JP6187313B2 - Solenoid valve - Google Patents

Description

  The present invention relates to a control valve for a valve opening / closing timing control device, and more specifically, 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 a camshaft for valve opening / closing of the internal combustion engine. And a solenoid valve that supplies and discharges fluid to and from an advance chamber or a retard chamber formed therebetween.

  Patent Document 1 shows a drive-side rotating body (a rotor in the document) and a driven-side rotating body (a second rotating member in the document), and locks the relative rotational phase between the driving-side rotating body and the driven-side rotating body. A locking mechanism is described. This lock mechanism is composed of a lock recess formed in the driven side rotator and a lock member (lock body in the literature) that engages with this by a biasing force of a spring. By enabling the engagement of the lock body to the lock recess (transition to the lock state) with hydraulic oil discharged from the lock recess by a solenoid valve (hydraulic control valve in the literature), and supplying hydraulic oil to the lock recess The lock state can be released.

  The solenoid valve has a body formed with a port that communicates with the advance chamber, a port that communicates with the retard chamber, a port that controls the lock mechanism, a port that is supplied with hydraulic fluid from the hydraulic pump, and a port that discharges hydraulic fluid. Have. A spool is slidably accommodated inside the body, and the spool is operated to one of a plurality of positions by adjusting the power supplied to the electromagnetic solenoid.

  In Patent Document 1, when the engine is stopped, the ECU drains the advance chamber, the retard chamber, and the lock oil passage by setting the power supply amount to the solenoid valve to 0, and the fluctuation of the relative rotation phase due to the cam fluctuation torque. The operation | movement form which transfers to a locked state using is shown.

JP 2003-172109 A

  As described in Patent Document 1, by shifting the valve opening / closing timing control device to the locked state when the engine is stopped, the fluctuation of the relative rotational phase due to the action of the cam fluctuation torque is suppressed when the engine is started thereafter. And stable starting.

  However, even if the control disclosed in Patent Document 1 is performed, the locked state may not be entered, and there is a reality that the locked state cannot be entered even when the engine is stalled. When the engine is started in such a state where the valve opening / closing timing control device is in the unlocked state, the relative rotation phase of the valve opening / closing timing control device varies greatly due to the cam fluctuation torque, and the intake / exhaust valve opening / closing timing is changed. The engine startability was lowered due to the fluctuation of the engine.

  For this reason, when the lock mechanism of the valve timing control device is in the unlocked state, it is desired that the valve can be quickly shifted to the locked state. However, in the solenoid valve described in Patent Document 1 and the generally used solenoid valve, when fluid is supplied to the advance chamber or the retard chamber, the port corresponding to the solenoid valve is fully opened. Therefore, even when the relative rotation phase changes at a high speed and the lock member reaches a relative rotation phase that can be engaged with the lock recess, the lock member may not engage with the lock recess.

  In other words, a predetermined time is required for the lock member to fully engage with the lock recess, so that when the relative rotation phase changes at a high speed, the lock state is maintained even if the relative rotation phase reaches the lock phase. In some cases, it was not possible to move to. For this reason, it is possible to shift to the locked state by repeatedly displacing the relative rotational phase in the advance angle direction and the retard angle direction, but in such a transition mode, it may take extra time. There is room for improvement.

  An object of the present invention is to rationally configure a solenoid valve that enables a reliable transition to a locked state by reducing the displacement of the relative rotation phase of the valve opening / closing timing control device.

  The features of the present invention include a valve case, a spool that is mounted so as to be able to reciprocate from one end portion to the other end portion of the valve case, and an electromagnetic solenoid that drives and operates the spool. A main port to which a fluid discharged from an external fluid pressure pump is supplied, and a fluid that has flowed into the main port flows into an advance chamber or a retard chamber of a valve timing control device provided in an external internal combustion engine. Alternatively, the first port and the second port that allow the outflow from the advance chamber or the retard chamber, and the fluid returned from the valve opening / closing timing control device through the first port or the second port are discharged. A third port that allows the spool to be located at one end or the other end of the valve case, the main port communicates with the first port, and the second port When serial communication with the third port, the second port is in terms of communicating with the main port.

For example, assuming that the first port communicates with the advance chamber of the valve timing control device and the second port of the retard chamber communicates with the main port when the spool is at one end of the valve case. The fluid is supplied to the advance chamber through the first port, and the fluid in the retard chamber is discharged from the second port to the third port. At the same time, the second port communicates with the main port, so that the fluid from the third port is supplied to the retarding chamber.
In addition, when the internal combustion engine is started, there is almost no fluid in the advance chamber and retard chamber of the valve opening / closing timing control device, and if cam fluctuation torque acts from the camshaft in this situation, the valve opening / closing This causes fluctuations in the relative rotational phase of the timing control device (a phenomenon in which the timing control device alternately and rapidly changes between an advance angle and a delay angle). In contrast, in the present invention, when the lock mechanism is in a locked state when the internal combustion engine is started, it is possible to fill the advance chamber and the retard chamber with fluid, and then release the locked state. Also, it is possible to suppress flutter of the relative rotational phase.
Further, according to the present invention, when the lock mechanism is not in a locked state when the internal combustion engine is started, the amount of fluid supplied to the advance chamber is reduced, and the displacement in the advance direction is reduced. It is possible to ensure that the transition to is performed.

  The present invention, the valve opening and closing timing control device comprises a lock mechanism that is operated by a fluid so that the valve opening and closing timing is fixed at an intermediate phase between the most advanced angle phase and the most retarded angle phase, The valve case has a subport that receives fluid from the fluid pressure pump, a fourth port that allows the fluid flowing out from the subport to flow into or out of the lock mechanism, and the spool includes the spool And a fifth port for discharging the fluid returned from the lock mechanism through the fourth port when the valve case is at the end of the valve case and setting the lock mechanism in a locked state.

  According to this, when the spool is at one end of the valve case, the fluid from the fourth port is discharged through the fifth port, thereby ensuring the shift of the lock mechanism to the locked state. It is also possible to supply fluid to the advance chamber and retard chamber after unlocking the lock mechanism in the locked state, and even when the lock is released, the relative rotation phase of the valve timing control device Suppress fluctuations.

  The present invention may include a biasing member that biases the spool at one end of the valve case when the power supplied to the electromagnetic solenoid is zero.

  According to this, the spool can be held at one end portion of the valve case by the urging force of the urging member without consuming electric power even in a situation where electric power is required for the starter motor or the like, such as when starting the internal combustion engine. Thereby, the displacement speed of the relative rotational phase can be reduced without supplying electric power to the electromagnetic solenoid.

  In the present invention, when the electric power supplied to the electromagnetic solenoid is maximum, the spool is positioned at the other end of the valve case, the main port communicates with the second port, and the first port is the first port. The advance chamber and the retard chamber may be communicated with 3 ports and the main port.

According to this, when the electric power supplied to the electromagnetic solenoid is maximum, the spool reaches the other end of the valve case. Here, assuming that the first port communicates with the advance chamber of the valve timing control device and the second discharge port communicates with the retard chamber, the fluid from the main port flows from the second port to the retard chamber. The advance chamber fluid is supplied and discharged from the first port to the third port. At the same time, the advance chamber and the retard chamber communicate with each other.
Thus, for example, when the internal combustion engine is stopped, the relative rotational speed of the valve opening / closing timing control device can be reduced to easily shift to the locked state at the lock phase.

  In the present invention, when the spool is positioned at one of both end portions of the valve case, and the first port or the second port communicates with the third port and the main port, The area of the opening of the first port or the second port communicating with the port is configured to be larger than the area of the opening communicating with the third port.

According to this, for example, in the configuration in which the fluid from the main port is supplied to the first port, the main port communicates with the first port to supply the fluid, and at the same time, the first port communicates with the third port. Is discharged. In this case, since the opening area of the first port communicating with the main port is larger than the opening area communicating with the third port, the amount of fluid discharged from the first port to the third port is limited.
As described above, by limiting the amount of fluid discharged from the first port or the second port to the third port, the relative rotation phase of the valve timing control device can be surely displaced.

  In the present invention, when the spool is positioned at one of both end portions of the valve case, and the first port or the second port communicates with the third port and the main port, The area of the opening part of the communication path communicating from the port to the third port is larger than the area of the opening part of the part communicating with the third port. It is.

According to this, for example, in the configuration in which the fluid from the main port is supplied to the first port, the main port communicates with the first port to supply the fluid, and at the same time, the first port communicates with the third port. Is discharged. In this case, the area of the opening portion of the communication path communicating from the main port to the third port is larger than the area of the opening portion of the communication path communicating with the third port. The amount of fluid discharged directly from the main port to the third port is limited.
In this way, it is possible to reliably shift the relative rotation phase of the valve timing control device by limiting the amount of fluid discharged directly from the main port to the third port.

  The present invention includes a biasing member that biases the spool toward one end of the valve case, and when the electromagnetic force of the electromagnetic solenoid is smaller than the biasing force of the biasing member, the spool It may be arranged at one end.

  According to this, when electric power is supplied to the electromagnetic solenoid and the electromagnetic force generated by this supply is smaller than the biasing force of the biasing member, the spool is maintained at one end of the valve case.

The present invention includes a biasing member that biases the spool toward one end of the valve case, and when the electromagnetic force of the electromagnetic solenoid is larger than the biasing force of the biasing member, the spool It may be arranged at the other end.

  According to this, when electric power is supplied to the electromagnetic solenoid and the electromagnetic force generated by this supply is larger than the urging force of the urging member, the spool is maintained at the other end of the valve case.

1 is an overall view of a configuration of an internal combustion engine control system. It is the II-II sectional view taken on the line of the valve timing control apparatus 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 locked state in the most retarded angle lock phase. It is the figure which listed the position of a spool, the supply-discharge relationship of hydraulic fluid, etc. It is sectional drawing of the solenoid valve which has a spool in a 1st advance angle position. It is sectional drawing of the solenoid valve which has a spool in a 2nd advance position. It is sectional drawing of the solenoid valve which has a spool in a lock release position. It is sectional drawing of the solenoid valve which has a spool in a 2nd retard position. It is sectional drawing of the solenoid valve which has a spool in a 1st retard position. It is a figure which shows the relationship between the stroke of a spool, and opening areas, such as a port. It is a general view of the structure of the internal combustion engine control system of another embodiment (a). It is sectional drawing of the solenoid valve of another embodiment (a). It is the figure which listed the position of the spool of another embodiment (a), the supply / discharge relationship of hydraulic fluid, etc.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[Basic configuration]
As shown in FIGS. 1 to 4, a valve opening / closing timing control device A for setting the opening / closing timing of an intake valve Va of an engine E as an internal combustion engine, and a solenoid valve SV for controlling the valve opening / closing timing control device A by hydraulic pressure, The internal combustion engine control system includes the solenoid valve SV and an engine control unit 10 configured as an ECU for controlling start / stop of the engine E.

  The engine E (an example of an internal combustion engine) is provided in a vehicle such as a passenger car. This engine E has a crankshaft 1 in the lower part, accommodates a piston 3 in a cylinder bore formed in a cylinder block 2, and is configured in a four-cycle type in which the piston 3 and the crankshaft 1 are connected by a connecting rod 4. Has been.

  The upper part of the engine E is provided with an intake camshaft 5 and an exhaust camshaft, and the engine E is provided with a hydraulic pump P (an example of a fluid pressure pump) driven by the driving force of the crankshaft 1. The hydraulic pump P supplies the lubricating oil stored in the oil pan of the engine E to the solenoid valve SV as a working oil (an example of fluid) via the supply flow path 8. Further, the engine E includes a rotation speed sensor 1S that detects the rotation speed of the crankshaft 1 (the number of rotations per unit time) and a starter motor M.

  In this embodiment, a valve opening / closing timing control device A is provided at the shaft end of the intake camshaft 5. This valve opening / closing timing control device A includes an external rotor 20 as a driving side rotating body and an internal rotor 30 as a driven side rotating body. In this system, relative rotation between the external rotor 20 and the internal rotor 30 is performed. A phase sensor AS that detects a phase (hereinafter referred to as a relative rotational phase) is provided. The vehicle body also includes a start / stop button 11 for starting and stopping the engine E.

  The engine control unit 10 receives a signal from the phase sensor AS, a signal from the start / stop button 11 for stopping and starting the engine E, and a signal from the rotational speed sensor 1S. The engine control unit 10 also outputs control signals to the solenoid valve SV, the starter motor M, a fuel control system, an ignition control system, and the like necessary for engine operation.

  This internal combustion engine control system sets the opening / closing timing (opening / closing timing) of the intake valve Va by controlling the valve opening / closing timing control device A based on the rotational speed of the engine E, the load acting on the engine E, and the like. Control to improve or obtain necessary torque is executed. Further, in this internal combustion engine control system, when the engine E is stopped, the relative rotation phase is fixed at the intermediate lock phase Pm (an example of the intermediate phase) by the pair of lock mechanisms L of the valve opening / closing timing control device A. Perform transition control.

  In particular, in this internal combustion engine control system, the engine E is operated in a situation where the lock mechanism L is in the unlocked state, such as after the engine E has stopped without the pair of lock mechanisms L shifting to the locked state, such as engine stall. In starting, the relative rotational phase is displaced to the intermediate lock phase Pm, and control for shifting to the locked state by the pair of lock mechanisms L is performed.

[Valve opening / closing timing control device]
The valve opening / closing timing control device A is connected to the external rotor 20 as a driving side rotating body that rotates synchronously with the crankshaft 1 of the engine E and the intake camshaft by being connected to the intake valve Va of the engine E by a connecting bolt 31. 5 and an internal rotor 30 as a driven side rotating body that rotates integrally with the motor 5. The inner rotor 30 is included in the outer rotor 20, and these are relatively rotatable about the rotation axis X of the intake camshaft 5. Further, a pair of lock mechanisms L are provided between the outer rotor 20 and the inner rotor 30, and this lock mechanism L has a relative rotation phase as an intermediate lock phase Pm shown in FIG. Lock (fixed) to any lock phase with the phase Pr.

  The external rotor 20 includes an external rotor main body 21, a front plate 22, and a rear plate 23, which are integrated by fastening a plurality of fastening bolts 24. The outer rotor body 21 is integrally formed with a plurality of protrusions 21T that protrude inward in the radial direction with respect to the rotation axis X. A timing sprocket 23 </ b> S is formed on the outer periphery of the rear plate 23.

  The internal rotor 30 is disposed at a position sandwiched between the front plate 22 and the rear plate 23. The internal rotor 30 protrudes from the outer periphery of the internal rotor body 32 so as to come into contact with the cylindrical inner rotor body 32 closely contacting the protruding end of the protruding portion 21T of the external rotor body 21 and the inner peripheral surface of the external rotor body 21. And a plurality of vanes 33 provided. The vane 33 is biased by a spring or the like in a direction away from the rotation axis X.

  Thereby, in a state where the inner rotor 30 is included in the outer rotor 20, a plurality of fluid pressure chambers C are formed on the outer peripheral side of the inner rotor body 32 at an intermediate position between the projecting portions 21 </ b> T adjacent in the rotation direction. Further, these fluid pressure chambers C are partitioned by the vanes 33 to form an advance chamber Ca and a retard chamber Cb.

  As shown in FIG. 1, the urging force is applied across the internal rotor 30 and the front plate 22 until the relative rotational phase between the external rotor 20 and the internal rotor 30 reaches an intermediate lock phase Pm from the most retarded phase described later. A torsion spring 39 is provided to act. The range in which the urging force of the torsion spring 39 acts may exceed the intermediate lock phase Pm or may not reach the intermediate lock phase Pm.

  The timing chain 7 is wound around the output sprocket 6 provided on the crankshaft 1 of the engine E and the timing sprocket 23S. As a result, the external rotor 20 rotates in synchronization with the crankshaft 1. Although not shown in the drawings, a sprocket is also provided at the front end of the camshaft on the exhaust side, and a timing chain 7 is wound around the sprocket.

  In this embodiment, the intake camshaft 5 is provided with the valve opening / closing timing control device A. However, the valve opening / closing timing control device A is provided on the exhaust camshaft, and the intake camshaft 5 and the exhaust camshaft are connected to each other. You may prepare for both.

  As shown in FIGS. 2 to 4, in the valve opening / closing timing control device A, the external rotor 20 rotates in the driving rotation direction S by the driving force from the crankshaft 1. Further, the same direction as the drive rotation direction S of the inner rotor 30 with respect to the outer rotor 20 is referred to as an advance angle direction Sa, and the opposite direction is referred to as a retard angle direction Sb. In this valve opening / closing timing control device A, when the relative rotational phase is displaced in the advance direction Sa, the intake compression ratio is increased as the displacement amount is increased, and when the relative rotational phase is displaced in the retard direction Sb, the displacement amount is increased. The relationship between the crankshaft 1 and the intake camshaft 5 is set so as to reduce the intake compression ratio as it increases.

  The space in which the relative rotational phase is displaced in the advance direction Sa by the supply of hydraulic oil is the advance chamber Ca. Conversely, the space in which the relative rotational phase is displaced in the retard direction Sb by the supply of hydraulic oil is delayed. This is the corner chamber Cb. The relative rotational phase in a state where the vane 33 has reached the working end in the advance direction Sa (including the phase near the working end of the vane 33 in the advance direction Sa) is referred to as a most advanced phase, and the vane 33 is retarded. The relative rotational phase in a state where the operating end in the direction Sb (including the phase in the vicinity of the operating end of the vane 33 in the retarding direction Sb) has been reached is referred to as the most retarded phase.

[Valve opening / closing timing control device: lock mechanism, flow path configuration]
The lock mechanism L includes a lock member 25, a lock spring 26, an intermediate lock recess 37, and a most retarded angle lock recess 38.

  That is, a pair of guide grooves are formed in a radial posture with the rotation axis X as the center with respect to one protrusion 21T, and a plate-like lock member 25 is removably inserted into these guide grooves. Yes. The lock spring 26 urges the lock member 25 in a direction approaching the rotation axis X (lock direction). The shape of the lock member 25 is not limited to a plate shape, and may be a rod shape, for example.

  The intermediate lock recess 37 is configured so that the pair of lock members 25 are engaged with each other at the outer periphery of the inner rotor body 32 so that the relative rotation phase is at an intermediate lock phase Pm that is intermediate between the most advanced angle phase and the most retarded angle phase. Is formed in a groove shape along the circumferential direction.

  The most retarded angle locking recess 38 is formed in a groove shape parallel to the rotation axis X. When the relative rotation phase is at the most retarded angle lock phase Pr, the most retarded angle lock recess 38 is engaged with one of the lock members 25 and reaches the locked state.

  In particular, since the pair of lock members 25 are provided and the intermediate lock concave portion 37 is formed along the circumferential direction, one of the lock members 25 is the intermediate lock concave portion 37 when the intermediate lock phase Pm is shifted to the locked state. The lock member 25 facilitates the engagement of the other lock member 25 to the intermediate lock recess 37 in a state in which the width of fluctuation of the relative rotation phase is reduced.

  The internal rotor 30 is formed with an advance passage 34 communicating with the advance chamber Ca, a retard passage 35 communicating with the retard chamber Cb, and an unlock passage 36 communicating with the intermediate lock recess 37. Yes. An advance channel 34 communicates with the most retarded lock recess 38. The advance channel 34, the retard channel 35, and the lock release channel 36 are supplied and discharged with hydraulic oil by a solenoid valve SV.

  From these configurations, the engine control unit 10 controls the solenoid valve SV to supply hydraulic oil to one of the advance chamber Ca and the retard chamber Cb, as shown in FIGS. The control for setting the relative rotation phase in the range from the most retarded phase to the most advanced angle phase is realized.

(Solenoid valve)
As shown in FIGS. 6 to 10, the solenoid valve SV includes a valve case 40, a spool 50, an electromagnetic solenoid 60, and a spool spring 61. The spool 50 is accommodated in the spool housing space of the valve case 40 so as to be capable of reciprocating from one end to the other end of the valve case 40 along the spool axis Y. The electromagnetic solenoid 60 shifts the spool 50 by applying an electromagnetic force in a direction against a biasing force of the spool spring 61 (an example of a biasing member).

  In the solenoid valve SV, the spool 50 is set to the first advance angle position PA1 (one end portion of the valve case 40) shown in FIG. Further, in this solenoid valve SV, by increasing the power supplied to the electromagnetic solenoid 60, the second advance position PA2 and the unlocking position are resisted against the urging force of the spool spring 61 as shown in FIGS. It is set to any one of PL, the second retardation position PB2, and the first retardation position PB1 (the other end of the valve case 40). FIG. 5 shows the relationship between supply and discharge of hydraulic oil at each port at these positions.

The valve case 40 includes a first drain port 40DA (an example of a third port) , an advance port 40A, and a main pump port sequentially from the position close to the electromagnetic solenoid 60 in the direction along the spool axis Y. 40Pm, retardation port 40B, second drain port 40DB (an example of a third port), sub pump port 40Ps (an example of a sub port), an unlock port 40L, and a third drain port 40DC are formed. Yes.

  In particular, an advance port 40A (an example of a first port) and a retard port 40B (an example of a second port) are disposed at positions that sandwich the main pump port 40Pm (an example of a main port) in the direction along the spool axis Y. Is arranged. Further, the first drain port 40DA is disposed at a position closest to the electromagnetic solenoid 60, and the second drain port 40DB is disposed at a position away from the electromagnetic solenoid 60 from the retard port 40B.

  Further, the lock release port 40L (an example of the fourth port) and the third drain port 40DC (an example of the fifth port) are arranged on the side away from the electromagnetic solenoid 60 in the direction along the spool axis Y with respect to the auxiliary pump port 40Ps. Are arranged in this order.

  In the present invention, the positions of the advance port 40A and the retard port 40B are interchanged without changing the configuration of the solenoid valve in place of the advance port 40A and the retard port 40B in place of the above-described embodiment. The solenoid valve SV may be configured (by exchanging the position where the advance channel 34 and the retard channel 35 are connected).

  The main pump port 40Pm and the sub pump port 40Ps communicate with the hydraulic pump P through the supply flow path 8. The advance port 40A communicates with the advance chamber Ca via the advance channel 34. The retard port 40B communicates with the retard chamber Cb via the retard channel 35. The unlock port 40L communicates with the intermediate lock recess 37 through the unlock channel 36.

  The spool 50 has a cylindrical shape that is coaxial with the spool shaft core Y and forms a space in which air can flow. The spool 50 is arranged in the direction along the spool shaft core Y in order from the position close to the electromagnetic solenoid 60 to the first side. The sixth groove portions 51A to 51F are formed, and the first to fifth land portions 52A to 52E are formed.

  As a specific arrangement, the second groove portion 51B is arranged at a position communicating with the main pump port 40Pm. The first land portion 52A and the second land portion 52B are arranged at positions sandwiching the second groove portion 51B. Further, the first groove portion 51A is disposed on the side closer to the electromagnetic solenoid 60 than the first land portion 52A, and the third groove portion 51C is disposed on the spool spring side (anti-electromagnetic solenoid side) from the second land portion 52B. .

  The first land portion 52A controls the supply and discharge of hydraulic fluid to the advance port 40A, and the second land portion 52B controls the supply and discharge of hydraulic fluid to the retard port 40B.

  Further, the fourth groove portion 51D is disposed at a position where it can communicate with the sub pump port 40Ps. The third land portion 52C and the fourth land portion 52D are arranged at positions sandwiching the fourth groove portion 51D. Further, a sixth groove portion 51F, a fifth land portion 52E, and a sixth groove portion 51F are arranged on the spool spring side from the fifth groove portion 51E.

  In particular, in the solenoid valve SV of the present invention, the advance side deceleration passage 55 (communication passage) is formed by machining the outer periphery of the second groove portion 51B and the first groove portion 51A and a part of the inner peripheral surface of the valve case 40. ) And a retard side deceleration passage 56 (an example of a communication path).

  When the spool 50 is set to the first advance position PA1 shown in FIG. 6, the advance side deceleration flow path 55 retards a part of the fluid supplied from the main pump port 40Pm to the advance port 40A. It functions to send to the port 40B and the second drain port 40DB. Similarly, the retard side deceleration passage 56 is one of the fluid supplied from the main pump port 40Pm to the retard port 40B when the spool 50 is set to the first retard position PB1 shown in FIG. Function to send to the advance port 40A and the first drain port 40DA.

  That is, as shown in FIG. 5, the advance side deceleration channel 55 communicates the advance chamber Ca and the retard chamber Cb at the first advance position PA1, and the retard side deceleration channel 56 serves as the first delay channel 56. It functions to communicate the advance chamber Ca and the retard chamber Cb at the angular position PB1. The flow of the fluid at each position will be described later.

  The engine control unit 10 includes a power supply system that intermittently supplies power to the electromagnetic solenoid 60 in a short cycle, and sets the shift amount of the spool 50 by adjusting the power by setting the duty ratio of the power. To do.

[First advance angle position]
As shown in FIG. 6, when the spool 50 is in the first advance angle position PA1 (one end portion of the valve case 40), the second groove portion 51B is determined from the positional relationship between the first land portion 52A and the advance port 40A. The advance port 40A communicates with the main pump port 40Pm via Further, the retard port 40B and the second drain port 40DB communicate with each other from the positional relationship between the second land portion 52B and the retard port 40B. At the same time, the lock release port 40L and the third drain port 40DC communicate with each other from the positional relationship between the fifth groove portion 51E, the sixth groove portion 51F, and the lock release port 40L.

  Therefore, at the first advance angle position PA1, the hydraulic oil from the main pump port 40Pm is supplied to the advance port 40A, the hydraulic oil is discharged from the retard port 40B, and the hydraulic oil is discharged from the lock release port 40L. As a result, when the lock mechanism L is in the locked state, the advance chamber Ca and the retard chamber Cb can be filled with hydraulic oil. When the lock mechanism L is not in the locked state, more hydraulic oil is supplied to the advance chamber Ca than the retard chamber Cb, and the relative rotation phase is displaced in the advance direction Sa. When the relative rotational phase reaches the intermediate lock phase Pm, the lock member 25 of the lock mechanism L is engaged with the intermediate lock recess 37, and the state shifts to the intermediate lock state. Details of the flow of hydraulic oil in the advance side deceleration passage 55 will be described later.

[Second advance angle position]
As shown in FIG. 7, when the spool 50 is set to the second advance position PA2, the advance port is set via the second groove 51B from the positional relationship between the first land portion 52A and the advance port 40A. 40A communicates with the main pump port 40Pm. Further, the retard port 40B and the second drain port 40DB communicate with each other from the positional relationship between the second land portion 52B and the retard port 40B. At the same time, the lock release port 40L and the sub pump port 40Ps communicate with each other from the positional relationship between the fifth groove portion 51E, the sixth groove portion 51F, and the lock release port 40L.

  Therefore, at the second advance angle position PA2, the hydraulic oil from the main pump port 40Pm is supplied to the advance port 40A, the hydraulic oil is discharged from the retard port 40B, and the hydraulic oil is supplied to the lock release port 40L. The relative rotational phase is displaced in the advance angle direction Sa. As a result, when the lock state is in the intermediate lock phase Pm, the lock state is released and the relative rotation phase is displaced in the advance direction Sa.

(Unlock position)
As shown in FIG. 8, when the spool 50 is in the unlock position PL, the first land portion 52A closes the advance port 40A, and the second land portion 52B closes the retard port 40B. At the same time, the lock release port 40L and the sub pump port 40Ps communicate with each other from the positional relationship between the fifth groove portion 51E, the sixth groove portion 51F, and the lock release port 40L.

  Accordingly, at the unlock position PL, the hydraulic oil from the main pump port 40Pm is not supplied to either the advance port 40A or the retard port 40B, and the hydraulic oil is supplied to the lock release port 40L. The relative rotational phase is maintained.

[Second retard position]
As shown in FIG. 9, when the spool 50 is set to the second retard position PB2, the advance port is set via the first groove 51A due to the positional relationship between the first land portion 52A and the advance port 40A. 40A communicates with the first drain port 40DA. Further, the retard port 40B communicates with the main pump port 40Pm from the positional relationship between the second land portion 52B and the retard port 40B. At the same time, the lock release port 40L and the sub pump port 40Ps communicate with each other from the positional relationship between the fifth groove portion 51E, the sixth groove portion 51F, and the lock release port 40L.

  Accordingly, in the second retard position PB2, the hydraulic oil from the main pump port 40Pm is supplied to the retard port 40B, the hydraulic oil is discharged from the advance port 40A, and the hydraulic oil is supplied to the lock release port 40L. The relative rotational phase is displaced in the retarding direction Sb. As a result, when the lock state is in the intermediate lock phase Pm, the lock state is released and the relative rotation phase is displaced in the retarding direction Sb.

[First retard position]
As shown in FIG. 10, when the spool 50 is set to the first retard position PB1 (the other end of the valve case 40), the first land position 52A and the advance port 40A are used to determine the first. The advance port 40A communicates with the first drain port 40DA via the groove 51A. Further, the retard port 40B communicates with the main pump port 40Pm from the positional relationship between the second land portion 52B and the retard port 40B. At the same time, the lock release port 40L and the third drain port 40DC communicate with each other from the positional relationship between the fifth groove portion 51E, the sixth groove portion 51F, and the lock release port 40L.

  Accordingly, in the first retard position PB1, the hydraulic oil from the main pump port 40Pm is supplied to the retard port 40B, the hydraulic oil is discharged from the advance port 40A, and the hydraulic oil is discharged from the lock release port 40L. As a result, when the lock mechanism L is in the locked state, the advance chamber Ca and the retard chamber Cb can be filled with hydraulic oil. When the lock mechanism L is not in the locked state, more hydraulic oil is supplied to the retard chamber Cb than the advance chamber Ca, and the relative rotational phase is displaced in the retard direction Sb. When the relative rotational phase reaches the intermediate lock phase Pm, the lock member 25 of the lock mechanism L is engaged with the intermediate lock recess 37, and the lock state is entered. Details of the flow of hydraulic oil in the retard side deceleration passage 56 will be described later.

[Flow of hydraulic oil in the advance side deceleration passage]
When the engine E is stopped by operating the start / stop button 11, the engine control unit 10 displaces the relative rotation phase of the valve opening / closing timing control device A to the intermediate lock phase Pm, and after shifting to the intermediate lock state, the engine control unit 10 Control to completely stop E is performed. When the engine E is thus stopped, the solenoid valve SV is set to the first advance angle position PA1 or the second retard angle position PB2.

  In many cases due to this control, the valve timing control device A reaches the intermediate lock phase Pm, and the lock mechanism L reaches the locked state. However, there is a case where the lock mechanism L cannot be shifted to the locked state even by such control. In addition, the engine E may stop without the pair of lock mechanisms L shifting to the locked state like the engine stall. Further, when the engine E is started in a state where the lock mechanism L is in the unlocked state, the engine control unit 10 performs control to shift to a state in which the lock mechanism L is locked at the intermediate lock phase Pm.

  As a specific example of this control, when the engine E is started and the relative rotational phase detected by the phase sensor AS is in the intermediate lock phase Pm, the spool 50 of the solenoid valve SV is set to the first advance position PA1. Set. On the other hand, when the engine E is started in a situation where the relative rotational phase detected by the phase sensor AS is out of the intermediate lock phase Pm (a situation where the lock mechanism L is in an unlocked state), the spool of the solenoid valve SV 50 is set to the first advance angle position PA1, or the spool 50 of the solenoid valve SV is set to the first retard position PB1, thereby controlling the relative rotation phase to the intermediate lock phase Pm.

  That is, when the spool 50 is in the first advance angle position PA1, the advance port 40A communicates with the main pump port 40Pm with the advance port opening area Ta from the positional relationship between the first land portion 52A and the advance port 40A. To do. Further, due to the positional relationship between the second land portion 52B and the retard port 40B, the retard port 40B communicates with the second drain port 40DB through the retard port opening area Tb.

  In the solenoid valve SV of the present invention, as shown in FIG. 6, when the spool 50 is in the first advance angle position PA1, the end on the main pump port 40Pm side of the advance side deceleration passage 55 is on the pump side. The opening area Tp communicates with the main pump port 40Pm, and the end of the advance side deceleration passage 55 on the second drain port 40DB side communicates with the second drain port 40DB with a drain side opening area Td.

  Further, at the first advance angle position PA1, the end of the main pump port 40Pm of the retard side deceleration passage 56 communicates with the main pump port 40Pm via the pump side opening area Tp. The end on the second drain port 40DB side communicates with the second drain port 40DB through the drain side opening area Td.

  FIG. 11 shows the relationship among the advance port opening area Ta, the retard port opening area Tb, the pump side opening area Tp, and the drain side opening area Td with respect to the stroke when the spool 50 is operated. In the figure, the left end is the first advance position PA1 and the right end is the first retard position PB1. It should be noted that, at the first advance angle position PA1, the spool 50 does not operate, but the situation when it operates is graphed.

  In particular, when the first advance position PA1 is set, the pump side opening area Tp is set larger than the drain side opening area Td (Tp> Td), and the retarded port opening area Tb is set to the drain side opening area. It is set to be larger than Td (Tb> Td).

  Accordingly, when the spool 50 is in the first advance angle position PA1, most of the hydraulic oil from the main pump port 40Pm is supplied to the advance port 40A, and a part of the hydraulic oil in the main pump port 40Pm is It flows to the retard port 40B and the second drain port 40DB via the advance side deceleration channel 55. When the hydraulic oil flows in this way, the drain side opening area Td is set to be narrow, so that more hydraulic oil than the amount of hydraulic oil discharged is supplied to the retard port 40B.

  Thus, when the lock mechanism L is in the unlocked state, the operation of engaging the lock member 25 into the intermediate lock recess 37 when the intermediate lock phase Pm is reached to reduce the displacement speed of the counter rotation phase. To ensure the transition to the locked state.

[Flow of hydraulic oil in retarding side deceleration passage]
As described above, when the engine E is started in a state where the lock mechanism L is in the unlocked state, if the relative rotation phase is deviated from the intermediate lock phase Pm to the advance side, the relative rotation phase is set to the intermediate lock. In order to shift to the phase Pm, the engine control unit 10 may set the spool 50 of the solenoid valve SV to the first retard position PB1.

  That is, when the spool 50 is in the first retard position PB1, the retard port 40B communicates with the main pump port 40Pm through the retard port opening area Ub from the positional relationship between the second land portion 52B and the retard port 40B. To do. Further, the advance port 40A communicates with the first drain port 40DA through the advance port opening area Ua from the positional relationship between the first land portion 52A and the advance port 40A.

In the solenoid valve SV of the present invention, as shown in FIG. 10, when the spool 50 is in the first retard position PB1, the end on the main pump port 40Pm side of the retard side deceleration passage 56 is on the pump side. The opening area Up communicates with the main pump port 40Pm, and the end of the retard side deceleration passage 56 on the first drain port 40DA side communicates with the second drain port 40DB with the drain side opening area Ud.

  In the first retard position PB1, the advance port opening area Ua, the retard port opening area Ub, the pump side opening area Up, and the drain side opening area Ud with respect to the stroke when the spool 50 is operated are , And changes as shown in the graph of FIG.

  When the first retard angle position PB1 is set, the pump side opening area Up is set larger than the drain side opening area Ud (Up> Ud), and the retardation port opening area Ub is set to the drain side opening area. It is set to be larger than Ud (Ub> Ud).

  As a result, when the spool 50 is set to the first retard position PB1, most of the hydraulic fluid from the main pump port 40Pm is supplied to the retard port 40B, and one of the hydraulic fluid of the main pump port 40Pm is supplied. The portion flows to the advance port 40A and the first drain port 40DA via the retard side deceleration passage 56. When the hydraulic oil flows in this way, the drain side opening area Ud is set to be narrow, so that more hydraulic oil than the amount of hydraulic oil discharged is supplied to the advance port 40A, and the relative rotation The phase can be reduced in the displacement speed. As a result, when the relative rotational phase reaches the intermediate lock phase Pm, the lock member 25 is engaged with the intermediate lock recess 37 to ensure the shift to the locked state.

[Operation / Effect of Embodiment]
As described above, when the lock mechanism L is in the intermediate lock phase Pm when the engine E is started, the retarded position of the advance chamber Ca and the retard is set regardless of which of the first advance position PA1 and the first retard position PB1 is set. Hydraulic fluid is supplied to the corner chamber Cb. Thus, since the fluid filling is started into the advance chamber Ca and the retard chamber Cb, even when the lock mechanism L is unlocked, the relative rotational phase is caused by the torque acting from the intake camshaft 5. It is possible to suppress fluctuations that fluctuate greatly.

  If the lock mechanism L is not in the intermediate lock phase Pm when the engine E is started, the valve opening / closing timing is set by setting the spool 50 of the solenoid valve SV to the first advance angle position PA1 or the first retard angle position PB1. The displacement of the relative rotational phase of the control device A is performed at a low speed. When the relative rotational phase reaches the intermediate lock phase Pm due to this displacement, the pair of lock members 25 can be reliably engaged with the intermediate lock recess 37 and held at the intermediate lock phase Pm by the lock mechanism L.

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

(A) As shown in FIGS. 12 to 14, the solenoid valve SV is composed of a phase control valve SV1 and a lock control valve SV2. The phase control valve SV1 is configured to supply and discharge hydraulic fluid to and from the advance chamber Ca and the retard chamber Cb, and is operated to the advance position PA, the neutral position N, and the retard position PB. It is configured freely. In this different embodiment (a), those corresponding to the embodiment are given the same numbers and symbols as in the embodiment.

  As shown in FIG. 13, the phase control valve SV <b> 1 is set to the advance position PA set by the urging force of the spool spring 61 in a state where power is not supplied to the electromagnetic solenoid 60. In this advance angle position PA, the hydraulic oil from the hydraulic pump P is supplied to the advance chamber Ca and the hydraulic oil from the retard chamber Cb is discharged. Further, the advance side deceleration passage 55 functions at the advance position PA.

  The configuration of the phase control valve SV1, as shown in FIG. 13, is a configuration for controlling the lock mechanism L (sub pump port 40Ps, lock release port 40L, fourth, among the configurations of the solenoid valve SV described in the embodiment). To 6th groove portion, 4th and 5th land portions, etc.). Further, the phase control valve SV1 does not include the retard side deceleration flow path 56 of the embodiment.

  In the solenoid valve SV, the neutral position N is reached as the electric power supplied to the electromagnetic solenoid 60 increases. In this neutral position N, the hydraulic oil is prevented from being supplied to and discharged from the advance chamber Ca and the retard chamber Cb. Further, the retard position PB is reached by increasing the power supplied to the electromagnetic solenoid 60. In this retard position PB, the hydraulic oil of the hydraulic pump P is supplied to the retard chamber Cb, and the hydraulic oil of the advance chamber Ca is discharged.

  Furthermore, the lock control valve SV2 is configured as a two-position switching type so as to control the supply and discharge of fluid to and from the intermediate lock recess 37. Thus, in the case where the solenoid valve SV is constituted by the phase control valve SV1 and the lock control valve SV2, the unlocking timing of the lock mechanism L can be arbitrarily set, so that the lock mechanism L is in the locked state when the engine E is started. In this case, the advance chamber Ca and the retard chamber Cb are sufficiently filled with the hydraulic oil, and then the lock is released to suppress the fluctuation of the relative rotational phase.

  FIG. 14 shows the supply / discharge relationship of the hydraulic oil at each port at the three positions of the phase control valve SV1. As shown in the figure, when the spool 50 is in the advance position PA, the advance side deceleration passage 55 functions to communicate the advance chamber Ca and the retard chamber Cb. Further, before reaching the neutral position N from the advance angle position PA, the flow of hydraulic oil in the advance side deceleration passage 55 is blocked, and the displacement speed in the advance angle direction Sa increases.

  Even when configured as in this different embodiment (a), when the spool 50 of the phase control valve SV1 is set to the advance position PA, the advance side deceleration passage 55 is used in the embodiment. In the same manner as described above, hydraulic oil flows, and the displacement speed of the relative rotational phase in the advance direction Sa is reduced.

  As a modified example of this another embodiment (a), when the spool 50 is set to the retard position PB, the advance chamber Ca and the retard chamber Cb are set as in the first retard position PB1 of the embodiment. You may provide the retard angle side deceleration flow path 56 connected. By configuring as in this modification, the displacement speed in the retarding direction Sb can be reduced.

(B) The lock mechanism L includes a single lock member 25 and a single lock spring 26 instead of a pair of lock members 25 and a lock spring 26 corresponding thereto as shown in the embodiment. It is possible to configure. In addition, as a configuration using a pair of lock mechanisms L, the lock mechanisms L may be arranged at two locations that are opposed to each other with the rotation axis X interposed therebetween.

(C) In the present invention, only the advance side deceleration passage 55 corresponding to the first advance position PA1 set in a state where no electric power is supplied to the electromagnetic solenoid 60 is formed. By forming a single deceleration passage in this way, the configuration of the solenoid valve SV is simplified, and the cost of the solenoid valve SV can be reduced.

(D) The advance side deceleration passage 55 is formed on at least one of the outer periphery of the land and the inner periphery of the valve case 40. By forming the advance side deceleration passage 55 on one side, the solenoid valve SV can be easily manufactured. Similarly, the retard side deceleration flow path 56 may be formed.

  The present invention can be used for a solenoid valve that controls a relative rotation phase and a lock mechanism of a valve opening / closing timing control device.

40 Valve case 40Pm Main port (Main pump port)
40Ps sub port (sub pump port)
40A 1st port (advance port)
40B 2nd port (retarding port)
40DB 3rd port (2nd drain port)
40L 4th port (lock release port)
40DC 5th port (3rd drain port)
50 Spool 55 Communication path (advance side deceleration path)
56 Communication path (retarding side deceleration flow path)
60 Electromagnetic solenoid 61 Biasing member (spool spring)
A Valve timing control device E Internal combustion engine
Ca advance chamber Cb retard chamber P Fluid pressure pump (hydraulic pump)
Pm Intermediate phase (Intermediate lock phase)
L Lock mechanism Ta Opening area (Advance port opening area)
Tb Opening area (retarding port opening area)
Tp Opening area (pump side opening area)
Td Opening area (drain side opening area)

Claims (8)

A valve case,
A spool that is reciprocally movable from one end to the other end of the valve case;
An electromagnetic solenoid for driving the spool, and
In the valve case,
A main port to which fluid discharged from an external fluid pressure pump is supplied;
A first port allowing fluid flowing into the main port to flow into or from the advance chamber or retard chamber of a valve opening / closing timing control device provided in an external internal combustion engine; A second port;
A third port allowing the fluid returned from the valve opening / closing timing control device via the first port or the second port to be discharged;
When the spool is located at one end or the other end of the valve case, the main port communicates with the first port, and the second port communicates with the third port, the second port is the main port. Solenoid valve that communicates with the port. The valve opening / closing timing control device includes a lock mechanism that is operated by fluid so that the valve opening / closing timing is fixed at an intermediate phase between the most advanced angle phase and the most retarded angle phase,
The valve case is
A subport for receiving fluid from the fluid pressure pump;
A fourth port that allows fluid flowing out of the subport to flow into or out of the locking mechanism;
5. A fifth port that discharges fluid returned from the lock mechanism through the fourth port when the spool is at an end of the valve case, and sets the lock mechanism in a locked state. The solenoid valve according to 1.   3. The solenoid valve according to claim 1, further comprising an urging member that urges the spool at one end portion of the valve case when electric power supplied to the electromagnetic solenoid is zero. When the power supplied to the electromagnetic solenoid is maximum, the spool is located at the other end of the valve case,
4. The solenoid valve according to claim 3, wherein the main port communicates with the second port, the first port communicates with the third port and the main port, and the advance chamber and the retard chamber communicate with each other. . The spool is located at one end of either end of the valve case;
When the first port or the second port communicates with the third port and the main port,
The solenoid according to any one of claims 1 to 4, wherein an area of the opening of the first port or the second port communicating with the main port is larger than an area of the opening communicating with the third port. valve. The spool is located at one end of either end of the valve case;
When the first port or the second port communicates with the third port and the main port,
Of the communication path communicating from the main port to the third port, the area of the opening part of the part communicating with the main port is larger than the area of the opening part of the part communicating with the third port. The solenoid valve according to claim 5.   An urging member for urging the spool to one end of the valve case, and when the electromagnetic force of the electromagnetic solenoid is smaller than the urging force of the urging member, the spool is disposed at one end of the valve case; The solenoid valve according to claim 1 or 2. An urging member for urging the spool to one end of the valve case, and when the electromagnetic force of the electromagnetic solenoid is larger than the urging force of the urging member, the spool is attached to the other end of the valve case; The solenoid valve according to claim 1 or 2, which is arranged.

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