JP2016061175A - Control valve - Google Patents

Abstract

A control valve that reliably shifts a lock mechanism of a valve opening / closing timing control device to a locked state while having a single spool is provided. When the spool 50 is operated to the lock transition position P1, the fluid is discharged from the lock release port 40L, and the drain port 40DA is connected from the advance port 40A or the retard port 40B from which the fluid is discharged. The discharge flow path R that restricts the flow of the fluid flowing through is formed on at least one of the outer periphery of the discharge control land portion 50Le and the inner periphery of the sleeve 40. [Selection] Figure 6

Description

  The present invention relates to a control valve of a valve opening / closing timing control device including a driving side rotating body that rotates synchronously with a crankshaft and a driven side rotating body connected to a camshaft. The present invention relates to a control valve for controlling a fluid supplied to one of a chamber and a retard chamber and for controlling a fluid supplied to and discharged from a lock mechanism.

  As a control valve configured as described above, Patent Document 1 discloses that a spool in which six land portions are formed is housed in a sleeve, a spring that biases the spool in a predetermined direction, and a biasing force of the spring. A technique with an electromagnetic solenoid for operating a spool is shown.

  In Patent Document 1, a valve opening / closing timing control device is configured by a housing and a rotor that are disposed so as to be relatively rotatable, and an advance chamber and a retard chamber are formed between the housing and the rotor. A lock mechanism that holds the relative rotation of the motor is provided. In Patent Document 1, the control valve is configured to supply and discharge hydraulic oil to and from the advance chamber, the retard chamber, and the lock plate of the lock mechanism by setting the spool.

  In particular, Patent Document 1 is configured to supply fluid to either the advance chamber or the retard chamber when the spool is set to a position for shifting the lock plate of the lock mechanism to the locked state. ing. Therefore, at this position, the housing and the rotor rotate relative to each other, and the lock plate engages with the lock groove and reaches the locked state at the timing when the lockable phase is reached.

JP 2010-59979 A

  Japanese Patent Laid-Open No. 2004-260688 is configured to be able to control the relative rotation phase of the valve opening / closing timing control device and the lock mechanism using a single spool. The number of parts can be reduced as compared with a configuration including a control valve for controlling the phase and a control valve for controlling the lock mechanism.

  However, when the lock mechanism is shifted to the locked state, as described in Patent Document 1, in the case of supplying fluid to either the advance chamber or the retard chamber, the relative valve opening / closing timing control device Since the rotational phase changes, it may be difficult to shift to the locked state.

  In other words, when the operation of engaging the lock member of the lock mechanism with the lock recess or the like at the timing when the relative rotation phase reaches the lock phase, the change of the relative rotation phase may be performed at a high speed, and the lock member is locked. Even when the phase that can be engaged with the concave portion is reached, the phase cannot be engaged and the locked state may not be entered.

  An object of the present invention is to configure a control valve that reliably shifts the lock mechanism of the valve timing control device to the locked state even in a configuration having a single spool.

A feature of the present invention is that it has a driving side rotating body that rotates synchronously with a crankshaft of an internal combustion engine, and a driven side rotating body that rotates integrally with the camshaft of the internal combustion engine and rotates relative to the driving side rotating body. The fluid is supplied to the advance chamber defined between the drive-side rotor and the driven-side rotor so that the relative rotation phase between the drive-side rotor and the driven-side rotor is in the advance direction. And the relative rotation phase is retarded by supplying fluid to a retard chamber that is between the drive-side rotor and the driven-side rotor and is partitioned at a position different from the advance chamber. The relative rotational phase is locked to a predetermined level by engaging a locking member supported on the other side with an engaging portion formed on one of the driving side rotating body and the driven side rotating body. Valve timing control with a lock mechanism that maintains the phase A control valve used in the location, the control valve,
A sleeve, a spool accommodated in the sleeve, and an electromagnetic solenoid that moves the spool along an axis of the sleeve;
The sleeve has a pump port to which a fluid is supplied, an advance port communicating with the advance chamber, a retard port communicating with the retard chamber, and a space in which unlocking pressure is applied to the lock member. It has a lock release port that communicates and a drain port that allows fluid to be discharged,
The spool includes a plurality of land portions for controlling the flow of fluid, and supplies the fluid to one of the advance port and the retard port while supplying the fluid to the unlock port, and discharges the fluid from the other. Between the phase control position to be moved and the lock transition position in which fluid is supplied to one of the advance port and the retard port while the fluid is discharged from the lock release port and the fluid is discharged from the other. Is possible,
In the lock transition position, the fluid discharge amount from the discharge port from which the fluid is discharged out of the advance port or the retard port is the amount of fluid discharge from the discharge port in a position adjacent to the lock transition position. It is in the point set less.

  According to this configuration, when the spool is set to the lock transition position, the fluid is discharged from the lock release port, and the fluid is discharged from the discharge port from which the fluid is discharged to the drain port of the advance port or the retard port. Is discharged. In this lock transition position, the amount of fluid discharged from the discharge port is reduced from the amount of fluid discharged from the discharge port at the adjacent position. As a result, when the spool is set to the lock transition position, the relative rotational speed between the driving side rotating body and the driven side rotating body is reduced, and when the phase at which the lock member is engaged with the engaging portion is reached. The locking member is reliably engaged with the engaging portion. Therefore, a control valve that reliably shifts the lock mechanism of the valve opening / closing timing control device to the locked state while having a single spool is configured.

  In the present invention, when the spool is in the lock transition position, at least one of the outer peripheral portion of the discharge control land portion that is one of the plurality of land portions and the inner peripheral portion of the sleeve, A discharge flow path for restricting and discharging the fluid may be formed.

  Thus, by forming the discharge restricting portion on at least one of the outer peripheral portion of the discharge control land portion and the inner peripheral portion of the sleeve, the discharge of the fluid is originally blocked by the control land portion. It is also possible to restrict the flow of the fluid using the configuration, and it is possible to limit the flow rate of the fluid with a simple configuration.

  In the present invention, the discharge flow path is formed by setting the outer diameter of the discharge control land portion to be smaller than the outer diameters of the other land portions so as to allow fluid flow on the outer periphery of the discharge control land portion. May be.

  In this manner, by performing processing such that the outer diameter of the discharge control land portion is smaller than the outer diameter of the other land portions, a fluid discharge flow path is provided between the outer periphery of the discharge control land portion and the inner periphery of the sleeve. Can be formed, and the rate of change of the relative rotational phase can be controlled. Further, according to this configuration, since simple processing is sufficient, the manufacturing cost of the control valve is hardly increased.

  In the present invention, the discharge channel may be formed by a groove.

  As described above, even when the groove is formed in at least one of the outer periphery of the discharge control land portion and the inner periphery of the sleeve, the manufacturing cost of the control valve is hardly increased. Further, in the case where the discharge flow path is formed on the outer periphery of the discharge control land portion as described above, high accuracy is required for setting the cutting amount on the outer periphery of the discharge land portion in order to determine the flow rate of the discharged fluid. On the other hand, in the case of forming the discharge flow path with a configuration, a plurality of grooves are formed, and for example, the depth and width of the grooves are individually set at the time of manufacturing the control valve to adjust the flow rate of the fluid. Can be performed relatively easily.

  In the present invention, the discharge channel may be formed by a communication hole.

  As described above, even if processing is performed in which the communication hole is formed in at least one of the outer peripheral portion of the discharge control land portion and the inner peripheral portion of the sleeve, the manufacturing cost of the control valve is hardly increased. In particular, in the case where the communication hole is formed as the flow path discharge path, the flow path cross-sectional area of the discharge flow path becomes a fixed value, so that it is difficult to change the change speed of the relative rotation phase, and management of the change speed becomes easy. .

It is sectional drawing of a valve opening / closing timing control apparatus and a control valve. It is sectional drawing of the valve timing control apparatus of the II-II line | wire of FIG. It is sectional drawing of the valve opening / closing timing control apparatus of a lock release state. It is sectional drawing of the valve timing control apparatus of the most retarded angle lock phase. It is a figure which shows the position of a control valve, and the supply / discharge pattern of hydraulic fluid. It is sectional drawing of the control valve in a 1st position. It is sectional drawing of the control valve in a 2nd position. It is sectional drawing of the control valve in a 3rd position. It is sectional drawing of the control valve in a 4th position. It is a perspective view which shows a 4th land part and a 5th land part. It is a perspective view which shows the edge part of the spool of another embodiment (b). It is a perspective view which shows the edge part of the spool of another embodiment (c).

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[Basic configuration]
As shown in FIGS. 1 and 2, a valve opening / closing timing control device A for setting an opening / closing timing (opening / closing timing) of the intake valve Va for an engine E as an internal combustion engine is provided. The valve opening / closing timing control device A is configured to supply / discharge hydraulic fluid as a fluid by an electromagnetically operated control valve CV, and to set the opening / closing timing of the intake valve Va by this supply / discharge.

  The engine E (an example of an internal combustion engine) is provided in a vehicle such as a passenger car. The engine E is configured as a four-cycle type in which a piston 4 is accommodated in a cylinder bore of the cylinder block 2 and the piston 4 and the crankshaft 1 are connected by a connecting rod 5.

  The valve opening / closing timing control device A includes an external rotor 20 as a driving side rotating body that rotates synchronously with the crankshaft 1 of the engine E, and a driven side rotating body that rotates integrally with the intake camshaft 7 that controls the intake valve Va of the engine E. As an internal rotor 30. An advance chamber Ca and a retard chamber Cb are formed between the external rotor 20 (an example of a driving side rotating body) and the internal rotor 30 (an example of a driven side rotating body). Further, a lock mechanism L that locks (fixes) the relative rotation phase between the outer rotor 20 and the inner rotor 30 to the intermediate lock phase is provided.

  The engine E includes a hydraulic pump P that is driven by the driving force of the crankshaft 1. The hydraulic pump P supplies lubricating oil stored in an oil pan of the engine E as hydraulic oil (an example of fluid) from a supply oil passage 8 to a control valve CV. The control valve CV is supported by the engine E in such a manner that a shaft-like portion 41 that supports the sleeve 40 is inserted into the internal rotor 30. The control valve CV supplies and discharges hydraulic oil to and from the valve opening / closing timing control device A through a flow path formed inside the shaft-like portion 41. A check valve 9 is provided in the supply oil passage 8 to prevent the backflow of the hydraulic oil.

  With this configuration, the control valve CV selects one of the advance chamber Ca and the retard chamber Cb and supplies hydraulic oil, whereby the relative rotational phase between the external rotor 20 and the internal rotor 30 (hereinafter referred to as relative rotational phase). And the opening / closing timing of the intake valve Va is set. Furthermore, the control valve CV enables the lock mechanism L to be unlocked or shifted to the locked state by supplying and discharging hydraulic oil.

  The control valve CV is not limited to the position shown in FIG. 1 but may be located at a position away from the valve opening / closing timing control device A. Thus, when spaced apart from the valve opening / closing timing control device A, a flow path for supplying and discharging hydraulic oil is formed between the control valve CV and the valve opening / closing timing control device A.

  In this embodiment, a configuration in which the valve opening / closing timing control device A is provided for the intake camshaft 7 is shown, but the exhaust camshaft 7 and the exhaust cam may be provided with the valve opening / closing timing control device A. A valve opening / closing timing control device A may be provided on both the shaft and the shaft.

[Specific configuration of valve timing control device]
As shown in FIGS. 1 to 4, the valve opening / closing timing control device A includes an internal rotor 30 with respect to the external rotor 20, and these can rotate relative to each other on a coaxial axis with the rotational axis X of the intake camshaft 7. It is arranged and arranged. The internal rotor 30 is connected to the intake camshaft 7 by a connecting bolt 33. The timing chain 6 is wound around the drive sprocket 22S formed on the external rotor 20 and the sprocket 1S formed on the crankshaft 1.

  The outer rotor 20 has a cylindrical rotor body 21, a rear block 22 disposed at one end of the rotor body 21 in the direction along the rotation axis X, and a rotor in the direction along the rotation axis X. A front plate 23 disposed at the other end of the main body 21 is fastened by a plurality of fastening bolts 24. A drive sprocket 22 </ b> S is formed on the outer periphery of the rear block 22. On the inner peripheral side of the rotor body 21, a plurality of projecting portions 21 </ b> T are formed that project in a direction close to the rotation axis X (inward in the radial direction).

  A pair of guide grooves are formed in a radial attitude from the rotation axis X with respect to one of the plurality of protrusions 21T. A plate-like lock member 25 is removably inserted into these guide grooves, and each lock member 25 is provided with a lock spring 26 that urges them in a direction approaching the rotation axis X (lock direction). Yes. Thus, the lock mechanism L is comprised by the lock member 25 and the lock spring 26 which urges them in the protruding direction.

  The shape of the lock member 25 is not limited to a plate shape, and may be a rod shape, for example. Further, the lock mechanism L may be constituted by the single lock member 25 and the single lock spring 26. Further, the lock mechanism L may include a lock member 25 that operates in a direction along the rotation axis X and a lock recess that engages with the lock member 25.

  The inner rotor 30 is formed with an inner peripheral surface 30 </ b> S having a cylindrical inner surface on the same axis as the rotational axis X and a columnar outer peripheral surface centering on the rotational axis X. A flange-shaped portion 32 is formed at one end of the internal rotor 30 in the direction along the rotation axis X, and the internal rotor is connected by a connecting bolt 33 that is inserted into a hole at the inner peripheral position of the flange-shaped portion 32. 30 is connected to the intake camshaft 7.

  A plurality of vanes 31 projecting outward are provided on the outer peripheral surface of the inner rotor 30. With this configuration, the inner rotor 30 is fitted (included) in the outer rotor 20, thereby being surrounded by the inner surface (cylindrical inner wall surface and the plurality of protruding portions 21 </ b> T) of the rotor body 21 and the outer peripheral surface of the inner rotor 30. A fluid pressure chamber C is formed in the region. Further, the advance chamber Ca and the retard chamber Cb are formed by dividing the fluid pressure chamber C by the vane 31. The internal rotor 30 is formed with an advance passage 34 that communicates with the advance chamber Ca, a retard passage 35 that communicates with the retard chamber Cb, and a lock release passage 36.

  In the valve opening / closing timing control device A, the external rotor 20 rotates in the driving rotation direction S by the driving force transmitted from the timing chain 6. Further, when the working oil is supplied to the advance chamber Ca, the relative rotational phase is displaced in the advance direction Sa, and when the hydraulic oil is supplied to the retard chamber Cb, the relative rotational phase is displaced in the retard direction Sb. Let

  A direction in which the inner rotor 30 rotates in the same direction as the drive rotation direction S with respect to the outer rotor 20 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 A, the intake timing is advanced as the relative rotational phase is displaced in the advance direction Sa, and the intake timing is delayed as the relative rotational phase is displaced in the retard direction Sb.

  An intermediate lock recess 37 (an example of a space in which an engagement portion / unlocking pressure is applied) is formed on the outer periphery of the inner rotor 30 so that the pair of lock members 25 can be engaged / removed. Further, one lock member 25 is engaged with the outer periphery of the inner rotor 30 in the most retarded lock phase in which the pair of lock members 25 are displaced in the retard direction Sb from the intermediate lock phase in which the pair of lock members 25 are simultaneously engaged with the intermediate lock recess 37. The most retarded angle locking recess 38 is formed. An unlock channel 36 communicates with the intermediate lock recess 37, and an advance channel 34 communicates with the most retarded lock recess 38.

  In the intermediate lock phase, as shown in FIG. 2, the pair of lock members 25 are fitted into the intermediate lock recesses 37, and the respective lock members 25 come into contact with the circumferential end surfaces of the intermediate lock recesses 37. When hydraulic oil is supplied to the unlocking flow path 36 in this intermediate locking phase, the direction in which the two locking members 25 are separated from the rotational axis X against the urging force of the lock spring 26 as shown in FIG. And the engagement is released (the locked state is released). In the most retarded angle lock phase, as shown in FIG. 4, one of the lock members 25 is engaged with the most retarded angle lock recess 38. In this most retarded lock phase, when hydraulic oil is supplied to the advance flow path 34, the lock member 25 is moved away from the rotational axis against the urging force of the lock spring 26 and engaged. Is released (the locked state is released), and after the release of the locked state, the relative rotational phase is displaced in the advance direction Sa.

  In addition, the relative rotation phase in a state where the vane 31 has reached the moving end in the advance direction Sa (the rotation limit about the rotation axis X) is referred to as the most advanced phase, and the vane 31 moves on the retard side. The relative rotation phase in the state where the end (the rotation limit about the rotation axis X) is reached is called the most retarded phase.

  The intermediate lock phase is a phase in which the valve opening / closing timing is optimally maintained when the engine E in the cold state is started, and when the engine E is stopped, the relative rotation phase is displaced to the intermediate lock phase to lock the lock mechanism L. Then, the control state is shifted to the locked state, and then the engine E is stopped. The most retarded angle lock phase is a phase that reduces the starting load of the engine E. For example, when there is a high possibility of restarting the engine E in a warm-up state such as an idle stop, the relative rotational phase is shifted to the most retarded lock phase and the lock mechanism L is shifted to the locked state. Control for stopping the engine E is performed.

  A torsion spring 27 is provided across the rear block 22 of the outer rotor 20 and the inner rotor 30. The torsion spring 27 applies an urging force for displacing the relative rotation phase to the vicinity of the intermediate lock phase from the state in the most retarded lock phase.

(Control valve)
As shown in FIGS. 1 and 6, the control valve CV of the present invention includes a sleeve 40, a spool 50, an electromagnetic solenoid 60, and a spool spring 61. The spool 50 is accommodated in the spool accommodating space of the sleeve 40 so as to be movable along the spool axis Y. The electromagnetic solenoid 60 applies an operating force to the spool 50 in a direction that resists the biasing force of the spool spring 61.

  In this control valve CV, the spool 50 is formed in a cylindrical shape centered on the spool axis Y, and the sleeve 40 is formed in a cylindrical shape coaxial with the spool axis Y so that the spool 50 can be slidably received. Has been. In this embodiment, as shown in FIGS. 1 and 6, the electromagnetic solenoid 60 is used in a vertically long posture, and the arrangement of each part will be described based on this posture.

  In the control valve CV, the sleeve 40 is supported with respect to the engine E via a bracket or the like in a state where the shaft-like portion 41 formed on the sleeve 40 is inserted into the internal rotor 30. As described above, the shaft-like portion 41 is formed with a plurality of flow paths that are formed into a cylindrical shape that is coaxial with the rotation axis X and that can supply and discharge fluid. Further, in order to enable supply and discharge of hydraulic oil even when the valve timing control device A rotates about the rotation axis X, the outer periphery of the shaft-like portion 41 and the inner peripheral surface 30S of the inner rotor 30 are provided. A plurality of ring-shaped seals 42 are provided between the two.

  The electromagnetic solenoid 60 is configured by arranging a solenoid coil 60B on the outer periphery of a plunger 60A made of a magnetic material such as iron. The electromagnetic solenoid 60 functions to displace the spool 50 downward against the biasing force of the spool spring 61 as the electric power supplied to the solenoid coil 60B increases.

  The sleeve 40 has a first pump port 40PA, an unlock port 40L, an advance port 40A, a second pump port 40PB, and a retard port from a position close to the electromagnetic solenoid 60 in the direction along the spool axis Y. 40B and the first drain port 40DA are formed in this order. A second drain port 40DB is formed at the lower end of the sleeve 40.

  The spool 50 has a connecting cylinder portion 50S having a small diameter at the upper end connected to the plunger 60A of the electromagnetic solenoid 60, and a plurality of land portions to be described later are formed below the connecting cylinder portion 50A. A drain channel 50D is formed in the shape of a hole. Further, an upper drain opening 50Da communicating with the drain channel 50D is formed in the connecting cylinder portion 50S.

  The spool 50 has a first land portion 50La, a second land portion 50Lb, a third land portion 50Lc, a fourth land portion 50Ld, and a fifth land portion 50Le (discharge control land) from a position close to the electromagnetic solenoid 60. Are formed in this order. In addition, the first groove 50Ga, the second groove 50Gb, the third groove 50Gc, and the fourth groove 50Gd are formed in this order at positions sandwiched between these land portions.

  A central drain opening 50Db communicating with the drain flow path 50D is formed in the second groove portion 50Bb.

  In this control valve CV, the inner diameter of the sleeve 40 is set to be constant at any position in the direction along the spool axis Y, and the fifth land portion 50Le at the end position of the spool 50 is formed as a discharge control land. Yes. In particular, as shown in FIG. 10, the parts other than the fifth land portion 50Le (discharge control land) are set to a standard outer diameter φA that is in close contact with the inner periphery of the sleeve 40, and the fifth land portion 50Le has a standard outer diameter φA. The limit outer diameter φB is set to be slightly smaller. As a result, a gap is formed between the outer periphery of the fifth land portion 50Le and the inner periphery of the sleeve 40 so that the hydraulic oil is restricted. The discharge flow path R is configured so that this gap acts as an orifice by applying resistance to the flow of the hydraulic oil.

[Spool position]
In the control valve CV, the spool 50 is held at the first position P1 (an example of a lock transition position) in a state where no power is supplied to the solenoid coil 60B, and the second position P2 and the third position are increased as the supplied power increases. P3 and the fourth position P4 are sequentially set. The supply / discharge pattern at these positions is shown in FIG.

  Note that these positions are examples of the embodiment, and the spool 50 is set to the fourth position P4 in a state where no power is supplied to the solenoid coil 60B, and the third position P3, the second position are increased as the supplied power increases. The operation mode may be set so as to be set to the position P2 and the first position P1.

[Third position]
When the relative rotation phase of the valve timing control device A is maintained, the spool 50 is maintained at the third position P3 as shown in FIG. In this position, the advance port 40A is closed by the third land portion 50Lc, the retard port 40B is closed by the fourth land portion 50Ld, and the hydraulic oil from the first pump port 40PA passes through the first groove 50Ga. Supplied to the lock release port 40L.

  As a result, hydraulic oil is not supplied to and discharged from the advance chamber Ca and the retard chamber Cb, and the relative rotational phase is maintained.

[4th position]
When the relative rotation phase of the valve opening / closing timing control device A is displaced in the retard direction, the spool 50 is operated to the fourth position P4 (an example of the phase control position) as shown in FIG. In this position, hydraulic oil from the second pump port 40PB is supplied to the retard port 40B via the third groove 50Gc, and hydraulic oil from the advance port 40A enters the central drain opening 50Db of the second groove 50Gb. It is discharged to the flow drain channel 50D. Further, at the fourth position P4, the hydraulic oil from the first pump port 40PA is supplied to the lock release port 40L via the first groove 50Ga.

  As a result, the hydraulic oil is supplied to the retard chamber Cb and simultaneously the hydraulic oil is discharged from the advance chamber Ca, and the hydraulic oil pressure acts on the lock member 25 in the unlocking direction, so that the relative rotation phase is delayed. Displacement in the angular direction Sb.

[Second position]
When the relative rotation phase of the valve opening / closing timing control device A is displaced in the advance direction, as shown in FIG. 7, the spool 50 is operated to the second position P2 (an example of the phase control position). In this position, hydraulic oil from the second pump port 40PB is supplied to the advance port 40A via the third groove 50Gc, and hydraulic oil from the retard port 40B is supplied to the first drain via the fourth groove 50Gd. It flows to the port 40DA and is discharged. Further, at the second position P2, the hydraulic oil from the first pump port 40PA is supplied to the lock release port 40L via the first groove 50Ga.

  As a result, the hydraulic oil is supplied to the advance chamber Ca, and at the same time, the hydraulic oil is discharged from the retard chamber Cb. Since the hydraulic oil pressure acts on the lock member 25 in the unlocking direction, the relative rotation phase advances. Displacement in the angular direction Sa.

[First position]
When the lock mechanism L is shifted to the locked state, the spool 50 is operated to the first position P1 as shown in FIG. The first position P1 is a position set by the urging force of the spool spring 61 in a state where the power supply to the electromagnetic solenoid 60 is stopped. Accordingly, at the time of control for stopping the engine E, the spool 50 is automatically set to the first position P1 only by stopping the power supply to the electromagnetic solenoid 60.

  As described above, the outer diameter (restricted outer diameter φB) of the fifth land portion 50Le is set to a value slightly smaller than the outer diameter (standard outer diameter φA) of the other land portions. It is comprised as the discharge flow path R which restrict | limits the flow of hydraulic fluid between.

  As a result, in this first position, hydraulic oil from the second pump port 40PB is supplied to the advance port 40A via the third groove 50Gc, and hydraulic oil from the retard port 40B passes through the fourth groove 50Gd. Through the first drain port 40DA. The fifth land portion 50Le functions as a discharge control land portion of the present invention. The fifth land portion 50Le is connected to the retard port 40B (discharge port) when the spool 50 is set to the first position P1. As a result of restricting the discharged hydraulic oil, the discharge amount of the hydraulic oil per unit time is reduced, and the discharge amount is limited.

  Further, at the first position P1, the lock release port 40L communicates with the central drain opening 50Db of the second groove 50Gb, and the hydraulic oil from the intermediate lock recess 37 is discharged. The lock release port 40L starts discharging the hydraulic oil before the spool 50 reaches the first position P1.

  Furthermore, when the spool 50 is set to the first position P1, the amount of hydraulic oil discharged from the retard port 40B (discharge port) per unit time at the second position P2 is determined at the first position P1. The amount of hydraulic oil discharged from the retard port 40B (discharge port) per unit time is set small.

  Therefore, when the spool 50 is operated from the second position P2 to the first position P1, the discharge flow path R discharges the hydraulic oil discharged from the retard port 40B per unit time after the start of this operation. In order to limit the amount, the displacement speed of the relative rotational phase in the advance direction Sa is greatly reduced before the spool 50 reaches the first position P1. Then, at a timing when the lock member 25 reaches a phase capable of being engaged with the intermediate lock recess 37, the pair of lock members 25 are shifted to a state where the lock member 25 is reliably engaged with the intermediate lock recess 37, and the relative rotational phase becomes the intermediate lock phase. There is no overshoot to pass through.

  Since the valve opening / closing timing control device A includes a pair of lock members 25, when hydraulic oil is discharged from the lock release port 40L before the relative rotational phase reaches the intermediate lock phase, one lock member is locked. The member 25 is engaged with the intermediate lock recess 37 prior to the other lock member 25. Thereafter, the displacement speed of the relative rotational phase is lowered, so that the other lock member 25 is reliably engaged with the intermediate lock recess 37.

  In particular, the timing at which the lock mechanism L shifts to the locked state during this operation may be immediately before the spool 50 reaches the first position P1 or after it reaches the first position P1. After the spool 50 reaches the first position P1, the state in which the hydraulic oil is discharged from the lock release port 40L is continued, so that the locked state is maintained.

  When the lock mechanism L is shifted to the locked state from the state in which the relative rotation phase is on the advance side with respect to the intermediate lock phase, the relative rotation phase is set to the intermediate lock by operating the spool 50 to the fourth position P4. Control is performed so that the spool 50 is moved to the first position P1 after being displaced from the phase toward the retard side.

[Another embodiment]
The present invention may be configured as follows in addition to the embodiment described above.

(A) Without changing the basic configuration of the control valve CV shown in the embodiment, the advance port 40A in the figure is changed to a retard port, and the retard port 40B in the figure is changed to an advance port. To do. Thereby, in the embodiment, instead of the configuration that realizes the shift to the locked state while displacing the relative rotational phase in the advance angle direction Sa, the locked state of the lock mechanism L while displacing the relative rotational phase in the retarded direction Sb. The transition to can be done reliably.

(B) As shown in FIG. 11, the outer diameter of the fifth land portion 50Le is set to the standard outer diameter φA, and the discharge passage R is parallel to the spool axis Y on the outer peripheral portion of the fifth land portion 50Le. A groove that becomes a posture is formed as a discharge flow path R. This groove may be plural or singular. Further, the groove may be formed while the outer diameter of the fifth land portion 50Le is set to the restricted outer diameter φB. In this case, the discharge flow path R is configured by the fifth land portion 50Le and the groove.

  As a modified example of this other embodiment (b), a groove may be formed as the discharge flow path R on the inner peripheral surface of the sleeve 40 into which the fifth land portion 50Le is fitted with the spool 50 in the first position P1. Is possible. In addition, it is also possible to combine the groove | channel of this modification with the groove | channel of another embodiment (b).

  In the configuration and modification of this other embodiment (b), a plurality of grooves are formed during the manufacture of the control valve CV, and the adjustment of the flow rate of the fluid is compared by individually setting the depth and width of each groove. It is also possible to do this easily.

(C) As shown in FIG. 12, the outer diameter of the fifth land portion 50Le is set to a standard outer diameter φA, and the end of the spool 50 is used as a discharge flow path R with respect to the fifth land portion 50Le. A communication hole for communicating with the fourth groove 50Gd is formed. The communication holes are preferably formed to have a small diameter so as to restrict the flow of hydraulic oil, and a plurality of communication holes may be formed, or a plurality of communication holes may be formed. Further, the communication hole may be formed by setting the outer diameter of the fifth land portion 50Le to the restricted outer diameter φB. In this case, the discharge passage R is constituted by the fifth land portion 50Le and the communication hole.

  As a modification of this other embodiment (c), a communication hole that communicates with the fourth groove 50Gd and the first drain port 40DA in a state where the spool 50 is at the first position P1 may be formed as the discharge flow path R. In addition, it is also possible to combine the communication hole of this modification with the communication hole of another embodiment (c).

  In the configuration and modification of this other embodiment (c), the flow passage cross-sectional area of the communication hole (discharge flow passage R) is a fixed value, so that it is difficult to change the change speed of the relative rotation phase. Management becomes easier.

  INDUSTRIAL APPLICABILITY The present invention can be used for a valve opening / closing timing control device that controls the opening / closing timing of a valve and a lock mechanism by supplying and discharging fluid.

1 Crankshaft 7 Camshaft (Intake camshaft)
20 Drive-side rotating body (external rotor)
25 Locking member 30 Driven side rotating body (internal rotor)
37 Engagement part (intermediate lock recess)
40 Sleeve 40A Advance port 40B Delay port 40L Unlock port 40DA Drain port (second drain port)
40PA pump port (first pump port)
40PB pump port (second pump port)
50 Spool 50Le Discharge control land (5th land)
60 Electromagnetic Solenoid A Valve Open / Close Timing Control Device E Internal Combustion Engine (Engine)
Ca advance angle chamber Cb retard angle chamber CV Control valve P1 Lock transition position (first position)
P2 Phase control position (second position)
P4 Phase control position (4th position)
R discharge flow path Y shaft core (spool shaft core)
φA outer diameter (outer diameter of other land / standard outer diameter)
φB outside diameter (outside diameter / restricted outside diameter of discharge control land)

Claims (5)

A drive-side rotator that rotates synchronously with the crankshaft of the internal combustion engine; and a driven-side rotator that rotates integrally with the camshaft of the internal combustion engine and rotates relative to the drive-side rotator. When the fluid is supplied to the advance angle chamber defined between the drive side rotary body and the driven side rotary body, the relative rotational phase between the drive side rotary body and the driven side rotary body is displaced in the advance direction, and the drive The relative rotational phase is displaced in the retarding direction by supplying a fluid to the retarding chamber that is between the side rotating body and the driven-side rotating body and is partitioned at a position different from the advance chamber, A lock mechanism that holds the relative rotation phase at a predetermined lock phase by engaging a lock member supported on one side of the engagement part formed on one of the drive side rotary body and the driven side rotary body Used for valve timing control device with A control valve, the control valve,
A sleeve, a spool accommodated in the sleeve, and an electromagnetic solenoid that moves the spool along an axis of the sleeve;
The sleeve has a pump port to which a fluid is supplied, an advance port communicating with the advance chamber, a retard port communicating with the retard chamber, and a space in which unlocking pressure is applied to the lock member. It has a lock release port that communicates and a drain port that allows fluid to be discharged,
The spool includes a plurality of land portions for controlling the flow of fluid, and supplies the fluid to one of the advance port and the retard port while supplying the fluid to the unlock port, and discharges the fluid from the other. Between the phase control position to be moved and the lock transition position in which fluid is supplied to one of the advance port and the retard port while the fluid is discharged from the lock release port and the fluid is discharged from the other. Is possible,
In the lock transition position, the fluid discharge amount from the discharge port from which the fluid is discharged out of the advance port or the retard port is the amount of fluid discharge from the discharge port in a position adjacent to the lock transition position. Control valve set less.   When the spool is in the lock transition position, the fluid is restricted to at least one of the outer peripheral portion of the discharge control land portion that is one of the plurality of land portions and the inner peripheral portion of the sleeve. The control valve according to claim 1, wherein a discharge passage for discharging is formed.   The discharge flow path is formed by setting an outer diameter of the discharge control land portion to be smaller than an outer diameter of another land portion so as to allow a fluid flow on an outer periphery of the discharge control land portion. Item 3. The control valve according to Item 2.   The control valve according to claim 2, wherein the discharge channel is formed by a groove.   The control valve according to claim 2, wherein the discharge channel is formed by a communication hole.

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