above, the hydraulic oil directly acts on the first lock member 31 from the first release oil passage 23 </ b> A and causes the first lock member 31 to be retracted from the first recess 35. At this time, the hydraulic oil is also supplied to the second release oil passage 23B at the same time, but since the orifice R is formed in the oil passage from the second release oil passage 23B to the second recess 36, The increase in pressure of the hydraulic oil acting on the second lock member 32 is suppressed, and the second lock member 32 does not exit from the second recess 36.

  As a specific operation mode of the orifice portion R, when the hydraulic oil is supplied to the second release oil passage 23B, the ball 26 is brought into contact with the contact surface 27S by the pressure of the hydraulic oil flowing through the second release oil passage 23B. The hydraulic oil flows through only the groove 27A. Accordingly, the amount of hydraulic oil flowing into the second recess 36 is limited, and when the first lock member 31 is retracted from the first recess 35, the second lock member 32 is sufficiently large to retract from the second recess 36. No hydraulic pressure is applied, and the fitted state is maintained.

  When the first lock member 31 retreats from the first recess 35, the relative rotation phase starts to be displaced in the retard direction Sb by the retard control of the phase control unit 42. FIG. 8 is a schematic diagram showing a lock mechanism and a fluid control mechanism when the relative rotation phase changes from the first intermediate lock phase P1 to the second intermediate lock phase P2. At this time, the release control valve 25 is energized again to enter the lock position, and the supply of hydraulic oil to the main release oil passage 23 has already stopped. Therefore, at the time of displacement in the retarding direction Sb, the second lock member 32 is in a state of being fitted with the second recess 36. When the relative rotational phase reaches the second intermediate lock phase P2, the second lock member 32 enters the fitting recess 36A of the second recess 36. Thus, the relative rotation phase is locked to the second intermediate lock phase P2 by the second intermediate lock mechanism L2. FIG. 9 is a schematic diagram showing the lock mechanism and the fluid control mechanism during the second intermediate lock phase P2.

  In the normal start control, the engine E is started in a situation where the temperature of the hydraulic oil is low and the viscosity is high. For this reason, when the engine E is started, the hydraulic fluid supplied from the hydraulic pump 20 to the second lock member 32 via the second release oil passage 23B receives a large flow resistance from the orifice R, and acts on the second lock member 32. The pressure rise is slow. Accordingly, after the hydraulic oil is supplied to the main release oil passage 23 and the first lock member 31 is withdrawn from the first recess 35, the time until the second lock member 32 is withdrawn from the second recess 36 becomes longer. Thereby, even if it is a case where the set time mentioned above is not set strictly, only the 1st lock member 31 can be surely withdrawn, and it can shift to the 2nd intermediate lock phase P2. Thus, since the relative rotation phase can be constrained to the second intermediate lock phase P2 by the second intermediate lock mechanism L2, it is possible to suppress the HC discharge amount during the idling operation.

[Control form: Normal operation control]
When the idling operation ends, the control of the internal combustion engine control system shifts to the normal operation control. The end of the disconnection is determined by the ECU 40 based on a detection result of a water temperature sensor (not shown) that detects the temperature of the cooling water flowing through the engine E. When shifting to the normal operation control, the phase control unit 42 performs control to cut off the energization to the release control valve 25 and switch from the lock position to the unlock position. By this operation, the hydraulic oil is supplied to the main release oil passage 23, and the second lock member 32 retreats from the second recess 36 (fitting recess 36A). Since the first lock member 31 has already retracted from the first recess 35, all the locked states between the outer rotor 11 and the inner rotor 12 are released. Thereafter, as long as the normal operation control is performed, the release of the locked state is maintained.

  Further, in the normal operation control, the phase control unit 42 operates the energization chamber Ca by energizing the phase control valve 24 to be in the advance position according to the load or rotation speed of the engine E during operation. The advance angle control for supplying hydraulic oil is performed, or the delay angle control for supplying the hydraulic oil to the retard chamber Cb is performed by turning off the energization to operate the retard position. As a result, the relative rotational phase is displaced toward the advance side with respect to the first intermediate lock phase P1, or as shown in FIG. 10, the relative rotation phase is displaced toward the retard side with respect to the second intermediate lock phase P2. Further, the relative rotation phase may be maintained at an arbitrary phase by operating the energized phase control valve 24 to the neutral position.

[Control form: idling stop control]
In idling stop control, when the brake pedal is depressed during normal operation and the vehicle stops (when the accelerator pedal is not operated), the engine E is temporarily stopped and the engine E is released when the brake pedal is released. The control mode is set so as to start. Thereby, useless fuel consumption can be suppressed and fuel consumption can be improved.

  When the engine E is stopped by the idling stop control, in the normal operation state, the energization to the phase control valve 24 is cut off and the working oil is supplied to the retarding chamber Cb to change the relative rotational phase to the retarding direction Sb. Displace to. Thereafter, when the relative rotational phase reaches the vicinity of the most retarded angle phase, the release control valve 25 is energized to switch to the lock position, and the hydraulic oil is discharged from the third recess 37. Then, when the relative rotation phase reaches the most retarded lock phase P3, the first lock member 31 is fitted with the third recess 37, and the first lock member 31 is locked by the most retarded lock mechanism L3. Thereafter, the engine control unit 41 stops the fuel supply to the combustion chamber by the fuel control device 5 and stops the ignition by the ignition control device 6 to stop the engine E. FIG. 11 is a schematic diagram showing a lock mechanism and a fluid control mechanism at the time of the most retarded lock phase P3.

  In the idling stop control, since the engine E is started at a high temperature, the mixture is easily ignited. Further, when cranking is performed with the relative rotational phase set to the most retarded angle, the crankshaft 1 can be smoothly rotated with a light load. For this reason, when the engine E is stopped by the idling stop control, the engine is locked at the most retarded angle lock phase P3. Thereafter, when the brake pedal is depressed and the engine E is started, cranking by the starter motor M is started.

  When the rotational speed of the crankshaft 1 reaches a preset value due to this cranking, the phase control unit 42 cuts off the energization of the release control valve 25 and switches it to the unlock position, whereby the first lock member 31 is moved. Retreat from the third recess 37 to unlock the most retarded angle locking mechanism L3. In parallel with this control, by switching the phase control valve 24 to the advance angle position, the fuel control device 5 supplies fuel to the combustion chamber while the relative rotation phase is shifted to the advance angle direction Sa. The engine E is restarted by igniting with a spark plug. As described above, since the relative rotation phase can be constrained to the most retarded angle lock phase P3 by the most retarded angle lock mechanism L3 at the start of idling stop, the vane 17 swings in the retarded angle direction and the advanced angle direction. It is possible to stably start the engine E by preventing the occurrence of noise.

[Control form: Normal stop control]
Before the ignition switch 43 is artificially turned off in a state where the engine E is operating, a stop operation is performed and an idling operation is performed. The relative rotational phase at this time is the most retarded phase. When the ignition switch 43 is artificially turned off, the ECU 40 sets the internal combustion engine control system to the engine stop mode. In the engine stop mode, the engine E is not stopped immediately, but the phase control unit 42 is energized to the phase control valve 24 to operate to the advance position to supply hydraulic oil to the advance chamber Ca, and the relative rotation phase is set. Transition to the first intermediate lock phase P1 shown in FIG. At this transition, the release control valve 25 is in the unlock position, but when it reaches the vicinity of the first intermediate lock phase P1, the release control valve 25 is energized to switch to the lock position, and the first recess 35, the second recess 36, The hydraulic oil is discharged from the third recess 37. Thereafter, the first intermediate lock mechanism P1 reaches the locked state in the first intermediate lock phase P1.

  In this locked state, the first lock member 31 is in contact with the end portion of the inner surface of the first recess 35 in the advance direction Sa in a state where the first lock member 31 is engaged with the first recess 35 by the urging force of the first spring 31S. Further, the second lock member 32 is fitted into the second recess 36 by the urging force of the second spring 32S, and abuts on the end portion of the inner surface of the second recess 36 in the retarding direction Sb.

  After the transition to the first intermediate lock phase P1 is completed, the engine control unit 41 stops the fuel supply to the combustion chamber by the fuel control device 5 and stops the ignition by the ignition control device 6 to stop the engine E. . After the engine E is completely stopped, the power supply to the release control valve 25 is cut off. If the engine E is stopped at the first intermediate lock phase P1, the engine E in the low temperature state can be started next time.

[Operations and effects of the first embodiment]
As described above, in the present embodiment, when the engine E is stopped by the idling stop control, the relative rotation phase is displaced to the most retarded angle lock phase P3, and the state is shifted to a state in which the engine is locked by the most retarded angle lock mechanism L3. When restarting the engine E after this, a light cranking is realized by a low compression ratio.

  Further, when the driver turns off the ignition switch 43 to stop the engine E, the relative rotational phase is displaced to the first intermediate lock phase P1 and the state is shifted to the locked state by the first intermediate lock mechanism L1. Engine E is stopped. As a result, the engine E can be reliably started next time at a low temperature.

  After starting the engine E, it is possible to maintain the state where the second lock member 32 is fitted to the second recess 36 by only performing control for supplying hydraulic oil to the main release oil passage 23 for a set time. The first lock member 31 can be withdrawn from the first recess 35. Then, the transition to the second intermediate lock phase P2 can be reliably performed.

  Since the hydraulic oil is supplied from the single main release oil passage 23 to the first intermediate lock mechanism L1 and the second intermediate lock mechanism L2 in this way, It is a two-position switching type that performs discharging, and the output side port can use one release control valve 25. Therefore, the configuration of the release control valve 25 is simpler than that provided with two ports on the output side so as to supply and discharge hydraulic fluid separately to the first intermediate lock mechanism L1 and the second intermediate lock mechanism L2. Thus, it is not necessary to form two oil passages for supplying and discharging hydraulic oil to / from the release control valve 25, the first intermediate lock mechanism L1, and the second intermediate lock mechanism L2.

  In the present embodiment, the single main release oil passage 23 branches to the first release oil passage 23A, the second release oil passage 23B, and the third release oil passage 23C. However, the present invention is not limited to this. . Each of the first release oil passage 23A, the second release oil passage 23B, and the third release oil passage 23C may be configured as an independent oil passage. In that case, it is necessary to provide a release control valve independently.

2. Other Embodiments Next, other embodiments of the present invention will be described in detail with reference to the drawings. In the description of the present embodiment, parts having the same configuration as in the first embodiment are denoted by the same reference numerals, and description of the same configuration is omitted.

  In FIG. 13, the cross-sectional view of the valve timing control apparatus 10 which concerns on this embodiment is shown. As shown in FIG. 13, the main release oil passage 23 branches into a first release oil passage 23 </ b> A that supplies and discharges hydraulic oil to the first recess 35 and a second release oil passage 23 </ b> B that supplies and discharges the second recess 36. doing. The hydraulic oil is supplied to and discharged from the third recess 37 by the advance angle control oil passage 21.

  The most retarded angle locking mechanism L3 fits the first locking member 31 into the third recess 37 when the relative rotation phase is in the most retarded angle locking phase P3. At this time, the hydraulic oil is discharged from both the third recess 37 and the advance chamber Ca. Conversely, when the relative rotational phase is not in the state of the most retarded angle lock phase P3, the first lock member 31 is withdrawn from the third recess 37, and hydraulic oil is supplied to the third recess 37 and the advance chamber Ca. ing.

  That is, the supply / discharge timing of the hydraulic oil to the third recess 37 and the supply / discharge timing of the hydraulic oil to the advance chamber Ca are the same. Therefore, even in the structure in which the hydraulic oil is supplied to and discharged from the third recess 37 by the advance angle control oil passage 21 as in this embodiment, the most retarded angle locking mechanism L3 operates correctly.

  The present invention can be used for 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.

DESCRIPTION OF SYMBOLS 1 Crankshaft 3 Camshaft 10 Valve opening / closing timing control apparatus 11 External rotor (drive side rotating member)
12 Internal rotor (driven side rotating member)
17 Vane (partition)
20 Hydraulic pump (fluid control mechanism)
21 Lead angle control oil passage (fluid control mechanism)
22 Retardation control oil passage (fluid control mechanism)
23 Main release oil path (fluid control mechanism, common flow path)
24 Phase control valve (fluid control mechanism)
25 Release control valve (fluid control mechanism)
31 1st locking member 32 2nd locking member 35 1st recessed part 36 2nd recessed part 37 3rd recessed part E Engine (internal combustion engine)
C Fluid pressure chamber Ca Advance angle chamber Cb Delay angle chamber L1 First intermediate lock mechanism L2 Second intermediate lock mechanism L3 Most retarded angle lock mechanism P1 First intermediate lock phase P2 Second intermediate lock phase P3 Most retarded angle lock phase R Orifice Part (delay part)

Claims (3)

A drive-side rotating member that rotates synchronously with the crankshaft of the internal combustion engine;
A driven-side rotating member that is arranged coaxially with the drive-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 by the driving side rotating member and the driven side rotating member;
An advance chamber and a retard chamber formed by partitioning the fluid pressure chamber with a partition provided in at least one of the driving side rotating member and the driven side rotating member;
A fluid control mechanism for controlling supply and discharge of the working fluid to and from the fluid pressure chamber;
A first intermediate lock mechanism that restricts or releases the relative rotation phase of the driven side rotation member with respect to the driving side rotation member to a first intermediate lock phase between a most advanced angle phase and a most retarded angle phase; ,
A most retarded angle locking mechanism for constraining the relative rotation phase to the most retarded angle lock phase, or releasing the constraint;
A second intermediate lock mechanism that constrains the relative rotational phase to a second intermediate lock phase between the first intermediate lock phase and the most retarded angle lock phase, or releases the constraint ;
The first intermediate lock mechanism, the second intermediate lock mechanism, and the most retarded angle lock mechanism, each having a common flow path that is a common portion for supplying and discharging the working fluid,
When the working fluid is supplied to the first intermediate lock mechanism and the second intermediate lock mechanism, the working fluid reaches the second intermediate lock mechanism rather than the working fluid reaches the first intermediate lock mechanism. A valve opening / closing timing control device provided with a delay unit that is delayed . A drive-side rotating member that rotates synchronously with the crankshaft of the internal combustion engine;
A driven-side rotating member that is arranged coaxially with the drive-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 by the driving side rotating member and the driven side rotating member;
An advance chamber and a retard chamber formed by partitioning the fluid pressure chamber with a partition provided in at least one of the driving side rotating member and the driven side rotating member;
A fluid control mechanism for controlling supply and discharge of the working fluid to and from the fluid pressure chamber;
A first intermediate lock mechanism that restricts or releases the relative rotation phase of the driven side rotation member with respect to the driving side rotation member to a first intermediate lock phase between a most advanced angle phase and a most retarded angle phase; ,
A most retarded angle locking mechanism for constraining the relative rotation phase to the most retarded angle lock phase, or releasing the constraint;
A second intermediate lock mechanism that constrains the relative rotational phase to a second intermediate lock phase between the first intermediate lock phase and the most retarded angle lock phase, or releases the constraint;
A common flow path for supplying and discharging working fluid to and from the first intermediate lock mechanism and the second intermediate lock mechanism;
The flow path for supplying and discharging the working fluid to the most retarded angle locking mechanism is the same as the flow path for supplying and discharging the working fluid to the advance chamber,
When the working fluid is supplied to the first intermediate lock mechanism and the second intermediate lock mechanism, the working fluid reaches the second intermediate lock mechanism rather than the working fluid reaches the first intermediate lock mechanism. A valve opening / closing timing control device provided with a delay unit that is delayed . A first lock member and a second lock member provided together on either one of the drive side rotation member and the driven side rotation member;
A first concave portion, a second concave portion and a third concave portion provided on either one of the driving side rotating member and the driven side rotating member,
At least one of the first lock member and the second lock member is engaged with at least one of the first recess, the second recess, and the third recess, thereby setting the relative rotational phase to the first intermediate lock. The valve timing control apparatus according to claim 1 or 2 , wherein the valve timing control device is constrained to a phase, the second intermediate lock phase, and the most retarded angle lock phase.

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