JP2002349220A - Valve timing control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To quickly rotate a rotor member relative to a housing member to a target phase position between a most advanced phase position and a most retarded phase position in start-up of an internal combustion engine and to keep the rotor member roughly on the target phase position under a condition of releasing a lock of a relative rotation control mechanism in a process of shifting from a latter part of start-up to normal operation. SOLUTION: A hydraulic circuit, which can discharge hydraulic fluid from an advancing fluid chamber, a retarding fluid chamber and the relative rotation control mechanism until the pressure of hydraulic fluid gets to controllable pressure in start-up of the internal combustion engine, can supply hydraulic fluid repeatedly and alternately to the advancing fluid chamber and the retarding fluid chamber to fill the advancing fluid chamber and the retarding fluid chamber with hydraulic fluid after the pressure of the hydraulic fluid gets higher than the controllable pressure, and can supply hydraulic fluid to the relative rotation control mechanism thereafter, is adopted as a hydraulic circuit for controlling supply and discharge of hydraulic fluid to the advancing fluid chamber, the retarding fluid chamber and the relative rotation control mechanism.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve opening / closing timing control device (valve opening / closing timing adjusting device for an internal combustion engine) used for controlling the opening / closing timing of an intake valve or an exhaust valve in a valve gear of an internal combustion engine. .

[0002]

2. Description of the Related Art As one type of valve opening / closing timing control device of this type, a driving force transmission system for transmitting driving force from a crankshaft of an internal combustion engine to a camshaft for opening and closing an intake valve or an exhaust valve of the internal combustion engine is provided. A housing member rotatable integrally with the crankshaft or the camshaft, and an advancing oil chamber and a retarder mounted in the housing member at a vane portion so as to be rotatable relative to a shoe portion provided on the housing member. A rotor member forming a square oil chamber and rotating integrally with the camshaft or the crankshaft, and unlocking by supply of hydraulic oil to permit relative rotation of the housing member and the rotor member to discharge hydraulic oil The lock operation is performed so that the relative rotation of the housing member and the rotor member is performed at a target phase position in an intermediate region excluding a rotation limit position at both ends between the most advanced phase position and the most retarded phase position. And a hydraulic circuit for controlling the supply and discharge of hydraulic oil to and from the advance oil chamber, the retard oil chamber, and the relative rotation control mechanism. No. in the official gazette.

[0003]

In the above-described valve timing control apparatus, the relative rotation control mechanism controls the relative rotation of the housing member and the rotor member to the both-end rotation limit position between the most advanced phase position and the most retarded phase position. The opening and closing timings of the intake valve and the exhaust valve are set so that good startability of the internal combustion engine can be obtained in a state where the internal phase is regulated at the target phase position in the intermediate region excluding the above. For this reason, when the relative rotation control mechanism does not regulate the relative rotation between the housing member and the rotor member at the target phase position at the time of starting the internal combustion engine, the torque of the driving force transmission system including the fluctuating torque acting on the camshaft. Due to the fluctuation, the housing member and the rotor member may rotate relative to each other in an unstable manner, and the startability of the internal combustion engine may be impaired.

[0004] By the way, when starting the internal combustion engine, a factor that hinders the relative rotation control mechanism from regulating the relative rotation between the housing member and the rotor member at the target phase position (intermediate phase position) is the setting of the hydraulic circuit. And the hydraulic oil remains in the advance oil chamber, the retard oil chamber, and the relative rotation control mechanism. In addition, in the conventional hydraulic circuit, when starting the internal combustion engine, sufficient consideration has not been given to how to control the hydraulic control valve provided in the hydraulic circuit, and the process of shifting from the start of the internal combustion engine to the normal operation is not performed. In this case, there is a possibility that the relative rotation phase of the housing member and the rotor member becomes transiently unstable (the rotor member largely fluctuates on the advance side and the retard side with respect to the housing member).

[0005]

SUMMARY OF THE INVENTION According to the present invention, there is provided a valve opening / closing timing control apparatus for solving the above-mentioned problems.
As a hydraulic circuit for controlling the supply and discharge of hydraulic oil to the advance and retard oil chambers and the relative rotation control mechanism, after the hydraulic pressure of the hydraulic oil at the start of the internal combustion engine becomes equal to or higher than the controllable hydraulic pressure,
The advance oil chamber and the retard oil chamber can be supplied alternately and repeatedly with hydraulic oil to fill the advance oil chamber and the retard oil chamber with hydraulic oil, and then the relative rotation control can be performed. A hydraulic circuit capable of supplying hydraulic oil to the mechanism is employed.
Of the present invention).

In implementing the present invention, a control value of a hydraulic control valve provided in the hydraulic circuit when the hydraulic oil is alternately and repeatedly supplied to the advance oil chamber and the retard oil chamber is set as follows:
It is possible to set based on a control value for maintaining the relative rotational phase of the housing member and the rotor member during normal operation before the internal combustion engine is stopped (the invention according to claim 2). In this case, it is desirable to correct the control value of the hydraulic control valve according to the temperature of the hydraulic oil (the invention according to claim 3).

In the practice of the present invention, when the hydraulic oil is alternately and repeatedly supplied to the advance oil chamber and the retard oil chamber, the amount of hydraulic oil supplied at one time is increased by the advance oil amount. It is possible to make the angle oil chamber different from the retard oil chamber (the invention according to claim 4). In this case, the oil amount ratio of the hydraulic oil supplied to the advance oil chamber and the retard oil chamber at one time is determined by the advance oil chamber and the retard oil when the relative rotation control mechanism is locked. It is possible to set based on the volume ratio of the square oil chamber (the invention according to claim 5).

In practicing the present invention, the amount of hydraulic oil supplied to the advance oil chamber and the retard oil chamber at one time is detected by detecting the relative rotational phase of the housing member and the rotor member. (The invention according to claim 6) can be set based on the difference between the detected value (actual phase position) of the phase detecting means and the target phase position. Further, it is possible to sequentially reduce the amount of hydraulic oil supplied to the advance oil chamber and the retard oil chamber at one time in accordance with the elapsed time (the invention according to claim 7). Further, it is possible to determine that the hydraulic pressure of the hydraulic oil has become equal to or higher than the controllable hydraulic pressure at a predetermined elapsed time after the start of the internal combustion engine (the invention according to claim 8).

In practicing the present invention, when the internal combustion engine is started, the hydraulic circuit includes both the advance oil chamber and the retard oil chamber until the hydraulic oil pressure becomes controllable. It is desirable that hydraulic fluid can be discharged from the relative rotation control mechanism (the invention according to claim 9).

[0010]

In the valve opening / closing timing control device according to the present invention (the invention according to claim 1), at the time of starting the internal combustion engine, the starting oil pressure becomes higher than the controllable oil pressure after the hydraulic oil pressure becomes higher than the controllable oil pressure. The hydraulic circuit can alternately supply hydraulic oil to the advance oil chamber and the retard oil chamber repeatedly to fill the advance oil chamber and the retard oil chamber with hydraulic oil, and then control the relative rotation. Hydraulic oil can be supplied to the mechanism. For this reason, in the process of shifting from the latter half of the start-up of the internal combustion engine to the normal operation, the relative rotation phase of the housing member and the rotor member substantially coincides with the above-described target phase position in a state where the regulation (lock) by the relative rotation control mechanism is released. Can be held
The relative rotational phase between the housing member and the rotor member can be stabilized at a predetermined intermediate phase.

In the valve opening / closing timing control device according to the present invention (the invention according to claim 1), in the process of shifting from the latter half of the startup of the internal combustion engine to the normal operation, the hydraulic circuit is provided with an advance oil chamber and a retard oil chamber. Because the hydraulic oil is supplied alternately and repeatedly, even if the regulation (lock) by the relative rotation control mechanism is released before the advance oil chamber and the retard oil chamber are filled with the hydraulic oil, The relative rotation between the housing member and the rotor member can be suppressed by the hydraulic oil supplied to the advance oil chamber and the retard oil chamber by that time. Therefore, the relative rotational phase of the housing member and the rotor member can be prevented from being transiently unstable, and the rotor member flutters (vibrates) on the advance side and the retard side with respect to the housing member. Is suppressed.

Further, when the present invention is carried out, the control value of the hydraulic control valve provided in the hydraulic circuit when the hydraulic oil is alternately and repeatedly supplied to the advance oil chamber and the retard oil chamber is changed before the stop of the internal combustion engine. In the case of setting based on the control value for maintaining the relative rotation phase between the housing member and the rotor member during the normal operation (in the case of the invention according to claim 2), machine differences (variations in products) and deterioration over time are reduced. As a result, the desired hydraulic oil supply characteristics can always be obtained, and the desired operation responsiveness can be obtained. In this case, the control value of the hydraulic control valve is changed according to the temperature of the hydraulic oil (for example,
When the hydraulic oil temperature is high, the viscosity is low, so that the opening area of the hydraulic control valve is small, and when the hydraulic oil temperature is low, the viscosity is high, so that the opening area of the hydraulic control valve is large. In (in the case of the invention according to claim 3), the desired hydraulic oil supply characteristic is always obtained regardless of the temperature of the hydraulic oil, and the desired operation responsiveness can be obtained.

Further, when the present invention is carried out, when the hydraulic oil is supplied repeatedly and alternately to the advance oil chamber and the retard oil chamber,
In the case where the amount of hydraulic oil supplied each time is different between the advance oil chamber and the retard oil chamber (in the case of the invention according to claim 4), for example, the relative rotation control mechanism is in a locked state. When the volumes of the advance oil chamber and the retard oil chamber are different from each other, the working oil can be supplied to the advance oil chamber and the retard oil chamber with good balance.

In this case, the oil amount ratio of the hydraulic oil supplied to the advance oil chamber and the retard oil chamber at one time is determined by the ratio between the advance oil chamber and the retard oil when the relative rotation control mechanism is locked. In the case of setting based on the volume ratio of the chambers (in the case of the invention according to claim 5), before the advance oil chamber and the retard oil chamber are filled with the hydraulic oil, provisional control by the relative rotation control mechanism is performed. (Lock)
Is released, the hydraulic fluid supplied to the advance oil chamber and the retard oil chamber and the hydraulic oil subsequently supplied to the advance oil chamber and the retard oil chamber cause the rotor to rotate with respect to the housing member. The member can be moved and held toward the target phase position.

In practicing the present invention, the amount of hydraulic oil supplied to the advance oil chamber and the retard oil chamber at one time is determined by the amount of hydraulic oil supplied to the advance oil chamber and the retard oil chamber. In the case of setting based on the difference between the detected value (actual phase position) and the target phase position (in the case of the invention according to claim 6), before the advance oil chamber and the retard oil chamber are filled with hydraulic oil. Even if the regulation (lock) by the relative rotation control mechanism is released, the rotor member is moved to the target phase position with respect to the housing member by the hydraulic oil supplied to the advance oil chamber and the retard oil chamber thereafter. It is possible to move the rotor member toward the target phase position with respect to the housing member.

Further, when the present invention is carried out, the amount of hydraulic oil supplied to the advance oil chamber and the retard oil chamber at one time is sequentially reduced according to the elapsed time. In the case of the invention), a large amount of hydraulic oil can be supplied to the advance oil chamber and the retard oil chamber in the initial stage of supplying the hydraulic oil alternately and repeatedly to the advance oil chamber and the retard oil chamber. Hydraulic oil can be filled in the square oil chamber and the retard oil chamber in a short time, and the time required for shifting from the start of the internal combustion engine to the normal operation can be shortened.

Further, when the present invention is carried out, the determination that the hydraulic pressure of the hydraulic oil has become equal to or higher than the controllable hydraulic pressure is made at a predetermined elapsed time after the start of the internal combustion engine. In the case of the invention), the present invention can be implemented at low cost without using the oil pressure detecting means.

Further, in the valve timing control apparatus according to the present invention (invention of claim 9), when the internal combustion engine is started, the hydraulic circuit is connected to the hydraulic circuit at the initial stage until the hydraulic oil pressure becomes controllable hydraulic pressure. Hydraulic oil can be discharged from the advance oil chamber, the retard oil chamber, and the relative rotation control mechanism. Therefore, the hydraulic oil remaining in the advance oil chamber and the retard oil chamber at the initial stage of starting the internal combustion engine can be discharged, and the hydraulic oil does not hinder the relative rotation of the housing member and the rotor member.
Due to the torque fluctuation of the driving force transmission system, the rotor member can be quickly rotated relative to the housing member to the target phase position between the most advanced phase position and the most retarded phase position. Further, the hydraulic oil can be discharged from the relative rotation control mechanism at the initial stage of the start of the internal combustion engine, an accurate locking operation can be obtained by the relative rotation control mechanism, and the relative rotation between the housing member and the rotor member is set to the target phase. The position can be regulated precisely. Therefore, the startability of the internal combustion engine can be improved.

[0019]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below with reference to the drawings. The valve timing control apparatus according to the present invention shown in FIGS.
), A housing member 30 externally rotatable within a predetermined range on the rotor member 20, and a torsion spring S interposed between the housing member 30 and the rotor member 20. And a relative rotation control mechanism B for controlling the relative rotation between the housing member 30 and the rotor member 20, and an advance oil chamber R described later.
1 and a hydraulic circuit C that controls the supply and discharge of hydraulic oil to and from the retard oil chamber R2 and the supply and discharge of hydraulic oil to and from the relative rotation control mechanism B.

The camshaft 10 has a well-known cam (not shown) for opening and closing an intake valve (not shown), and is rotatably supported by a cylinder head 40 of the internal combustion engine. An advance passage 11 and a retard passage 12 extending in the axial direction are provided. The advance angle passage 11 is connected to a connection port 101 of the hydraulic control valve 100 via a radial through hole 13, an annular passage 14, and a connection passage P 1. In addition, the retard passage 12 includes a radial through hole 15 and the annular passage 1.
6 and the connection passage 102 of the hydraulic control valve 100 via the connection passage P2. In addition, the through holes 13 in the radial direction,
15 and an annular passage 16 are formed in the camshaft 10,
The annular passage 14 is formed between the camshaft 10 and the step portion of the cylinder head 40.

The rotor member 20 includes a main rotor 21 and
The main rotor 21 is constituted by a stepped cylindrical front rotor 22 integrally attached to the front (left side in FIG. 1) of the main rotor 21, and is integrally fixed to the front end of the camshaft 10 by bolts 50. , The center bores of the rotors 21 and 22 whose front ends are closed by the heads of the bolts 50 are camshafts 10.
At an advanced angle passage 11 provided at the front end.

The main rotor 21 includes a front rotor 22
Has an inner hole 21a coaxially assembled,
It has a vane groove 21b for assembling four vanes 23 and a spring 24 (see FIG. 1) for urging the vanes 23 outward. Each vane 23 is attached to the vane groove 21b and extends radially outward, and defines four advance oil chambers R1 and retard oil chambers R2 in the housing member 30.
Further, the main rotor 21 is provided with four radial through holes 21c which communicate with the advance passage 11 through the central bore at the radial inner end and communicate with the advance oil chamber R1 at the radial outer end. And an axial through-hole 21 d communicating with the retard passage 12.
And four radial through holes 21e communicating with the through hole 21d at the radial inner end and communicating with the retard oil chamber R2 at the radial outer end.

The housing member 30 includes the housing body 3
1, a front plate 32, and a rear thin plate 33
And five bolts 34 (FIG. 2) for integrally connecting them.
), And a sprocket 31a is integrally formed on the outer periphery of the rear side of the housing main body 31. As is well known, the sprocket 31a is connected to a crankshaft of the internal combustion engine via a timing chain (not shown).
(Not shown), and is configured to be rotated clockwise in FIG. 2 by transmitting a driving force from a crankshaft.

The housing body 31 has four shoe portions 31b projecting radially inward.
The main rotor 21 is rotatably supported at a radially inner end of the main rotor 21. The front plate 32 and the rear thin plate 33 are separated from each other by the main rotor 21 at opposite end faces in the axial direction.
Slidably in contact with the outer circumference of the axial end face of the vane 23 and the entire axial end face of each vane 23. As shown in FIG. 2, the housing main body 31 is formed with a protrusion 31 c that defines the most retarded phase position by contact with the vane 23, and the most advanced phase position with the vane 23. A protrusion 31d defined by the contact is formed.

The relative rotation control mechanism B unlocks by supplying hydraulic oil to allow relative rotation between the housing member 30 and the rotor member 20, and locks by discharging hydraulic oil to perform the locking operation. Is regulated at a target phase position (the state shown in FIG. 2) between the most advanced phase position and the most retarded phase position. As shown in FIGS. , 62 and lock springs 63, 64.

The lock pins 61 and 62 are axially slidably mounted in axial retreat holes 32a and 32b provided in the front plate 32, respectively.
b are urged by lock springs 63 and 64 housed in b to protrude from the evacuation holes 32a and 32b.
In addition, the lock pins 61,
Through holes 32c, 32 for smoothly moving the shaft 62 in the axial direction.
d is provided.

Each of the lock pins 61, 62 has an arc-shaped lock groove 21f, 2 having a tip portion provided in the main rotor 21.
It is slidable to 1 g and can be inserted and removed (fitting / removing), and the urging force of the lock springs 63 and 64 (set to a small value) by supplying hydraulic oil to the arc-shaped lock grooves 21 f and 21 g. ) To move in the axial direction and to be retracted and stored in the retracting holes 32a and 32b. Further, the tips of the lock pins 61 and 62 can contact the end face of the main rotor 21 and can slide in the contact state.

Each of the arc-shaped lock grooves 21f and 21g corresponds to FIG.
When the rotor member 20 is at the intermediate phase position with respect to the housing member 30 as shown in FIG.
a, 32b so as to face each other, and has arc-shaped communication grooves 21h, 21i and an axial through hole 21 at the bottom.
j, 21k are provided. Arc-shaped lock groove 21f
2 and 3, as shown in FIG. 2 and FIG.
h, the through hole 21j in the axial direction, and the through hole 21c in the radial direction communicate with the advance passage 11 and communicate with the advance oil chamber R1 through a communication groove 21m extending radially outward. As shown in FIGS. 2 and 4, the arc-shaped lock groove 21g is formed through the arc-shaped communication groove 21i, the axial through hole 21k, the radial through hole 21e, and the axial through hole 21d. And communicates with the retard oil chamber R2 through a communication groove 21n extending radially outward.

The torsion spring S interposed between the housing member 30 and the rotor member 20
0, the rotor member 20 is rotationally biased to the advance side. The biasing force is generated by a spring (not shown) that biases the intake valve in the closing direction. The value is set so as to cancel the rotational bias of the member 20 to the retard side. For this reason, the operation responsiveness when changing the relative rotation phase of the rotor member 20 with respect to the housing member 30 to the advance side is considered to be good.

The hydraulic control valve 100 shown in FIG. 1 constitutes a hydraulic circuit C by an oil pump 110 driven by an internal combustion engine, an oil reservoir 120 of the internal combustion engine, and the like.
When the solenoid 103 is energized by the energization control device 200, the spool 104 is opposed to the spring 105 as shown in FIG.
Can be moved to the left, and the duty value (%)
, The spool 104 is configured to operate as illustrated in FIGS. 5 to 11. The energization control device 200 includes various sensors (crank angle sensor 201,
Cam angle sensor 202, throttle opening sensor 203, engine speed sensor 204, engine coolant temperature sensor 20
5. Vehicle speed sensor 206, oil pump discharge pressure sensor 20
7) based on the detection signal, a control routine set in advance (a start control routine and a normal operation control routine)
Accordingly, the output (duty value) is controlled according to the operating state of the internal combustion engine.

The spool 104 has five land portions 104a, 104b, 104 as shown in an enlarged manner in FIG.
c, 104d, 104e, and 4 formed between the land portions.
Annular grooves 104f, 104g, 104h, 104i
And the annular grooves 104f and 104i at both ends are connected to the discharge port 10
7 has a pair of communication holes 104j and 104k, and the wrap amount of each part shown in FIG. 5 is L1 <L2 <L.
3 <L4 <L5 <L6.

By the way, when the spool 104 is in the state shown in FIG. 5 (a state in which the duty value is 0% and is not energized), the supply port 106 connected to the discharge port of the oil pump 110 is controlled by both land portions 104b and 104c. The communication between the connection ports 101 and 102 is interrupted, and the connection ports 101 and 102 are connected to the discharge port 107 connected to the oil reservoir 120 by the annular grooves 104 f and 104.
i through both communication holes 104j, 104k, and from both connection ports 101, 102 to the discharge port 107.
The hydraulic oil can be discharged. For this reason, each advance oil chamber R1
Hydraulic oil can be discharged to the oil reservoir 120 through the hydraulic control valve 100 from both the arc-shaped lock grooves 21f and 21g of the retard oil chamber R2 and the relative rotation control mechanism B.

When the spool 104 is in the state shown in FIG.
The communication between the connection ports 101 and 102 is cut off by b and 104c, and the connection port 101 communicates with the discharge port 107 through the annular groove 104f and the communication hole 104j.
Although the operating oil can be discharged to the drain port 104, the connection port 102 is connected to the discharge port 10 by the land portions 104d and 104e.
Communication with 7 is cut off. Therefore, the hydraulic oil can be discharged from each advance oil chamber R1 and the arc-shaped lock groove 21f of the relative rotation control mechanism B to the oil reservoir 120 through the hydraulic control valve 100, and each retard oil chamber R2 and the relative rotation control mechanism can be discharged. The hydraulic oil can be sealed in the arc-shaped lock groove 21g of B.

When the spool 104 is in the state shown in FIG. 7, the supply port 106 is connected to the land 104b.
When the communication with the connection port 101 is interrupted by the connection port 102, the connection port 102 communicates with the connection port 102 through the annular groove 104h, and the connection port 101 communicates with the discharge port 107 through the annular groove 104f and the communication hole 104j. The hydraulic oil can be supplied from the connection port 102 to the connection port 102, and the hydraulic oil can be discharged from the connection port 101 to the discharge port 107. Therefore, hydraulic oil can be supplied to each retard oil chamber R2 and the arc-shaped lock groove 21g of the relative rotation control mechanism B through the hydraulic control valve 100, and each advance oil chamber R
Hydraulic oil can be discharged to the oil reservoir 120 through the hydraulic control valve 100 from the arc-shaped lock groove 21f of the relative rotation control mechanism 1 and the relative rotation control mechanism B.

When the spool 104 is in the state shown in FIG. 8, the supply port 106 is connected to the land 104b.
While the communication with the connection port 101 is interrupted by the connection port 101, the connection port 102 is communicated with the connection port 102 through the annular groove 104h, and the communication of the connection port 101 with the discharge port 107 is interrupted by the land portion 104b.
From 06, hydraulic oil can be supplied to the connection port 102.
Therefore, hydraulic oil can be supplied to each of the retard oil chambers R2 and the arc-shaped lock grooves 21g of the relative rotation control mechanism B through the hydraulic control valve 100, and each of the advance oil chambers R1 and the relative rotation control mechanism B
The hydraulic oil can be sealed in the arc-shaped lock groove 21f.

When the spool 104 is in the state shown in FIG.
b, 104d, the communication between the two connection ports 101, 102 is cut off.
2 is disconnected from the discharge port 107 by the lands 104b, 104d, and 104e. For this reason, each advance oil chamber R1 and each retard oil chamber R2 and the relative rotation control mechanism B
Hydraulic oil can be sealed in the two arc-shaped lock grooves 21f and 21g.

When the spool 104 is in the state shown in FIG.
In the state where the communication with the connection port 102 is cut off by d, the communication with the connection port 101 is made through the annular groove 104g, and the connection port 102 is connected to both land portions 104d,
The communication with the discharge port 107 is interrupted by 104 e, and hydraulic oil can be supplied from the supply port 106 to the connection port 101. For this reason, the hydraulic control valve 1 is provided in each advance oil chamber R1 and the arc-shaped lock groove 21f of the relative rotation control mechanism B.
00, hydraulic oil can be supplied to each of the retard oil chambers R2
The hydraulic oil can be sealed in the arc-shaped lock groove 21g of the relative rotation control mechanism B.

When the spool 104 is in the state shown in FIG. 11 (duty value of 100%), the connection port 101 is disconnected from the connection port 102 while the supply port 106 is disconnected from the connection port 102 by the land 104d.
And the connection port 102 communicates with the discharge port 107 through the annular groove 104i and the communication hole 104k, so that hydraulic oil can be supplied from the supply port 106 to the connection port 101. The working oil can be discharged to the discharge port 107. For this reason, hydraulic oil can be supplied to each advance oil chamber R1 and the arc-shaped lock groove 21f of the relative rotation control mechanism B through the hydraulic control valve 100, and each of the retard oil chamber R2 and the arc rotation groove of the relative rotation control mechanism B have an arc shape. Hydraulic oil can be discharged from the lock groove 21g through the hydraulic control valve 100.

In this embodiment configured as described above, when the internal combustion engine is started, energization of the solenoid 103 of the hydraulic control valve 100 is controlled by the energization control device 200 in accordance with a start-up control routine set in advance, and the oil pump The supply oil pressure (oil pump discharge pressure) P of the hydraulic oil discharged from 110 is zero (for example, to in FIGS. 12 and 13).
) To the controllable hydraulic pressure P1 (for example, at time t1 in FIGS. 12 and 13), the hydraulic control valve 100
5 is controlled and held in the state shown in FIG. 5, and the hydraulic oil is discharged from the advance oil chambers R1 and the retard oil chambers R2 and the relative rotation control mechanism B to the oil reservoir 120 in the hydraulic circuit C.

FIG. 12 shows the relative rotational phase (actual phase position calculated based on the outputs of the crank angle sensor 201 and the cam angle sensor 202) of the housing member 30 and the rotor member 20 when the internal combustion engine is stopped, and the target phase position. FIG. 13 shows an operation example in which the difference (the difference between the phase amounts) is zero, and FIG. 13 shows that the relative rotational phase (actual phase position) of the housing member 30 and the rotor member 20 when the internal combustion engine is stopped is later than the target phase position. It is an operation example when it is on the corner side. The operation example in the case where the relative rotation phase (actual phase position) of the housing member 30 and the rotor member 20 when the internal combustion engine is stopped is on the advance side of the target phase position will be described with reference to the operation examples of FIGS. Therefore, the description thereof will be omitted.

FIGS. 12 and 13 show to when the start of the internal combustion engine is started.
The output pressure of the oil pump 110 is controllable hydraulic pressure P1 at t1 in FIGS. 12 and 13.
1 (this is detected, for example, from the output of the oil pump discharge pressure sensor 207).
13 and the time from to to t1 in FIG. 13 is about 2 seconds (depending on the performance of the oil pump 110).

In the initial stage of starting the internal combustion engine described above,
Hydraulic oil remaining in each of the advance oil chambers R1 and each of the retard oil chambers R2 can be discharged, and the operating oil allows the housing member 30 to be discharged.
And the relative rotation of the rotor member 20 is not hindered,
Due to the torque fluctuation of the driving force transmission system, the housing member 30
In contrast, the rotor member 20 can be relatively quickly rotated to the target phase position between the most advanced phase position and the most retarded phase position. Also, at the initial stage of starting the internal combustion engine, the hydraulic oil can be discharged from the arc-shaped lock grooves 21f and 21g of the relative rotation control mechanism B, so that the relative rotation control mechanism B can perform an accurate locking operation (each lock spring 63). , 64), and the relative rotation between the housing member 30 and the rotor member 20 can be accurately regulated at the target phase position described above. Therefore, the startability of the internal combustion engine can be improved. FIG.
In the operation example shown in FIG. 2, when the internal combustion engine is started, the relative rotation phase (actual phase position) of the housing member 30 and the rotor member 20 matches the target phase position, and the relative rotation control mechanism B locks. Therefore, the rotor member 20 does not rotate relative to the housing member 30.

Further, at the time of starting the internal combustion engine, the starting period after the supply oil pressure P of the working oil discharged from the oil pump 110 becomes equal to or higher than the controllable oil pressure P1 (for example, FIG.
2 and after t1 in FIG. 13), the energization (duty value) to the solenoid 103 of the hydraulic control valve 100 in the hydraulic circuit C
Is controlled by the energization control device 200, and the hydraulic oil is repeatedly supplied from the hydraulic control valve 100 at a predetermined cycle Tc (for example, a cycle of about 16 to 20 msec) alternately between the advance oil chambers R1 and the retard oil chambers R2. Supplied.

Thus, the hydraulic oil can be filled in each of the advance oil chambers R1 and each of the retard oil chambers R2, and then the hydraulic control valve 100 is inserted into the arc-shaped lock grooves 21f and 21g of the relative rotation control mechanism B. Hydraulic oil can be supplied through. For this reason, in the process of shifting to the normal operation from the latter half of the start of the internal combustion engine, the relative rotation phase of the housing member 30 and the rotor member 20 is changed to the above-described target phase position while the regulation (lock) by the relative rotation control mechanism B is released. , The housing member 30 and the rotor member 2
The relative rotation phase of 0 can be stabilized at a predetermined intermediate phase.

In the operation example shown in FIG. 12, the housing member 30 and the rotor
Since the relative rotation phase of 0 (actual phase position) coincides with the target phase position, when the hydraulic oil is alternately and repeatedly supplied from the hydraulic control valve 100 to each advance oil chamber R1 and each retard oil chamber R2. Is a reference control value (a control value for maintaining the relative rotational phase between the housing member 30 and the rotor member 20 during normal operation of the internal combustion engine,
That is, with the duty value at which the spool 104 of the hydraulic control valve 100 is controlled and held in the state shown in FIG.
0 is updated and stored for each normal operation of the internal combustion engine), and the swing widths W1 and W2 from the reference control value to the advance side and the retard side are equalized from the beginning of the control. ing. For this reason, the amount of hydraulic oil supplied to each advance oil chamber R1 and each retard oil chamber R2 at one time is made substantially equal. Note that the spool 104 of the hydraulic control valve 100 is
In the state where the spool 104 is controlled and held in the state described above, the position of the spool 104 is displaced from the reference position in the left-right direction in the drawing (that is, the lap amount on the advance side and the wrap amount on the retard side are different. In the case where the above-described reference control value is displaced to the advance side or the retard side, the respective swing widths W1 and W2 are adjusted and supplied to the advance oil chamber R1 and the retard oil chamber R2 at one time. Are set so that the amount of hydraulic oil to be performed is substantially the same.

On the other hand, in the operation example of FIG. 13, since the relative rotational phase (actual phase position) of the housing member 30 and the rotor member 20 is on the retard side from the target phase position at the initial stage of starting the internal combustion engine, the hydraulic pressure is increased. The duty value to the solenoid 103 when the operating oil is alternately and repeatedly supplied from the control valve 100 to each of the advance oil chambers R1 and each of the retard oil chambers R2 is determined by the difference between the actual phase position and the target phase position, and Calculated based on the reference control value, and each swing width W from the reference control value is calculated.
1 and W2 largely swing to the advance side at the beginning of the control, and thereafter gradually shift to the retard side, and finally the swing widths W1 and W2 on the advance side and the retard side are equalized. Therefore, the amount of hydraulic oil supplied to each of the advance oil chambers R1 and each of the retard oil chambers R2 at one time gradually changes and finally becomes substantially equal.

In the present embodiment, during normal operation of the internal combustion engine, the energization of the solenoid 103 of the hydraulic control valve 100 is controlled by the energization control device 200 in accordance with a normal operation control routine set in advance, so that the rotor is controlled. The relative rotational phase of the member 20 with respect to the housing member 30 is changed from the most retarded phase (the phase in which the volume of the advance oil chamber R1 becomes the smallest and the volume of the retard oil chamber R2 becomes the largest) to the most advanced phase (the advance oil chamber R1). The phase of the intake valve is adjusted and held at an arbitrary phase in the range up to the maximum volume of the retarded oil chamber R2 and the volume of the retarded oil chamber R2 is minimized. And the operation in the most advanced angle control state is appropriately adjusted and held.

In this case, the adjustment of the relative rotation phase of the rotor member 20 to the housing member 30 to the advance side is performed by setting the spool 104 of the hydraulic control valve 100 to the state shown in FIG. R1 and relative rotation control mechanism B
Hydraulic oil is supplied to the arc-shaped lock groove 21f through the hydraulic control valve 100, and the hydraulic control valve 10 is released from each of the retard oil chambers R2 and the arc-shaped lock groove 21g of the relative rotation control mechanism B.
This is done by discharging the hydraulic oil through zero.

At this time, the hydraulic oil is supplied to the arc-shaped lock groove 21f of the relative rotation control mechanism B, and the lock pin 61 is unlocked against the lock spring 63 to be retracted and accommodated in the evacuation hole 32a, or Lock pin 61
Is slidably in contact with the end face of the main rotor 21,
When the lock pin 62 is slidably in contact with the end face of the main rotor 21 or the lock pin 62 is slidably fitted in the arc-shaped lock groove 21g, the hydraulic oil is supplied to each advance oil chamber. R1 and each retard oil chamber R2
, The rotor member 20 is relatively rotated with respect to the housing member 30 on the advance side.

The housing member 3 of the rotor member 20
Adjustment of the relative rotation phase to the retard side with respect to 0 is performed by setting the spool 104 of the hydraulic control valve 100 to the state shown in FIG. 7, and setting each of the retard oil chambers R2 and the arc-shaped lock groove 21g of the relative rotation control mechanism B. The hydraulic oil is supplied through the hydraulic control valve 100 through the hydraulic control valve 100, and the hydraulic oil is discharged through the hydraulic control valve 100 from each of the advance oil chambers R1 and the arc-shaped lock groove 21f of the relative rotation control mechanism B.

At this time, the hydraulic oil is supplied to the arc-shaped lock groove 21g of the relative rotation control mechanism B, and the lock pin 62 is unlocked against the lock spring 64 to be retracted and accommodated in the evacuation hole 32b, or Lock pin 62
Is slidably in contact with the end face of the main rotor 21,
When the lock pin 61 is slidably abutted on the end face of the main rotor 21 or the lock pin 61 is slidably fitted in the arc-shaped lock groove 21f, the hydraulic oil is supplied to each of the retard oil chambers. R2 and each advance oil chamber R1
, The rotor member 20 relatively rotates to the retard side with respect to the housing member 30.

As is clear from the above description of the operation, in the present embodiment, in the process of shifting from the latter half of the start-up of the internal combustion engine to the normal operation, the hydraulic circuit C controls the advance oil chambers R1 and the retard oil chambers R2. Before the hydraulic oil is filled in each of the advance oil chambers R1 and each of the retard oil chambers R2, the regulation (lock) by the relative rotation control mechanism B may be temporarily stopped. Even if it is released, the relative rotation between the housing member 30 and the rotor member 20 can be suppressed by the hydraulic oil supplied to each of the advance oil chambers R1 and each of the retard oil chambers R2. Accordingly, it is possible to suppress the relative rotational phase of the housing member 30 and the rotor member 20 from becoming transiently unstable, and the rotor member 20 flaps toward the advance side and the retard side with respect to the housing member 30 ( Vibration) is suppressed.

In this embodiment, the duty value to the solenoid 103 when the hydraulic oil is alternately and repeatedly supplied to each advance oil chamber R1 and each retard oil chamber R2 is set to the reference control value (the internal combustion engine). During normal operation of the housing member 3
9 and the control value for maintaining the relative rotational phase of the rotor member 20, that is, the spool 104 of the hydraulic control valve 100 shown in FIG.
The duty value is controlled and held in the state described above, and is updated and stored in the energization control device 200 for each normal operation of the internal combustion engine.)
Because it is defined based on the following, it can absorb machine differences (variations in products) and deterioration over time, always obtain the expected hydraulic oil supply characteristics, and obtain the expected operation responsiveness. Can be.

In the present embodiment, the duty value to the solenoid 103 when the hydraulic oil is supplied alternately and repeatedly to the advance oil chamber R1 and the retard oil chamber R2 is determined by the actual phase position and the target phase. The position is also changed according to the difference between the positions, and before the advance oil chambers R1 and the retard oil chambers R2 are filled with hydraulic oil, provisional regulation (lock) by the relative rotation control mechanism B is performed. Is released, then each advance oil chamber R
1 and the hydraulic oil supplied to each of the retard oil chambers R2, the rotor member 20 can be quickly moved toward the target phase position with respect to the housing member 30, and the rotor can be moved with respect to the housing member 30. The member 20 can be held at the target phase position.

In the above embodiment, as shown in FIGS. 12 and 13, when the hydraulic oil is supplied alternately and repeatedly in the advance oil chamber R1 and the retard oil chamber R2, one cycle (Tc) is performed.
(Time), the hydraulic oil supplied to the advance oil chamber R1 and the hydraulic oil supplied to the retard oil chamber R2 (W1 + W2) were equalized. However, as shown in FIG. ), The amount of hydraulic oil supplied to the advance oil chamber R1 and the retard oil chamber R2 may be sequentially reduced. In the embodiment shown in FIG. 14, the amount of hydraulic oil supplied to the retard oil chamber R2 is constant, and the advance oil chamber R1
, The amount of hydraulic oil supplied to the motor decreases sequentially.

In the above embodiment, as shown in FIG. 12, the relative rotational phase (actual phase position) of the housing member 30 and the rotor member 20 coincides with the target phase position at the initial stage of starting the internal combustion engine. In the operation in the state (operation in which the hydraulic oil is alternately and repeatedly supplied from the hydraulic control valve 100 to each of the advance oil chambers R1 and each of the retard oil chambers R2), one is supplied to the advance oil chamber R1 and the retard oil chamber R2. The operation was performed such that the amount of hydraulic oil supplied each time was equal, but as shown in FIG. 15, the amount of hydraulic oil supplied once to the advance oil chamber R1 and the retard oil chamber R2 It is also possible to carry out the quantity in such a way that the quantity is successively reduced over time.

In the embodiment in which the operation shown in FIG. 15 is obtained, a large amount of hydraulic oil is supplied to the advance oil chamber R1 at the initial stage of alternately supplying the hydraulic oil alternately to the advance oil chamber R1 and the retard oil chamber R2. And the retarding oil chamber R2 can be supplied to the advancing oil chamber R1 and the retarding oil chamber R2 in a short time. Can be shortened.

As shown in FIG. 16 or 17, the hydraulic oil supplied to the advance oil chamber R1 and the retard oil chamber R2 at one time is reduced by the advance oil chamber R1 and the retard oil oil. By changing each swing width or each supply time from the reference control value indicated by the broken line in the chamber R2, the amount of hydraulic oil supplied to the advance oil chamber R1 at one time can be changed by the retard oil It is also possible to carry out the process (the amount is smaller than the amount of the working oil supplied to the chamber R2 at one time). These embodiments are effective when the volumes of the advance oil chamber R1 and the retard oil chamber R2 when the relative rotation control mechanism B is in the locked state are different, and the advance oil chamber R1 and the retard oil chamber R2 The hydraulic oil can be supplied in a well-balanced manner.

In these embodiments, the advance oil chamber R1
And the oil amount ratio of hydraulic oil supplied to the retard oil chamber R2 at one time (the ratio of the swing widths W1 and W2 shown in FIG. 16 or the ratio of the supply times T1 and T2 shown in FIG. 17). Rotation control mechanism B
Oil chamber R1 and retard oil chamber R2 when is locked
Is set based on the volume ratio of the advance oil chamber R1
Even before the restriction (lock) by the relative rotation control mechanism B is released before the hydraulic oil is filled in the retard oil chamber R2 and the retard oil chamber R2, the oil is supplied to the advance oil chamber R1 and the retard oil chamber R2 by that time. Hydraulic oil and thereafter the advance oil chamber R1 and the retard oil chamber R
The hydraulic oil supplied to 2 allows the rotor member 20 to move toward the target phase position with respect to the housing member 30. In FIG. 16, the supply time T1,
T2 is equal, and the swing widths W1 and W2 are equal in FIG.

In the above-described embodiment, the calculation of the swing widths W1 and W2 from the reference control value is performed without considering the temperature of the hydraulic oil (which can be detected by the engine coolant temperature sensor 205). Swing width W1, W2 from the value
It is also possible to add the correction amounts shown in FIG. 18 or FIG. In FIG. 18, in consideration of the fact that when the temperature of the hydraulic oil is low, the viscosity of the hydraulic oil is high and the passage resistance increases, and it is difficult to supply the hydraulic oil to the advance oil chamber R1 or the retard oil chamber R2. Increase the correction value,
Also, when the temperature of the hydraulic oil is high, the viscosity of the hydraulic oil decreases, the pump efficiency of the oil pump 110 decreases, the hydraulic pressure of the hydraulic oil decreases, and the supply amount to the advance oil chamber R1 or the retard oil chamber R2. In view of the fact that the temperature decreases, the correction value is increased, though not so much as at the time of low temperature. On the other hand, in FIG. 19, the correction value is increased only at a low temperature in consideration of only the change in the passage resistance due to the change in viscosity described above. In the case where the correction amount shown in FIG. 18 or 19 is added, the desired hydraulic oil supply characteristic is always obtained irrespective of the temperature of the hydraulic oil, and the desired operation responsiveness is obtained. Can be.

In the above embodiment, the determination that the hydraulic oil pressure is equal to or higher than the controllable oil pressure is made based on the detection signal from the oil pump discharge pressure sensor 207. It is also possible to carry out the process in a predetermined elapsed time (time measured in advance when the discharge pressure P of the oil pump 110 driven by the start of the internal combustion engine becomes equal to or higher than the controllable oil pressure P1). In this case, the oil pump discharge pressure sensor 207 of the above embodiment is used.
It can be implemented at low cost without using (oil pressure detecting means).

Further, in the above-described embodiment, the hydraulic circuit C having one hydraulic control valve 100 controls the advance oil chamber R1.
In addition, the hydraulic oil supply / discharge to the retard oil chamber R2 and the relative rotation control mechanism B was performed in a compact configuration, but the hydraulic circuit provided with a plurality of hydraulic control valves was used as in the above-described embodiment. The hydraulic oil can be supplied to and discharged from the angular oil chamber R1, the retard oil chamber R2, and the relative rotation control mechanism B.

Further, in the above embodiment, the present invention is applied to a valve timing control apparatus in which the housing member 30 rotates integrally with the crankshaft and the rotor member 20 rotates integrally with the camshaft 10. Although the present invention has been implemented, the present invention can be similarly implemented in a valve opening / closing timing control device in which the housing member rotates integrally with the camshaft and the rotor member rotates integrally with the crankshaft. is there. Further, the present invention can be similarly applied to an apparatus of a type in which a vane is formed integrally with a rotor body.

In the above embodiment, the present invention is applied to a valve opening / closing timing control device mounted on a cam shaft for opening and closing an intake valve. However, the present invention is applied to a valve mounted on a cam shaft for opening and closing an exhaust valve. The opening / closing timing control device can be similarly or appropriately changed and implemented.

[Brief description of the drawings]

FIG. 1 is an overall configuration diagram showing an embodiment of a valve timing control apparatus according to the present invention.

FIG. 2 is a vertical sectional front view of a main part of FIG.

FIG. 3 is a sectional view of an upper lock pin portion shown in FIG. 2;

FIG. 4 is a sectional view of a lower lock pin portion shown in FIG. 2;

FIG. 5 is an enlarged sectional view of the hydraulic control valve shown in FIG.

6 is a cross-sectional view of a main part of the hydraulic control valve shown in FIG. 5 in a first energized state.

7 is a cross-sectional view of a main part of the hydraulic control valve shown in FIG. 5 in a second energized state.

8 is a cross-sectional view of a main part of the hydraulic control valve shown in FIG. 5 in a third energized state.

9 is a cross-sectional view of a main part of the hydraulic control valve shown in FIG. 5 in a fourth energized state.

10 is a cross-sectional view of a main part of the hydraulic control valve shown in FIG. 5 in a fifth energized state.

11 is a cross-sectional view of a main part of the hydraulic control valve shown in FIG. 5 in a sixth energized state.

12 shows an example of operation of the valve timing control apparatus shown in FIG. 1 (an example of operation when the actual phase position of the housing member and the rotor member coincides with the target phase position at the initial stage of starting the internal combustion engine). It is operation | movement explanatory drawing.

FIG. 13 shows another operation example of the valve timing control apparatus shown in FIG. 1 (an operation example in a case where the actual phase positions of the housing member and the rotor member are on the retard side from the target phase position at the initial stage of starting the internal combustion engine). FIG.

FIG. 14 is a modification of the operation example shown in FIGS. 12 and 13 (the amount of hydraulic oil supplied to the retard oil chamber is constant, and the amount of hydraulic oil supplied to the advance oil chamber is sequentially It is an operation explanatory view showing an operation example in the case of reducing the number.

FIG. 15 shows another modification of the operation example shown in FIGS. 12 and 13 (the amount of hydraulic oil supplied to the advance oil chamber and the retard oil chamber at one time is sequentially reduced in accordance with the elapsed time. FIG. 10 is an operation explanatory diagram showing an operation example in the case where the operation is performed.

FIG. 16 is an operation explanatory diagram showing an operation example when the volumes of the advance oil chamber and the retard oil chamber are different when the relative rotation control mechanism is in a locked state.

FIG. 17 is an operation explanatory view showing another operation example when the volumes of the advance oil chamber and the retard oil chamber are different when the relative rotation control mechanism is in a locked state.

FIG. 18 is a diagram showing an example of a correction amount added in accordance with the temperature of hydraulic oil when calculating a runout from a reference control value.

FIG. 19 is a diagram illustrating another example of the correction amount added in accordance with the temperature of the hydraulic oil when calculating the swing width from the reference control value.

[Explanation of symbols]

10 cam shaft, 11 advance passage, 12 retard passage, 20
... rotor member, 21 ... rotor body, 23 ... vane, 30
... housing member, 31 ... housing body, 31b ... shoe part, B ... relative rotation control mechanism, 61, 62 ... lock pin, 63, 64 ... lock spring, R1 ... advance oil chamber,
R2: retard oil chamber, C: hydraulic circuit, 100: hydraulic control valve,
110: oil pump, 120: oil reservoir, 200: energization control device.

 ──────────────────────────────────────────────────続 き Continued from the front page F term (reference) EA11 FA03 FA06 FA11 FA31 GA01 GA14 HA13Z HE08Z

Claims (9)

[Claims] 1. A driving force transmission system for transmitting driving force from a crankshaft of an internal combustion engine to a camshaft that opens and closes an intake valve or an exhaust valve of the internal combustion engine, and rotates integrally with the crankshaft or the camshaft. The camshaft or the crankshaft, wherein the camshaft or the crankshaft is formed so as to be rotatable relative to a housing member and a shoe portion provided on the housing member so as to form an advance oil chamber and a retard oil chamber in the housing member at a vane portion. A rotor member that rotates integrally with the housing member and the housing member and the rotor member that are unlocked by supply of hydraulic oil to allow relative rotation of the housing member and the rotor member and locked by discharge of hydraulic oil to lock the housing member and the rotor member. A relative rotation control mechanism that regulates relative rotation at a target phase position within an intermediate region excluding a rotation limit position at both ends between a most advanced phase position and a most retarded phase position; And a valve opening / closing timing control device provided with a hydraulic circuit for controlling the supply and discharge of hydraulic oil to and from the retard oil chamber and the relative rotation control mechanism. After the controllable oil pressure or more, the hydraulic oil is alternately and repeatedly supplied to the advance oil chamber and the retard oil chamber to fill the advance oil chamber and the retard oil chamber with hydraulic oil. And a hydraulic circuit capable of supplying hydraulic oil to the relative rotation control mechanism thereafter. 2. The valve timing control apparatus according to claim 1, wherein the hydraulic circuit is provided with a hydraulic control valve provided when the hydraulic oil is alternately and repeatedly supplied to the advance oil chamber and the retard oil chamber. A valve opening / closing timing control device, wherein a control value is set based on a control value for maintaining a relative rotation phase between the housing member and the rotor member during a normal operation before the internal combustion engine is stopped. 3. The valve timing control device according to claim 2, wherein the control value of the hydraulic control valve is corrected according to the temperature of the hydraulic oil. 4. The valve opening / closing timing control device according to claim 1, wherein when the hydraulic oil is alternately and repeatedly supplied to the advance oil chamber and the retard oil chamber, the hydraulic oil supplied at one time is used. A valve opening / closing timing control device, wherein an oil amount is different between the advance oil chamber and the retard oil chamber. 5. The valve opening / closing timing control device according to claim 4, wherein the relative rotation control mechanism determines an oil amount ratio of hydraulic oil supplied to the advance oil chamber and the retard oil chamber at one time. A valve opening / closing timing control device which is set based on a volume ratio between the advance oil chamber and the retard oil chamber in a locked state. 6. The valve opening / closing timing control device according to claim 1, wherein the amount of hydraulic oil supplied to the advance oil chamber and the retard oil chamber at one time is adjusted. A valve opening / closing timing control device which is set based on a difference between a detected value of a phase detecting means for detecting a relative rotation phase of the housing member and the rotor member and the target phase position. 7. The valve opening / closing timing control device according to claim 1, wherein the oil amount of the hydraulic oil supplied to the advance oil chamber and the retard oil chamber at one time is determined. A valve opening / closing timing control device which is sequentially reduced according to an elapsed time. 8. The valve timing control apparatus according to claim 1, wherein the determination that the hydraulic pressure of the hydraulic oil has become equal to or higher than the controllable hydraulic pressure is performed at a predetermined elapsed time after the start of the internal combustion engine. A valve timing control device, characterized in that: 9. The valve opening / closing timing control device according to claim 1, wherein the hydraulic circuit controls a hydraulic pressure of hydraulic oil when the internal combustion engine is started. A valve opening / closing timing control device wherein hydraulic oil can be discharged from both the advance oil chamber and the retard oil chamber and the relative rotation control mechanism until the hydraulic pressure reaches a possible hydraulic pressure.