JP2015007400A - Solenoid with check valve and valve opening/closing timing controller using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a solenoid with a check valve and a valve opening/closing timing controller capable of preventing reduction in hydraulic pressure of supplied hydraulic oil.SOLUTION: A solenoid with a check valve comprises: a body 42; a first channel 60, a second channel 62, and a third channel 64 each formed in the body 42, having one end portion open to an outside of the body 42, and having the other end portion present in the body 42, the first channel 60, the second channel 62, and the third channel 64 communicating with one another; a first valve 44 provided between the first channel 60 and the second channel 62; a second valve 54 provided between the second channel 62 and the third channel 64; and a solenoid portion. During supply of a current to the solenoid portion, the first valve 44 is opened and the second valve 54 is closed, and hydraulic oil flows from the first channel 60 to the second channel 62 if hydraulic pressure of the hydraulic oil in the first channel 60 is higher than that in the second channel 62. Both the first valve 44 and the second valve 54 are closed to restrict flow of the hydraulic oil from the second channel 62 if the hydraulic pressure in the second channel 62 is higher than that in the first channel 60.

Description

  The present invention relates to a solenoid with a check valve and a valve timing control apparatus using the solenoid.

  In general, the optimum opening / closing timing of the intake / exhaust valves varies depending on the operating conditions of the engine such as when the engine is started and when the vehicle is running. Therefore, in the valve opening / closing timing control device, for example, by restraining the relative rotation phase of the driven side rotating body with respect to the rotation of the driving side rotating body at the start of the engine to a predetermined phase between the most advanced angle phase and the most retarded angle phase, The intake / exhaust valve opening / closing timing that is optimal for engine startup is achieved, and the fluid pressure chamber partition formed by the drive-side rotator and driven-side rotator is prevented from rocking and generating sound. ing.

  The lock mechanism for constraining the relative rotational phase to a predetermined phase includes, for example, a lock member and a spring that applies a biasing force to the lock member on either the driving side rotating body or the driven side rotating body. Some of the other rotating bodies have a recess. In this lock mechanism, the lock member is moved by the urging force of the spring to be engaged with the recess to be in the locked state, and the lock member is separated from the recess by the pressure of hydraulic oil larger than the urging force of the spring to be in the unlocked state. .

  Patent Document 1 discloses a valve opening / closing timing control device having the lock mechanism as described above. This valve opening / closing timing control device is provided with a lock mechanism that locks the relative rotation phase of the internal rotor with respect to the external rotor at a predetermined intermediate lock phase between the most retarded angle phase and the most advanced angle phase. The lock mechanism includes a lock piece, a lock recess that fits into the lock piece, and a spring that biases the lock piece toward the lock recess. Supply and discharge of the hydraulic oil to and from the lock mechanism are performed using an oil switching valve (OSV), thereby locking and unlocking in the intermediate lock phase.

  Patent Document 2 also discloses an engine valve timing control device having the lock mechanism as described above. In this valve timing control device, when the hydraulic pressure drops, the lock position is not unlocked, or in order not to unintentionally lock from the unlocked state, within a range that does not straddle the locked position. There is a function of switching to valve timing control and executing control to the original target valve timing as much as possible while preventing problems due to unintentional locking. Specifically, the oil pressure is determined based on the oil temperature of the hydraulic oil and the engine speed, and if the oil pressure is lower than a predetermined value, it is checked whether or not the current angle is larger than the lock position. When the current angle ≦ the lock position and the target angle <the lock position, the control to the target angle is executed only on the retard side, and when the target angle ≧ the lock position, the hydraulic pressure lowering lock control is executed. On the other hand, if current angle> lock position and target angle ≦ lock position, hydraulic pressure reduction lock control is executed, and if target angle> lock position, control to the target angle is executed only on the advance side.

JP 2007-247509 A JP 2011-74840 A

  In the valve opening / closing timing control device of Patent Document 1, the lock piece is separated by the hydraulic pressure of the hydraulic oil supplied to the lock recess to realize the unlocked state. Even if the lock is released once, if the relative rotational phase is subsequently changed, the hydraulic pressure acting on the advance chamber and the retard chamber varies, and the hydraulic pressure acting on the lock recess varies accordingly. As a result, the hydraulic pressure in the lock recess may be lower than the hydraulic pressure required to maintain the unlocked state. If the relative rotational phase is changed across the intermediate phase in such a state, the lock piece protrudes at the intermediate lock phase and is caught in the lock recess as shown by the circled area in FIG. There was a problem that it could not be changed smoothly.

  In the valve timing control device of Patent Document 2, valve timing control is performed within a range that does not straddle the lock position when the hydraulic pressure is low, so it is optimal when it is necessary to straddle the lock position in order to control to the optimum target angle. There is a problem that control to a target angle is not performed.

  In view of the above problems, an object of the present invention is to provide a solenoid with a check valve in which the hydraulic pressure of supplied hydraulic oil does not decrease, and a valve opening / closing timing control device using the solenoid.

  In order to solve the above-described problem, the characteristic configuration of the solenoid with a check valve according to the present invention is formed in a body and the body, and one end is opened to the outside of the body and the other end is A first flow path inside the body; a first end formed in the body, with one end open to the outside of the body and the other end inside the body; A second flow path communicating with the second flow path is formed in the body, and one end is opened to the outside of the body and the other end is inside the body and communicates with the second flow path. The third flow path, the drive mechanism driven by the electromagnetic force generated by energization and the biasing force of the spring, and the first flow path and the second flow according to the electromagnetic force and the biasing force of the spring. A first valve that moves to selectively communicate with or shut off the road; A second valve that moves so as to selectively communicate or block the second flow path and the third flow path in accordance with the electromagnetic force and the biasing force of the spring, and When the second valve moves so that the second channel and the third channel communicate with each other when de-energized, hydraulic fluid flows from the second channel to the third channel, When the drive mechanism is energized and when the hydraulic pressure of the hydraulic fluid in the first flow path is higher than the hydraulic pressure in the second flow path, the first valve is connected so that the first flow path and the second flow path are communicated with each other. By moving, the hydraulic oil flows from the first flow path to the second flow path, and the hydraulic pressure of the hydraulic oil in the second flow path is higher than the hydraulic pressure in the first flow path when the drive mechanism is energized. Sometimes, the flow between each of the first flow path, the second flow path, and the third flow path is blocked. Thus, when both the first valve and the second valve move, the flow of hydraulic oil from the second flow path to both the first flow path and the third flow path is restricted. .

  With such a characteristic configuration, when the drive mechanism is energized, when the hydraulic pressure of the hydraulic fluid in the first flow path is higher than the hydraulic pressure in the second flow path, the first flow path and the second flow path. The first valve moves so as to communicate with the second flow path, and the second valve moves so that the second flow path and the third flow path are blocked, so that the first flow path is changed to the second flow path. Hydraulic oil is supplied toward the vehicle. Hereinafter, the state of the valve when the valve moves and the two flow paths communicate with each other is “open state”, and when the valve moves and the two flow paths are blocked, The state is referred to as a “closed state”. Then, when the hydraulic pressure of the hydraulic fluid in the first flow path is lower than the hydraulic pressure in the second flow path, the flow among the first flow path, the second flow path, and the third flow path is blocked. Since both the first valve and the second valve are moved, both the first valve and the second valve are closed and function as check valves. The flow of hydraulic oil is restricted to both of the third flow paths. Therefore, the hydraulic pressure of the hydraulic oil once supplied to the second flow path does not decrease while energization of the drive mechanism is continued.

  In the solenoid with a check valve according to the present invention, when the drive mechanism is not energized, the second valve body of the second valve contacts the first valve body of the first valve to transmit the urging force. Thus, it is preferable that the first valve moves and the first flow path and the second flow path are shut off.

  With such a configuration, both the closed state of the first valve and the open state of the second valve can be realized simultaneously with only the urging force of the drive mechanism.

  In the solenoid with a check valve according to the present invention, it is preferable that the first valve body and the second valve body are spheres having the same size.

  With such a configuration, the first valve body and the second valve body can be made into a common part, and the management cost and part cost of the part can be reduced, and the cost can be reduced.

  In the solenoid with a check valve according to the present invention, the first valve body is a leaf valve, a seat stopper that regulates the amount of movement of the leaf valve, and a spacer that makes the amount of movement of the leaf valve and the stopper constant. The first valve body is preferably moved according to the hydraulic pressure of the hydraulic oil acting on the leaf valve.

  With such a configuration, a small solenoid with a check valve having a short overall length and an equivalent function can be provided.

  In the valve opening / closing timing control device according to the present invention, the driving side rotating body that rotates synchronously with the crankshaft of the internal combustion engine and the driving side rotating body are arranged so as to have the same axis as the driving side rotating body. A driven-side rotator that rotates synchronously with the camshaft of the other, and the other of the drive-side rotator and the driven-side rotator that is accommodated in either the drive-side rotator or the driven-side rotator. And a recess formed in the other rotating body so that the locking member can be fitted when the locking member moves, and the locking member moves. A locked state in which the relative rotational phase of the driven-side rotator with respect to the driving-side rotator is constrained to an intermediate lock phase between a most advanced angle phase and a most retarded angle phase by being fitted into the recess, and the lock Member is in front An intermediate lock mechanism that can selectively switch between an unlocked state in which the restraint is released by separating from the recess, and hydraulic fluid that is communicated to the recess and supplied to and discharged from the recess The unlocking flow path, the oil pump supplying hydraulic oil to the unlocking flow path, the unlocking flow so that the first flow path communicates with the oil pump and the second flow path communicates with the recess. It is preferable to include the above-described solenoid with a check valve attached on the road.

  With this configuration, once the hydraulic pressure of the hydraulic oil supplied to the recess reaches the hydraulic pressure necessary for unlocking, even if the hydraulic pressure acting on the solenoid with a check valve subsequently fluctuates, Since the second valve functions as a check valve, the hydraulic pressure acting on the recess does not decrease. As a result, even when the relative rotation phase is changed across the intermediate lock phase in the unlocked state, the relative rotation phase can be changed smoothly without being caught by the intermediate lock phase.

It is a longitudinal section showing the structure of the solenoid with a check valve concerning a 1st embodiment. It is a partial expanded sectional view of the solenoid with a check valve which operates in the first mode. It is a partial expanded sectional view of the solenoid with a check valve which operates in the second mode. It is a partial expanded sectional view of the solenoid with a check valve which operates in the third mode. It is a partial expanded sectional view of the solenoid with a check valve concerning a 2nd embodiment which operates in the 1st mode. It is a partial expanded sectional view of the solenoid with a check valve which operates in the second mode. It is a partial expanded sectional view of the solenoid with a check valve which operates in the third mode. It is a disassembled perspective view showing the structure of a 1st valve body. It is a longitudinal section showing the composition of the valve timing control device using the solenoid with a check valve concerning this embodiment. FIG. 10 is a cross-sectional view taken along the line XX of FIG. 9 showing a locked state. FIG. 10 is a cross-sectional view taken along the line XX of FIG. 9 showing the unlocked state. It is a graph showing the time change of the camshaft phase when the conventional OSV is used. It is a graph showing the time change of a camshaft phase when the solenoid with a non-return valve concerning this embodiment is used as OSV.

1. First Embodiment [Structure of Solenoid with Check Valve]
Hereinafter, 1st Embodiment of the solenoid 1 with a non-return valve which concerns on this invention is described in detail using FIGS. 1-4. As shown in FIG. 1, the solenoid 1 with a check valve is composed of a solenoid part 10 and a check valve part 40. The solenoid part 10 includes a case 12, a cylindrical coil 14, and a core as a cylindrical member. 20, a yoke 22, a plunger 24, a spring 26, a shaft 28, and a connector 30. The check valve portion 40 includes a body 42, a first valve 44, and a second valve 54. The axes of the case 12, the cylindrical coil 14, the core 20, the yoke 22, the plunger 24, the spring 26, the shaft 28, the body 42, the first valve 44, and the second valve 54 are all coaxial with the axis 2. It is arranged to be. The solenoid unit 10 is an example of a drive mechanism.

  The case 12 has a cylindrical shape. The cylindrical coil 14 is disposed inside the case 12 in the radial direction, and is configured by winding a copper wire 18 covered with an insulator around a bobbin 16 made of an insulator. The core 20 includes a disk part 20a having an outer diameter substantially the same as the inner diameter of the case 12, and a bottomed cylindrical part 20b perpendicular to the disk part 20a formed by narrowing the center of the disk part 20a. The yoke 22 includes a disc portion 22a having an outer diameter substantially the same as the outer diameter of the case 12, and a cylindrical portion 22b perpendicular to the disc portion 22a formed by narrowing the center of the disc portion 22a. The bottom of the cylindrical portion 22b is opened, and the plunger 24 is held by the inner surface of the cylindrical portion 22b. The case 12, the disk portion 20a, and the disk portion 22a are assembled so as to contact each other, and the cylindrical coil 14 is accommodated in a space formed by the case 12, the core 20, and the yoke 22. The case 12, the core 20, and the yoke 22 are all made of a ferromagnetic material such as pure iron and serve as a magnetic path for lines of magnetic force generated by energizing the cylindrical coil 14.

  The plunger 24 has a cylindrical shape, and a bottomed hole 24a is formed in the center of the surface of the core 20 that faces the bottom 20c. The plunger 24 is made of a ferromagnetic material such as pure iron, and the surface thereof is plated with a nonmagnetic material such as nickel. A spring 26, which is a compression coil spring, is inserted between the bottom 24b of the hole 24a of the plunger 24 and the bottom 20c of the core 20, whereby the plunger 24 is separated from the core 20 along the axis 2 ( An urging force for movement to the left in FIG. 1 is applied. The plunger 24 moves to the left in FIG. 1 by the urging force of the spring 26, and moves to the right by the electromagnetic force generated by energizing the cylindrical coil 14.

  The shaft 28 has a cylindrical shape and is disposed adjacent to the plunger 24. In FIG. 1, the left end of the shaft 28 is tapered, and a pressing portion 28 a having a smaller outer diameter than the right end is formed. When the plunger 24 moves to the left in FIG. 1, the shaft 28 also moves to the left. Since the plunger 24 and the shaft 28 are not joined, the shaft 28 does not follow even if the plunger 24 moves to the right. However, the plunger 24 and the shaft 28 may be joined.

  The connector 30 includes a resin cover 32 a and a socket housing 32 b and metal pins 34. The cover 32a and the socket housing 32b are integrally formed by injection molding or the like. The cover 32 a covers the gap between the cylindrical coil 14 and the case 12 and the entire side of the core 20 not facing the plunger 24. The socket housing 32b is formed so as to surround the pin 34, and constitutes a fitting portion with a mating connector (not shown). The pin 34 is electrically connected to the copper wire 18, and when a voltage is applied to the pin 34 through the mating connector, a current flows through the copper wire 18 and magnetic lines of force are generated.

  The body 42 of the check valve portion 40 is made of a nonmagnetic metal such as aluminum, and one end of the case 42 is in contact with the yoke 22 and integrated. A concave hole 42a for receiving the plunger 24 when the plunger 24 moves to the left and a through hole 42b for holding the shaft 28 from the bottom surface of the concave hole 42a are formed from the surface in contact with the yoke 22 of the body 42. Yes.

  As shown in FIG. 2, at the other end of the body 42, a first flow path 60 having a circular cross section with one end opened to the outside of the body 42 and the other end inside the body 42 has an axis 2. It is formed along the direction. A first valve seat 48 having a flow hole 48a in the center is inserted into the other end of the first flow path 60, and is fixed by press-fitting a cylindrical fixing ring 50. A second flow path 62 is formed on the right side of the first valve seat 48. The second flow path 62 communicates with the first flow path 60 through the circulation hole 48a. The second flow path 62 includes a second cylindrical flow path 62a along the axis 2, a second side flow path 62b formed on the side surface of the second cylindrical flow path 62a, and a second cylindrical flow. And a second release channel 62c formed perpendicular to the shaft center 2 so as to pass through the path 62a and the second side channel 62b and be opened to the outside of the body 42. The inner diameter of the second cylindrical channel 62a is larger than the inner diameter of the flow hole 48a. In the body 42, a second valve seat 58 having a flow hole 58a smaller than the inner diameter of the second cylindrical channel 62a is provided at the end of the second cylindrical channel 62a opposite to the first valve seat 48. Is formed.

  A first valve body 46 that opposes the first valve seat 48 and a second valve body 56 that opposes the second valve seat 58 are disposed adjacent to the second cylindrical flow path 62a. The first valve body 46 and the second valve body 56 are both metal spheres and are the same parts. The first valve body 46, the first valve seat 48, and the fixing ring 50 constitute a first valve 44, and the second valve body 56 and the second valve seat 58 constitute a second valve 54. The first valve body 46 and the second valve body 56 are movable in the direction along the axis 2 in the second cylindrical flow path 62a. By making the 1st valve body 46 and the 2nd valve body 56 into a common component, the management cost and component cost of components can be reduced and cost reduction can be aimed at.

  In FIG. 2, a third flow path 64 is formed on the right side of the second valve seat 58. The third flow path 64 communicates with the second flow path 62 through the flow hole 58a. The third flow path 64 is formed in a direction perpendicular to the axial center 2 so as to be open to the outside of the body 42 through the third cylindrical flow path 64a along the axial center 2 and through the third cylindrical flow path 64a. A third release flow path 64c. The inner diameter of the third cylindrical channel 64a is larger than the inner diameter of the flow hole 58a. In FIG. 2, a through hole 42b is formed on the right side of the third release channel 64c, and the third channel 64 and the through hole 42b communicate with each other.

  In the first valve 44, when the first valve body 46 and the first valve seat 48 are in contact with each other, the first flow path 60 and the second flow path 62 are blocked, and the first valve 44 is in a closed state. Become. When the first valve body 46 and the first valve seat 48 are separated from each other, the first flow path 60 and the second flow path 62 communicate with each other via the flow hole 48a, and the first valve 44 is in an open state. Become. Similarly, when the second valve body 56 and the second valve seat 58 are in contact with each other in the second valve 54, the second flow path 62 and the third flow path 64 are blocked, and the second valve 54 is Closed. When the second valve body 56 and the second valve seat 58 are separated from each other, the second flow path 62 and the third flow path 64 communicate with each other through the flow hole 58a, and the second valve 54 is in an open state. Become. In the solenoid 1 with a check valve, the first channel 60 is a channel through which hydraulic oil flows from the outside, the second channel 62 is a channel through which hydraulic oil flows out or flows from the second release channel 62c, The channel 64 is a channel through which hydraulic oil flows out from the third release channel 64c.

  The solenoid 1 with a check valve is used as an OSV (oil switching valve) for switching between supply and discharge of hydraulic oil to and from a recess 152 constituting the intermediate lock mechanism 150 of the valve opening / closing timing control device 100 shown in FIG. 1 to 4 show a state where the solenoid 1 with a check valve is used in the valve opening / closing timing control device 100. In these drawings, the first flow path 60 of the solenoid 1 with a check valve is connected so that the hydraulic oil discharged from the oil pump 161 flows in, and the second release flow path 62c of the second flow path 62 is in the middle. A state is shown in which the third release flow path 64c of the third flow path 64 is connected to communicate with the recess 152 of the lock mechanism 150 and is connected to discharge the hydraulic oil toward the oil pan 165.

[Operation of solenoid with check valve]
Next, operation | movement of the solenoid 1 with a non-return valve is demonstrated using drawing. As shown in FIG. 2, when the cylindrical coil 14 is not energized, no electromagnetic force is generated, and the plunger 24 moves to the left by the urging force of the spring 26. Along with this, the shaft 28 is moved leftward by applying a leftward force from the plunger 24, and the second valve body 56 is moved leftward by being applied a leftward force from the pressing portion 28a. 46 is applied with a leftward force from the second valve body 56 and moves to the left to contact the first valve seat 48. That is, the urging force of the spring 26 acts on the plunger 24, the shaft 28, the second valve body 56, and the first valve body 46. As a result, the first valve 44 can be closed and the second valve 54 can be opened only by the urging force of the spring 26. Hereinafter, this state is referred to as a first mode. The first mode is a mode in which hydraulic oil flows in from the second flow path 62 and flows out from the third flow path 64. That is, the first mode is a mode for discharging hydraulic oil supplied to the intermediate lock mechanism 150 to the oil pan 165.

  As shown in FIG. 3, when the cylindrical coil 14 is energized, an electromagnetic force is generated, and this electromagnetic force acts on the plunger 24. As a result, the plunger 24 overcomes the urging force of the spring 26 and moves to the right, and the urging force of the spring 26 does not act on the shaft 28, the second valve body 56, and the first valve body 46, and is free to move. It becomes a state. When hydraulic oil flows from the first flow path 60 in this state, the first valve body 46 moves to the right due to the hydraulic pressure of the hydraulic oil, and accordingly, the second valve body 56 faces the right from the first valve body 46. The shaft 28 is moved to the right by being applied with a force, and the shaft 28 is moved to the right by being applied with a rightward force from the second valve body 56. That is, the hydraulic pressure of the hydraulic oil acts on the first valve body 46, the second valve body 56, and the shaft 28, so that the first valve 44 is opened and the second valve 54 is closed. Hereinafter, this state is referred to as a second mode. The second mode is a mode in which the hydraulic oil flows in from the first flow path 60 and flows out from the second flow path 62. That is, the second mode is a mode for supplying the hydraulic oil discharged from the oil pump 161 to the intermediate lock mechanism 150.

  As shown in FIG. 4, in the state where the cylindrical coil 14 is energized as in the second mode, when hydraulic fluid flows from the second flow path 62, the first valve body 46 is moved to the left by the hydraulic pressure of the hydraulic fluid. The second valve body 56 moves rightward, and the shaft 28 is moved rightward by applying a rightward force from the second valve body 56. That is, the hydraulic pressure of the hydraulic oil acts on the first valve body 46, the second valve body 56, and the shaft 28, and both the first valve 44 and the second valve 54 are closed. Hereinafter, this state is referred to as a third mode. The third mode is a mode in which hydraulic oil does not flow out of the second flow path 62. That is, the third mode prevents the hydraulic pressure of the recess 152 from being lowered when the hydraulic pressure of the hydraulic oil that has flowed into the first flow path 60 in the second mode becomes lower than the hydraulic pressure acting on the recess 152. It is a mode for. The second mode and the third mode are automatically switched depending on the hydraulic pressure acting on the first flow path 60 and the hydraulic pressure acting on the second flow path 62. In the third mode, both the first valve 44 and the second valve 54 function as check valves.

  As described above, in the solenoid 1 with a check valve, when the cylindrical coil 14 is energized, the first hydraulic pressure of the hydraulic fluid in the first flow path 60 is higher than the hydraulic pressure in the second flow path 62. The hydraulic oil is supplied from the first flow path 60 toward the second flow path 62 because the valve 44 is in the open state and the second valve 54 is in the closed state. When the hydraulic pressure of the hydraulic fluid in the first flow path 60 is lower than the hydraulic pressure in the second flow path 62, both the first valve 44 and the second valve 54 are closed and function as a check valve. Since the mode is set, the hydraulic oil is restricted from flowing out of the second flow path 62. Therefore, while the energization to the cylindrical coil 14 is continued, the hydraulic pressure of the hydraulic oil once supplied to the second flow path 62 does not decrease.

  Therefore, when the solenoid 1 with a check valve is used in the valve opening / closing timing control device 100, once the hydraulic pressure of the hydraulic oil supplied to the intermediate lock mechanism 150 reaches the hydraulic pressure necessary for unlocking, the check valve is subsequently attached. Even when the oil pressure acting on the solenoid 1 fluctuates, the oil pressure acting on the recess 152 does not decrease because the first valve 44 and the second valve 54 function as check valves. As a result, even when the relative rotation phase is changed across the intermediate lock phase in the unlocked state, the relative rotation phase can be changed smoothly without being caught by the intermediate lock phase.

  In the present embodiment, the first valve body 46 and the second valve body 56 are common parts, but the present invention is not limited to this. The first valve body 46 and the second valve body 56 may be separate parts having different sizes. Further, the second valve body 56 need not be a sphere. Any shape that can open and close the second valve 54 and apply force to the first valve body 46 may be, for example, a hemisphere or an ellipsoid.

2. Second Embodiment A second embodiment of the present invention will be described in detail with reference to FIGS. In the solenoid 1 with a check valve of the present embodiment, the structure of the first valve 44 is different from that of the first embodiment, and the other structures are the same. Therefore, in the description of the present embodiment, the same reference numerals are given to the same components as those in the first embodiment, and the description regarding the same configurations is omitted.

  The first valve body 46 of this embodiment does not use a sphere. The first valve body 46 of the present embodiment includes a leaf valve 47, a spacer 46a, and a seat stopper 46b. As shown in FIG. 5, the first valve body 46 is disposed between the first valve seat 48 and the fixing ring 50.

  As shown in FIG. 8, the leaf valve 47 is formed by processing a thin metal disk having elasticity, and a gripping portion 47a formed on the entire periphery, and protrudes radially inward from the gripping portion 47a. The leaf spring portion 47b is formed in the circumferential direction, and the valve portion 47c is formed radially inward from the leaf spring portion 47b. The leaf valve 47 is fixed by the gripping portion 47a being sandwiched between the spacer 46a and the fixing ring 50. As shown in FIG. 6, the leaf spring portion 47b and the valve portion 47c receive the hydraulic oil pressure, and the shaft center 2 Along the direction of the sheet stopper 46b.

  The spacer 46a has a cylindrical shape, and the leaf spring portion 47b and the valve portion 47c move in the internal space. The thickness of the spacer 46a in the direction of the axis 2 corresponds to the amount of movement of the valve portion 47c. The seat stopper 46b is a disk-shaped metal part, and restricts the movement of the valve portion 47c when the valve portion 47c contacts the surface thereof. In the seat stopper 46b, four flow holes 46c are formed at positions corresponding to the radially outer side of the outer diameter of the valve portion 47c. The inner diameter of the fixed ring 50 of the present embodiment is smaller than the outer diameter of the valve portion 47c, preventing the valve portion 47c from moving toward the fixed ring 50, and the valve portion 47c abutting on the hydraulic oil. Is prevented from flowing from the second flow path 62 to the first flow path 60. In the first mode, the first valve seat 48 abuts on the second valve body 56 to restrict the movement of the second valve body 56.

  As shown in FIG. 5, in the first mode, the second valve body 56 comes into contact with the first valve seat 48 by the urging force of the spring 26, and the second valve 54 is opened. Since the second valve body 56 is in contact with the first valve seat 48, the first valve 44 is in a closed state because the hydraulic oil flowing in from the second flow path 62 does not flow into the first flow path 60. Even if a part of the hydraulic oil flows into the first flow path 60 through the flow hole 48 a, the hydraulic pressure acts from the right side to the left side of the leaf valve 47, so that the valve portion 47 c contacts the fixing ring 50. In contact with it, the hydraulic oil does not flow into the left side of the leaf valve 47. Accordingly, the hydraulic oil that has flowed into the second flow path 62 flows out from the third flow path 64.

  As shown in FIG. 6, in the second mode, the first valve 44 is opened due to the hydraulic pressure of the hydraulic oil flowing from the first flow path 60. Specifically, since the hydraulic pressure acts from the left side of the valve portion 47c, the valve portion 47c moves to the right side and comes into contact with the seat stopper 46b. The hydraulic oil flows into the first valve body 46 from the gap between the gripping portion 47a and the leaf spring portion 47b of the leaf valve 47, and flows into the second flow path 62 through the flow holes 46c and the flow holes 48c. Due to the hydraulic pressure of the hydraulic fluid flowing into the second flow path 62, the second valve body 56 contacts the second valve seat 58, and the second valve 54 is closed. Accordingly, the hydraulic oil that has flowed into the first flow path 60 flows out from the second flow path 62.

  As shown in FIG. 7, in the third mode, the second valve body 56 comes into contact with the second valve seat 58 and the second valve 54 is closed by the hydraulic pressure of the hydraulic oil flowing in from the second flow path 62. Become. Further, in the first valve body 46, the hydraulic oil reaches the leaf valve 47 through the circulation hole 48a and the circulation hole 46c. However, since the hydraulic pressure of the hydraulic oil acts from the right side to the left side of the leaf valve 47, the valve portion 47 c comes into contact with the fixing ring 50 and the hydraulic oil does not flow to the left side from the leaf valve 47. Is closed. Therefore, since both the first valve 44 and the second valve 54 are closed and function as a check valve, the hydraulic oil that has flowed into the second flow path 62 flows into the first flow path 60 and the third flow path 64. Will not leak.

  As described above, also in the solenoid 1 with a check valve according to the present embodiment, the second flow from the first flow path 60 is once performed while the cylindrical coil 14 is energized, as in the first embodiment. Since the first valve 44 and the second valve 54 function as check valves, the hydraulic oil supplied through the path 62 is restricted from flowing out of the second flow path 62 to the second flow path 62. The hydraulic pressure of the supplied hydraulic oil does not decrease. In addition, the first valve body 46 of the first embodiment is a sphere, whereas the first valve body 46 of the present embodiment uses the leaf valve 47, so the length in the direction of the axis 2 is shortened. Therefore, the size of the solenoid 1 with a check valve can be reduced.

3. Application to valve timing control device [Structure of valve timing control device]
Next, the operation when the solenoid 1 with a check valve according to the first and second embodiments is applied to the valve timing control apparatus 100 will be described in detail with reference to the drawings. As shown in FIG. 9, the valve timing control device 100 is disposed inside and coaxially with a housing 120 as a drive side rotating body that rotates synchronously with a crankshaft 101 of an engine 110 as an internal combustion engine, The camshaft 104 and an inner rotor 130 as a driven side rotating body that rotates synchronously are provided. The housing 120 and the inner rotor 130 are made of metal such as sintered or aluminum alloy. The camshaft 104 is a rotating shaft of a cam (not shown) that controls the opening and closing of the intake valve of the engine 110.

  The inner rotor 130 is integrally assembled with the tip portion of the camshaft 104. The camshaft 104 is rotatably assembled to a cylinder head (not shown) of the engine 110.

  In the housing 120, a front plate 121, a rear plate 123 integrally provided with a timing sprocket 123a, and an outer rotor 122 disposed therebetween are integrally formed by fastening screws or the like. The inner rotor 130 can move relative to the housing 120 within a certain range.

  A torsion spring 103 is provided around the camshaft 104 across the inner rotor 130 and the front plate 121. The housing 120 and the inner rotor 130 are biased by the biasing force of the torsion spring 103 so that the relative rotational phase is in the advance direction. The torsion spring 103 may be a torsion spring 103 that urges in the retarding direction based on the engine 110 on which the valve opening / closing timing control device 100 is mounted, or may be without the torsion spring 103.

  When the crankshaft 101 is rotationally driven, the rotational driving force is transmitted to the timing sprocket 123a via the power transmission member 102, and the housing 120 is rotationally driven in the relative rotational direction S shown in FIG. As the housing 120 is rotationally driven, the inner rotor 130 is rotationally driven in the relative rotational direction S to rotate the camshaft 104, and the cam provided on the camshaft 104 opens and closes the intake valve of the engine 110.

  As shown in FIG. 10, the outer rotor 122 is formed with four protrusions 124 protruding radially inward and spaced apart from each other along the relative rotational direction S, and the protrusion 124 and the inner rotor 130 form a fluid pressure chamber. 140 is formed. In the present embodiment, the number of fluid pressure chambers 140 is four, but the present invention is not limited to this.

  A vane groove 132 is formed in the outer peripheral portion of the inner rotor 130 facing each fluid pressure chamber 140, and the vane 131 is supported by the vane groove 132 so as to be slidable in the radial direction. The vane 131 is urged radially outward by a spring (not shown) provided on the inner diameter side thereof. The fluid pressure chamber 140 is partitioned into the advance chamber 141 and the retard chamber 142 along the relative rotation direction S by the vane 131. The advance chamber 141 and the retard chamber 142 are respectively connected to an advance channel 143 and a retard channel 144 formed in the inner rotor 130, and supply and discharge of hydraulic oil are performed through these channels. Is called. The advance channel 143 and the retard channel 144 are connected to a fluid supply / discharge mechanism 160 described later.

  The valve opening / closing timing control device 100 is provided with an intermediate lock mechanism 150 that restricts the relative rotational phase of the housing 120 and the inner rotor 130 to an intermediate lock phase that is a predetermined phase between the most advanced angle phase and the most retarded angle phase. Yes. The intermediate lock phase is a predetermined phase optimum for starting the internal combustion engine or a phase suitable for reducing exhaust gas within a range where the internal combustion engine can be started. The configuration of the intermediate lock mechanism 150 will be briefly described below. As shown in FIG. 10, the intermediate lock mechanism 150 is composed of two parts spaced apart in the circumferential direction by the same protrusion 124. That is, two lock member insertion portions 125, 125 formed in the outer rotor 122, plate-like lock members 151, 151 that are inserted into the lock member insertion portions 125, 125 and are movable inward in the radial direction, and the inner rotor 130 Consists of recesses 152, 152 that are formed and engageable with the lock members 151, 151, and biasing members 153, 153 such as coil springs that apply a biasing force that moves the lock members 151, 151 radially inward. Is done. As the shape of the lock members 151 and 151, a pin shape or the like can be appropriately adopted in addition to the plate shape shown in the present embodiment.

  Unlock flow paths 155 and 155 communicate with the recesses 152 and 152, respectively. The hydraulic oil is supplied and discharged through the unlocking flow paths 155 and 155. The unlocking channels 155 and 155 are connected to a fluid supply / discharge mechanism 160 described later.

  When the hydraulic oil is discharged from the recesses 152 and 152, when the lock members 151 and 151 and the recesses 152 and 152 face each other due to the relative rotation of the housing 120 and the inner rotor 130, the biasing force of the biasing members 153 and 153 The lock members 151 and 151 move radially inward and engage with the recesses 152 and 152. As a result, as shown in FIG. 10, the relative rotational phase of the housing 120 and the inner rotor 130 is constrained to the intermediate lock phase (hereinafter also referred to as “locking”).

  When hydraulic oil is supplied to the recesses 152 and 152 via the lock release channels 155 and 155 in the locked state, the end surfaces of the lock members 151 and 151 receive fluid pressure of the hydraulic oil. When the fluid pressure received by the end surface exceeds the urging force of the urging members 153 and 153, the lock members 151 and 151 are retracted from the recesses 152 and 152, and the restraint is released (hereinafter also referred to as “the locked state is released”). ), The unlocked state in which the relative rotational phase can be changed as shown in FIG.

  The configuration of the fluid supply / discharge mechanism 160 will be briefly described. As shown in FIG. 9, the fluid supply / discharge mechanism 160 is driven by the engine 110 to supply hydraulic oil to the hydraulic pump 161, and supply and discharge of hydraulic oil to the advance flow path 143 and the retard flow path 144. An OCV (oil control valve) 162 to be controlled, an OSV (oil switching valve) that switches between supply and discharge of hydraulic oil to the intermediate lock mechanism 150, and a fluid pressure sensor that detects the pressure of hydraulic oil discharged from the oil pump 161 164, an oil pan 165 for storing hydraulic oil. In the valve timing control apparatus 100, the solenoid 1 with a check valve is used as the OSV.

  The oil pump 161 is a mechanical pump that is driven when the rotational driving force of the crankshaft 101 is transmitted. The oil pump 161 sucks the hydraulic oil stored in the oil pan 165 and discharges the hydraulic oil toward the OCV 162 or the solenoid 1 with a check valve on the downstream side.

  The OCV 162 is provided between the oil pump 161 and the advance chamber 141 and the retard chamber 142. The OCV 162 operates by changing the position of the internal spool valve based on the control of the energization amount by an ECU (Engine Control Unit) 170 which is a control unit. That is, advance control for supplying hydraulic oil to the advance chamber 141 and discharging hydraulic oil from the retard chamber 142, and retarding to discharge hydraulic oil from the advance chamber 141 and supply hydraulic oil to the retard chamber 142. Three types of operations are executed: control and control for cutting off hydraulic oil supply / discharge to the advance chamber 141 and the retard chamber 142.

  In the present embodiment, a hydraulic fluid path capable of advance control is formed when the energization amount to the OCV 162 is maximum, and the volume of the advance chamber 141 is increased by supplying the hydraulic fluid, so that the The relative rotational phase of the inner rotor 130 is displaced in the advance direction (S1 direction). A hydraulic fluid path capable of retarding control is formed when the energization is interrupted, and the volume of the retarding chamber 142 is increased by supplying hydraulic fluid, so that the relative rotation phase is retarded (S2 direction). Displace.

  The solenoid 1 with a check valve is provided on the unlocking flow path 155 between the oil pump 161 and the recesses 152 and 152 and in parallel with the OCV 162. Specifically, the first flow path 60 is connected so that the hydraulic oil discharged from the oil pump 161 flows in, and the second flow path 62 is connected so that the second release flow path 62c communicates with the recesses 152 and 152. The third flow path 64 is connected such that the third release flow path 64c discharges hydraulic oil toward the oil pan 165. Details of the operation of the solenoid 1 with a check valve in the valve timing control apparatus 100 will be described later.

  The fluid pressure sensor 164 is disposed on the downstream side of the discharge port of the oil pump 161 and on the upstream side of the branch point where the hydraulic oil flow path branches into the OCV 162 and the solenoid 1 with a check valve. The fluid pressure sensor 164 detects the pressure value of the hydraulic oil discharged from the oil pump 161 in real time, and transmits a pressure value signal to the ECU 170.

[Operation of valve timing control device]
Next, operation | movement of the solenoid 1 with a non-return valve in the valve timing control apparatus 100 is demonstrated using drawing. In a state where the engine 110 is stopped at a low temperature, the hydraulic oil is discharged from the advance chamber 141 and the retard chamber 142. Further, since the solenoid 1 with a check valve is not energized, it enters the first mode, the hydraulic oil is discharged from the recesses 152, 152, and the intermediate lock mechanism 150 is in the locked state. In this state, when the ignition switch is turned on and the engine 110 is started to enter an idling state, the ECU 170 controls the OCV 162 to be switched to advance angle control by 100% energization, and enters the advance angle chamber 141. Hydraulic oil is supplied. The solenoid 1 with a check valve is controlled to maintain the first mode, and is not energized. This state is shown in FIG.

  When the idling operation of the engine 110 is completed and the driver depresses the accelerator to start and accelerate the vehicle, the ECU 170 performs control for releasing the lock of the intermediate lock mechanism 150 in order to change the relative rotation phase to the advance side. Do. In the solenoid 1 with a check valve, the cylindrical coil 14 is energized and switched to the second mode. Then, hydraulic oil is supplied from the oil pump 161 to the first flow path 60, and is supplied from the second flow path 62 to the recesses 152 and 152 through the lock release flow paths 155 and 155. When the hydraulic pressure in the recesses 152 and 152 rises and exceeds the biasing force of the biasing members 153 and 153, the lock members 151 and 151 are separated from the recesses 152 and 152, and the lock is released. At this time, the supply of hydraulic oil to the advance chamber 141 has already been completed, and the hydraulic pressure of the hydraulic oil supplied to the solenoid 1 with a check valve is stable. Absent. Even if the hydraulic pressure of the hydraulic oil supplied to the solenoid 1 with check valve fluctuates and the hydraulic pressure of the hydraulic oil supplied to the recesses 152 and 152 may decrease, the solenoid 1 with check valve is in the third mode. And the hydraulic oil is prevented from being discharged from the recesses 152 and 152 through the lock release passages 155 and 155. Therefore, the oil pressure in the recesses 152 and 152 rises without decreasing, and the unlocked state is realized smoothly. This state is shown in FIG.

  When the vehicle is in a steady running state, the ECU 170 conducts advance angle control for supplying the hydraulic oil to the advance chamber 141 by energizing the OCV 162 according to the load, rotation speed, etc. of the engine 110 during operation. The retard control is performed to shut off and supply hydraulic oil to the retard chamber 142. As a result, the relative rotational phase is displaced to the advance side or the retard side from the intermediate lock phase. In addition, the energization to the OCV 162 is controlled to about 50% to keep the relative rotational phase at an arbitrary phase. Normally, the solenoid 1 with a check valve is maintained in the second mode in the steady running state.

  As described above, when the advance angle control and the retard angle control are repeated, the hydraulic pressure of the hydraulic oil in the advance chamber 141 and the retard chamber 142 always fluctuates. The hydraulic pressure of the hydraulic oil in the first flow path 60 varies. As a result, the hydraulic pressure in the first flow path 60 may be lower than the hydraulic pressure in the second flow path 62 and the unlocking flow paths 155 and 155, that is, the hydraulic pressure acting on the recesses 152 and 152. However, since the valve opening / closing timing control device 100 uses the solenoid 1 with a check valve, even if the hydraulic pressure in the first flow path 60 is lower than the hydraulic pressure in the second flow path 62, the solenoid with check valve is used. 1 is switched from the second mode to the third mode, and the hydraulic oil supplied to the second flow path 62 is prevented from being discharged. When the hydraulic pressure in the first flow path 60 exceeds the hydraulic pressure in the second flow path 62, the solenoid 1 with a check valve automatically switches from the third mode to the second mode. Therefore, even if the hydraulic pressure in the first flow path 60 fluctuates and falls below the hydraulic pressure in the second flow path 62, the hydraulic pressure of the hydraulic oil supplied to the second flow path 62, that is, the recesses 152 and 152 does not decrease. The hydraulic pressure can be maintained as long as the unlocked state is always maintained. As a result, as shown in FIG. 13, even when the relative rotation phase is changed across the intermediate lock phase in the unlocked state, unlike the case shown in FIG. 12, the catch at the intermediate lock phase occurs. Without changing the relative rotational phase smoothly.

  The present invention can be used in a solenoid with a check valve and a valve opening / closing timing control device using the solenoid.

1 Solenoid with check valve 10 Solenoid (drive mechanism)
26 Spring 42 Body 44 1st valve 46 1st valve body 46a Spacer 46b Seat stopper 47 Leaf valve 54 2nd valve 56 2nd valve body 60 1st flow path 62 2nd flow path 64 3rd flow path 101 Crankshaft 104 Cam Shaft 110 engine (internal combustion engine)
120 Housing (Drive-side rotating body)
130 Inner rotor (driven rotor)
150 Intermediate lock mechanism 151 Lock member 152 Recess 155 Lock release flow path 161 Oil pump

Claims (5)

Body,
A first channel formed in the body, having one end open to the outside of the body and the other end inside the body;
A second flow path formed in the body, having one end open to the outside of the body and the other end being inside the body and communicating with the first flow path;
A third channel formed in the body, having one end open to the outside of the body and the other end being inside the body and communicating with the second channel;
A drive mechanism driven by electromagnetic force generated by energization and biasing force of the spring;
A first valve that moves so that the first flow path and the second flow path are selectively communicated or blocked according to the electromagnetic force and the biasing force of the spring;
A second valve that moves so that the second flow path and the third flow path are selectively communicated or blocked according to the electromagnetic force and the biasing force of the spring,
When the drive mechanism is de-energized, the second valve moves so that the second flow path and the third flow path communicate with each other, so that hydraulic oil flows from the second flow path to the third flow path. Circulate,
When the drive mechanism is energized and when the hydraulic pressure of the hydraulic oil in the first flow path is higher than the hydraulic pressure in the second flow path, the first valve and the second flow path communicate with each other. The hydraulic fluid flows from the first flow path to the second flow path,
Between the first flow path, the second flow path, and the third flow path when the drive mechanism is energized and the hydraulic pressure of the hydraulic oil in the second flow path is higher than the hydraulic pressure in the first flow path. When both the first valve and the second valve move so that the flow of the oil is blocked, the working oil flows from the second flow path to both the first flow path and the third flow path. Solenoid with check valve that is regulated.   When the drive mechanism is de-energized, the second valve body of the second valve contacts the first valve body of the first valve to transmit the biasing force, so that the first valve moves and the first valve body moves. The solenoid with a check valve according to claim 1, wherein one flow path and the second flow path are blocked.   The solenoid with a check valve according to claim 1 or 2, wherein the first valve body and the second valve body are spherical bodies having the same size.   The first valve body includes a leaf valve, a seat stopper that regulates a movement amount of the leaf valve, and a spacer that makes a movement amount of the leaf valve and the stopper constant, and the first valve body 2. The solenoid with a check valve according to claim 1, wherein the solenoid moves in accordance with hydraulic pressure of hydraulic oil acting on the leaf valve. A drive-side rotating body that rotates synchronously with the crankshaft of the internal combustion engine;
A driven-side rotator that is disposed so as to have the same axis as the drive-side rotator, and rotates synchronously with a valve shaft of the internal combustion engine;
A lock member that is accommodated in one of the rotating bodies of the driving side or the driven side rotating body and is movable with respect to the other rotating body of the driving side rotating body or the driven side rotating body; A recess formed in the other rotating body so that the lock member can be fitted when the lock member is moved, and the drive member rotates when the lock member moves and fits into the recess. The locked state in which the relative rotational phase of the driven rotor relative to the body is constrained to an intermediate lock phase between the most advanced angle phase and the most retarded angle phase, and the constraint is released by separating the lock member from the recess. An intermediate locking mechanism that can selectively switch between unlocking states,
A lock release passage that is communicated with the recess and through which hydraulic oil supplied to and discharged from the recess flows.
An oil pump for supplying hydraulic oil to the unlocking flow path;
A solenoid with a check valve according to claim 1, wherein the solenoid is mounted on the unlocking channel so that the first channel communicates with the oil pump and the second channel communicates with the recess. Provided valve opening / closing timing control device.

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