JP6402682B2 - Control unit - Google Patents

Description

The present invention relates to a control unit .

  2. Description of the Related Art Conventionally, there is known a valve timing adjusting device that adjusts the opening / closing timing of at least one of an intake valve and an exhaust valve by oil pressure of oil supplied by a hydraulic control valve. A valve timing adjusting device includes a hydraulic control valve having a sleeve and a spool, a valve timing adjusting unit having an advance chamber and a retard chamber into which oil supplied by the hydraulic control valve flows in or out, an electromagnetic actuator that drives the spool, and an electromagnetic actuator It is comprised from the control part etc. which supply with electricity. For example, Patent Document 1 describes a valve timing adjusting device that includes a control unit that energizes an electromagnetic actuator so that a spool reciprocates when the valve timing does not change, and removes foreign matter between the sleeve and the spool. .

JP 2001-234768 A

  The electromagnetic actuator provided in the valve timing adjusting device described in Patent Document 1 has a housing in which a fixed core, a movable core, a coil, a rod connected to a spool, a fixed core, and the like are accommodated and the rod is inserted. The insertion hole of the housing through which the rod is inserted is provided to face the hydraulic control valve. For this reason, the relatively high temperature oil discharged from the hydraulic control valve is applied to the electromagnetic actuator. The oil applied to the electromagnetic actuator enters the housing through the gap between the insertion hole and the rod. Since the oil that has entered the housing increases in viscosity when the temperature of the oil itself decreases, for example, when the engine is restarted under low temperature conditions after the engine stops, the movable core moves to adjust the valve timing. Resistance. For this reason, the responsiveness of the valve timing immediately after engine startup may be deteriorated.

The objective of this invention is providing the control part which improves the responsiveness of valve timing .

The control unit of the present invention is provided opposite to a hydraulic control valve that supplies oil to a valve timing adjustment unit that can adjust the opening / closing timing of an intake valve or an exhaust valve of an engine, and is electrically connected to an electromagnetic actuator that drives the hydraulic control valve. Connected. Electromagnetic actuator comprises a fixed core, a movable core, coil, rod, and Haujin grayed.
The movable core is movable relative to the fixed core.
When energized, the coil forms a magnetic field that passes through the fixed core and the movable core.
Rods, Ru Tei provided to be reciprocated integrally with the movable core.
The housing includes a core chamber that movably accommodates the movable core, and an insertion hole that communicates with the core chamber and through which the rod is inserted.
The control unit is electrically connected to the coil and energizes the coil so that the movable core reciprocates after the engine stops.

In this onset bright, the control unit after the engine is stopped, to energize the coil so that the movable core reciprocates core chamber.
In the first aspect of the present invention, the control unit energizes the coil so that the oil in the valve timing adjusting unit is discharged after the engine stops and before the movable core reciprocates.
In the second aspect of the present invention, after the engine is stopped, the control unit energizes the coil so as to discharge a certain amount of oil in the valve timing adjustment unit and then discharge the remaining oil in the valve timing adjustment unit.
In the third aspect of the present invention, the control unit energizes the coil so that a certain amount of oil in the valve timing adjusting unit is discharged after the engine stops and before the movable core reciprocates.
In the fourth aspect of the present invention, the control unit energizes the coil such that the moving core moves faster toward the hydraulic control valve than the moving core moves away from the hydraulic control valve.
When the magnetic attraction force is generated between the fixed core and the movable core by energizing the coil and the movable core moves through the core chamber, the air in the core chamber is pushed out of the core chamber through the insertion hole. At this time, the oil contained in the air in the core chamber is discharged to the outside of the core chamber together with the air. Accordingly, since the viscosity increases as the temperature decreases, the oil in the core chamber that becomes a resistance when the movable core moves can be surely removed from the core chamber. Therefore, since the movable core can be smoothly moved even when the engine is restarted under a low temperature condition, the responsiveness of the valve timing can be improved.

It is a mimetic diagram of a valve timing adjustment device provided with an electromagnetic actuator by a first embodiment of the present invention. It is a flowchart of the oil discharge process of the electromagnetic actuator by 1st embodiment of this invention. It is a characteristic view of the oil discharge process in the electromagnetic actuator by 1st embodiment of this invention. It is a fragmentary sectional view of the electromagnetic actuator by a first embodiment of the present invention. It is a characteristic view of the oil discharge process in the electromagnetic actuator by 2nd embodiment of this invention. It is a flowchart of the oil discharge process of the electromagnetic actuator by 3rd embodiment of this invention. It is a characteristic view of the oil discharge process in the electromagnetic actuator by 3rd embodiment of this invention. It is a flowchart of the oil discharge process of the electromagnetic actuator by 4th embodiment of this invention. It is a characteristic view of the oil discharge process in the electromagnetic actuator by 4th embodiment of this invention. It is a flowchart of the oil discharge process of the electromagnetic actuator by 5th embodiment of this invention. It is a characteristic view of the oil discharge process in the electromagnetic actuator by 5th embodiment of this invention. It is a schematic diagram of the valve timing adjustment apparatus provided with the electromagnetic actuator by 6th embodiment of this invention. It is a characteristic view of the oil discharge process in the electromagnetic actuator by 6th embodiment of this invention. It is a fragmentary sectional view of the electromagnetic actuator by 6th embodiment of this invention.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
The electromagnetic actuator by 1st embodiment of this invention is demonstrated based on FIGS. The electromagnetic actuator 10 according to the first embodiment is provided in the valve timing adjusting device 1 shown in FIG. In addition to the electromagnetic actuator 10, the valve timing adjustment device 1 includes a valve timing adjustment unit 20, a hydraulic control valve 30, and the like. The valve timing adjusting device 1 controls the relative rotation phase of the camshaft 3 with respect to the crankshaft 9 by oil supplied through the hydraulic control valve 30 while rotating with the crankshaft 9 and the camshaft 3.

First, the configuration of the electromagnetic actuator 10 will be described.
The electromagnetic actuator 10 is provided so as to face the hydraulic control valve 30 fixed to the center of rotation of the valve timing adjusting unit 20. The electromagnetic actuator 10 drives the hydraulic control valve 30. The electromagnetic actuator 10 includes a coil 11, a fixed core 12, a movable core 13, a rod 14, a yoke 15, a housing 16, a control unit 17, and the like.

  The coil 11 is formed of a bobbin and a winding wound around the bobbin. Electric power is supplied to the winding via a terminal 172 of a connector 171 provided in the housing 16.

  The fixed core 12 is made of a magnetic material. The fixed core 12 is opposite to the first cylinder part 121 and the second cylinder part 122 provided inside the coil 11, the flange part 123 provided on the hydraulic control valve 30 side of the coil 11, and the hydraulic control valve 30 of the movable core 13. A rod support portion 124 that supports the rod 14 so as to be reciprocally movable on the side, a first cylinder portion 121, a non-magnetic member 125 provided between the second cylinder portion 122 and the coil 11, and the like. A core chamber 120 in which the movable core 13 is accommodated is formed inside the first cylinder part 121 and the second cylinder part 122.

  The second cylindrical portion 122 side of the first cylindrical portion 121 and the first cylindrical portion 121 side of the second cylindrical portion 122 are formed so that the end portions are narrowed. A gap 126 is formed between the end portion of the first tube portion 121 on the second tube portion 122 side and the end portion of the second tube portion 122 on the first tube portion 121 side.

The movable core 13 is formed of a magnetic material. The movable core 13 is accommodated in the core chamber 120 so as to be reciprocally movable in the axial direction. The movable core 13 has an insertion hole 131 through which the rod 14 is inserted.
The movable core 13 has an air hole 132 that communicates the core chamber 120 on the hydraulic control valve 30 side of the movable core 13 with the core chamber 120 on the opposite side of the hydraulic control valve 30. In the air hole 132, for example, when the movable core 13 moves to the hydraulic control valve 30 side from the state of FIG. 1, the air in the core chamber 120 on the hydraulic control valve 30 side of the movable core 13 is opposite to the hydraulic control valve 30. It flows toward the core chamber 120 on the side. Further, when the movable core 13 moves from the hydraulic control valve 30 side to the side opposite to the hydraulic control valve 30, the air in the core chamber 120 on the side opposite to the hydraulic control valve 30 of the movable core 13 is on the hydraulic control valve 30 side. It flows toward the core chamber 120.

  The rod 14 is fixed to the movable core 13 and is provided so as to be reciprocally movable in the axial direction integrally with the movable core 13. The rod 14 can press the spool 32 of the hydraulic control valve 30.

The yoke 15 is made of a magnetic material and has a bottomed cylindrical shape. The yoke 15 has a bottom portion 151 and a cylindrical portion 152.
The bottom 151 is provided so as to cover the opposite side of the coil 11 from the hydraulic control valve 30. The cylindrical portion 152 is formed so as to extend in a cylindrical shape from the outer edge of the bottom portion 151 toward the hydraulic control valve 30 side. The end of the cylindrical portion 152 is connected to the outer edge of the flange portion 123. The yoke 15 forms a magnetic circuit together with the fixed core 12 and the movable core 13.

The housing 16 accommodates the coil 11, the fixed core 12, the movable core 13, the rod 14, the yoke 15, and the like. The housing 16 has a molded body 161 and a lid 162.
The molded body 161 is resin-molded on the outside of the yoke 15 and a part of the coil 11.

The lid part 162 is formed integrally with the first cylinder part 121 and the flange part 123. The lid portion 162 is provided at a position facing one end portion 314 of the hydraulic control valve 30 so as to close the hydraulic control valve 30 side of the core chamber 120. The lid 162 has an insertion hole 163 and a communication path 164. The rod 14 is inserted through the insertion hole 163. Thereby, the rod 14 is supported by the cover part 162 and the rod support part 124 so that a reciprocation is possible. The communication path 164 communicates the core chamber 120 and the atmosphere. When the movable core 13 reciprocates through the core chamber 120, the communication path 164 can discharge the air in the core chamber 120 to the atmosphere, or can suck air from the atmosphere into the core chamber 120.
The housing 16 can be attached to the engine cover 5 with a bolt (not shown) inserted through the bolt hole 165.

  The control unit 17 is electrically connected to the coil 11 via the connector 171. The control unit 17 is electrically connected to a crank angle sensor 90 that detects the rotation angle of the crankshaft 9. The controller 17 controls the operation of the hydraulic control valve 30 by adjusting the duty ratio of the current flowing through the coil 11. Specifically, when the control unit 17 energizes the coil 11, a magnetic field passing through the fixed core 12, the movable core 13, and the yoke 15 is formed, and a magnetic circuit is configured. At this time, since the magnetic resistance between the first cylinder part 121 and the second cylinder part 122 forming the gap 126 is large, a magnetic attractive force is generated between the first cylinder part 121 and the movable core 13. . Thereby, the movable core 13 is magnetically attracted to the first cylindrical portion 121, and the rod 14 fixed to the movable core 13 presses the spool 32 of the hydraulic control valve 30. The control unit 17 can control the magnitude of the pressing force acting on the spool 32 according to the current duty ratio.

  The valve timing adjustment unit 20 switches the relative rotation phase of the camshaft 3 with respect to the crankshaft 9 while transmitting the rotation of the crankshaft 9 of the engine (not shown) to the camshaft 3 that drives the intake valve or the exhaust valve. The valve timing adjustment unit 20 includes a housing 21, a front cover 22, a vane rotor 23, and an intermediate lock member 24.

  The housing 21 includes a front plate 211, a rear plate 212, a peripheral wall 213, and the like. In the housing 21, a chain (not shown) is wound around a gear 214 provided on the peripheral wall 213 and is connected to the crankshaft 9 to rotate.

The front cover 22 is provided on the electromagnetic actuator side of the front plate 211. The front cover 22 has a disc portion 221 and a recess 222.
The disc part 221 is provided in parallel with the flange part 123 and the lid part 162 of the electromagnetic actuator 10.
The recess 222 is formed so as to be recessed from the approximate center of the disc portion 221 to the camshaft 3 side. One end 314 of the sleeve 31 of the hydraulic control valve 30 is provided in the recess 222. When the male screw 315 provided on the side opposite to the one end 314 of the sleeve 31 is screwed into the female screw 4 provided on the camshaft 3, the sleeve 31, the front cover 22, the vane rotor 23, and the camshaft 3 are fixed. The

  The vane rotor 23 is accommodated inside the housing 21. The vane rotor 23 is fixed to the end of the camshaft 3 and rotates integrally with the camshaft 3. The vane rotor 23 divides the interior of the housing 21 into an advance angle chamber and a retard angle chamber (not shown). The vane rotor 23 rotates relative to the housing 21 in the advance direction or the retard direction by the hydraulic pressure supplied to the advance chamber or the retard chamber. Thereby, the valve timing adjusting unit 20 can switch the relative rotation phase of the camshaft 3 with respect to the crankshaft 9.

  The intermediate lock member 24 is accommodated in the accommodation hole 231 of the vane rotor 23. The intermediate lock member 24 is formed so as to be fitted in a fitting hole 215 formed in the inner wall of the rear plate 212. The intermediate lock member 24 reciprocates in the accommodation hole 231 in accordance with the pressure of the oil supplied by the hydraulic control valve 30 to release the fitting hole 215 from the fitting or the fitting hole 215. When the intermediate lock member 24 is fitted into the fitting hole 215, the relative rotation phase of the vane rotor 23 with respect to the housing 21 is fixed to a predetermined phase. Thereby, the relative rotational phase of the crankshaft 9 and the camshaft 3 can be fixed to a predetermined phase.

  The hydraulic control valve 30 is fixed to the rotation center of the valve timing adjustment unit 20. The hydraulic control valve 30 includes a sleeve 31, a spool 32, a spring 33, and the like. The hydraulic control valve 30 can switch the hydraulic pressure supplied to the advance chamber or the retard chamber of the valve timing adjustment unit 20.

  The sleeve 31 is a cylindrical part. The sleeve 31 has a plurality of hydraulic ports 311, 312, 313 in the radial direction. The plurality of hydraulic ports 311, 312, and 313 communicate with the advance chamber, the retard chamber, and the hydraulic supply oil passage 232 of the valve timing adjustment unit 20.

  The spool 32 is provided inside the sleeve 31 so as to be able to reciprocate. The spool 32 has oil passages 321, 322, and 323 on a radially outer wall. The oil passages 321, 322, and 323 correspond to the hydraulic ports 311, 312, and 313. The spool 32 has a discharge oil passage 324 extending in the axial direction. The drain oil passage 324 communicates with oil drain ports 300 and 325 located at both ends of the sleeve 31 in the axial direction.

  The spring 33 is provided at the end of the spool 32 opposite to the electromagnetic actuator 10. The spring 33 biases the spool 32 toward the electromagnetic actuator 10 side.

Next, the operation of the valve timing adjusting device 1 will be described.
The oil pumped up from the engine oil pan 6 by the oil pump 7 is supplied from the oil passage 8 of the camshaft 3 to the hydraulic control valve 30 through the hydraulic supply oil passage 232 of the valve timing adjusting unit 20. In the hydraulic control valve 30, the position of the spool 32 with respect to the sleeve 31 is determined when the pressing force applied to the spool 32 by the electromagnetic actuator 10 and the elastic force applied to the spool 32 by the spring 33 are balanced. The positional relationship between the hydraulic ports 311, 312, 313 and the oil passages 321, 322, 323 is determined by the position of the spool 32 with respect to the sleeve 31, and oil is supplied to one of the advance chamber and the retard chamber.

  Further, when the hydraulic control valve 30 supplies oil to one of the advance chamber or the retard chamber, the oil stored in the other of the advance chamber or the retard chamber passes through the hydraulic ports 311 and 313, and the oil It is discharged from the discharge port 300. Most of the oil discharged from the oil discharge port 300 flows between the flange portion 123 and the lid portion 162 and the disc portion 221 and returns to the oil pan 6, but one part of the oil discharged from the oil discharge port 300. The part enters the core chamber 120 via a gap between the insertion hole 163 and the rod 14.

  In the first embodiment, the electromagnetic actuator 10 executes an oil discharge process for discharging the oil in the core chamber 120 to the outside after the engine is stopped. Here, the oil discharge process in the electromagnetic actuator 10 will be described with reference to FIGS. FIG. 3A is a characteristic diagram showing a change over time in the engine speed in the oil discharge process of the first embodiment, and FIG. 3B is a diagram of the oil discharge process of the first embodiment. It is a characteristic view which shows the time change of the duty ratio of the electric current which flows through the coil 11 of.

  First, in step (hereinafter simply referred to as “S”) 101, the ignition is turned OFF. When the ignition is turned off at time t10 in FIG. 3, the engine stops at time t11. The control unit 17 determines that the engine is stopped based on the detection result output from the crank angle sensor 90.

  After the engine is stopped, the reciprocating control of the movable core 13 is performed in S102. In S102, as shown from time t12 to time t15 in FIG. 3, the duty ratio of the current flowing through the coil 11 is changed in a pulse shape. Specifically, the duty ratio is increased from 0% to 100% between time t12 and time t13. Next, the duty ratio is decreased from 100% to 0% between time t13 and time t14. In the first embodiment, as shown in FIG. 3B, the control unit 17 energizes the coil 11 to repeat the change in current from time t12 to time t14 a plurality of times.

The operation and effect of the reciprocation control of the movable core 13 in S102 will be described with reference to FIG. FIG. 4A shows the state of the electromagnetic actuator 10 in a state where a current having a duty ratio of 0%, that is, no current flows through the coil 11. FIG. 4B shows a state of the electromagnetic actuator 10 in a state where a current having a duty ratio of 100% flows through the coil 11.
When the ignition is turned off in S101 and the engine is stopped, the movable core 13 is at a position farthest from the lid 162 as shown in FIG. At this time, the oil contained in the core chamber 120 accumulates on the inner wall on the ground side in the direction of gravity, for example, on the inner wall of the first cylindrical portion 121 in FIG. 4 or between the movable core 13 and the lid portion 162. The core chamber 120 may float in a form contained in air. Therefore, when the duty ratio of the current flowing through the coil 11 is set to 100% in S102, the movable core 13 comes closest to the lid 162 as shown in FIG. When the movable core 13 approaches the lid portion 162, the oil accumulated on the inner wall of the first cylindrical portion 121 is pushed out of the electromagnetic actuator 10 from the communication path 164 as indicated by a solid arrow F <b> 11 in FIG. It is. Further, since the volume of the core chamber 120 between the movable core 13 and the lid portion 162 is reduced, the oil floating in the core chamber 120 between the movable core 13 and the lid portion 162 in a form contained in air is 4B, the air is discharged from the gap between the insertion hole 163 and the rod 14 to the outside of the electromagnetic actuator 10 along with air.
When S102 ends, the current oil discharge process ends.

  (A) In the electromagnetic actuator 10 according to the first embodiment, the controller 17 energizes the coil 11 so that the movable core 13 reciprocates in the core chamber 120 after the engine stops. When the movable core 13 reciprocates in the core chamber 120, gaseous oil contained in the air in the core chamber 120 is discharged to the outside of the core chamber 120 together with the air. Further, the liquid oil accumulated on the inner wall of the first cylindrical portion 121 is pushed out of the core chamber 120 by the movable core 13. As a result, the oil contained in the core chamber 120 can be reliably removed from the core chamber 120, so that the movable core 13 can be moved smoothly without being affected by the viscosity of the oil even when the engine is restarted under low temperature conditions. be able to. Therefore, the responsiveness of the valve timing immediately after engine startup can be improved.

  (B) Moreover, in the electromagnetic actuator 10, the duty ratio of the electric current which flows through the coil 11 is changed in multiple times. Thereby, a large amount of oil that cannot be discharged by one reciprocating movement of the movable core 13 can be reliably discharged to the outside.

(Second embodiment)
Next, an electromagnetic actuator according to a second embodiment of the present invention will be described with reference to FIG. The second embodiment is different from the first embodiment in the method of oil discharge processing in the electromagnetic actuator after the engine is stopped. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

  FIG. 5 shows a characteristic diagram of oil discharge processing in the electromagnetic actuator according to the second embodiment. FIG. 5A is a characteristic diagram showing the change over time in the engine speed in the oil discharge process of the second embodiment, and FIG. 5B is the oil discharge process of the second embodiment. It is a characteristic view which shows the time change of the duty ratio of the electric current which flows through the coil 11 of.

  In the oil discharge process of the second embodiment, after turning off the ignition at time t20 in FIG. 5 and stopping the engine at time t21, the duty ratio of the current flowing through the coil 11 is pulsed as shown from time t22 to time t25. Change the shape. Specifically, the duty ratio is increased from 0% to 100% between time t22 and time t23. After increasing the duty ratio, the duty ratio is decreased from 100% to 0% between time t23 and time t24. At this time, the control unit 17 controls energization of the coil 11 so that the time from time t22 to time t23 is shorter than the time from time t23 to time t24.

In the electromagnetic actuator according to the second embodiment, when the current having the current waveform shown in FIG. 5B is passed through the coil 11, the movable core 13 is relatively moved from the state in contact with the rod support portion 124 to the lid portion 162. Approach at high speed. Thereby, the movable core 13 can push out the air containing the oil between the movable core 13 and the cover part 162 to the outside of the electromagnetic actuator 10 relatively quickly.
On the other hand, the movable core 13 moves away from the lid portion 162 at a relatively low speed after approaching the lid portion 162 most closely. Thereby, it is possible to prevent the core chamber 120 that becomes negative pressure when the movable core 13 moves away from the lid portion 162 from sucking air that may contain oil outside the electromagnetic actuator 10 more than necessary.
As described above, in the electromagnetic actuator according to the second embodiment, the air containing the oil in the core chamber 120 is pushed out to the outside quickly, while the movable core is not sucked into the core chamber 120 more than necessary. 13 reciprocating movements are controlled. Thereby, 2nd embodiment can prevent attraction | suction of a new oil as effect (c) of 2nd embodiment while having effect (a), (b) of 1st embodiment.

(Third embodiment)
Next, an electromagnetic actuator according to a third embodiment of the present invention will be described with reference to FIGS. The third embodiment differs from the first embodiment in the method of oil discharge processing in the electromagnetic actuator after the engine is stopped. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

  FIG. 6 shows a flowchart of the oil discharge process in the electromagnetic actuator according to the third embodiment. FIG. 7 shows a characteristic diagram of oil discharge processing in the electromagnetic actuator according to the third embodiment. FIG. 7A is a characteristic diagram showing a change over time in the engine speed in the oil discharge process of the third embodiment. FIG. 7B is a characteristic diagram showing a change over time of the hydraulic pressure in the valve timing adjusting unit 20 in the oil discharge process of the third embodiment. FIG.7 (c) is a characteristic view which shows the time change of the duty ratio of the electric current which flows through the coil 11 in the discharge process of the oil of 3rd embodiment.

  In the oil discharge process of the third embodiment, first, in S301, the ignition is turned OFF as in S101 of the first embodiment. When the ignition is turned off at time t30 in FIG. 6, the engine stops at time t31.

  Next, in S302, residual pressure removal control for discharging oil remaining in the valve timing adjusting unit 20 is performed. When the engine is stopped, the oil used for adjusting the valve timing remains in the advance chamber and the retard chamber. As shown in FIG. 7C, the control unit 17 energizes the coil 11 from time t32 to time t33 to reciprocate the spool 32 within the sleeve 31. At this time, the control unit 17 causes a current having a duty ratio of 100% to flow through the coil 11. Thereby, the oil remaining in the advance chamber and the retard chamber is discharged from the oil discharge port 300, and the hydraulic pressure in the valve timing adjusting unit 20 becomes 0 (see FIG. 7B).

  Next, in S303, similarly to S102 of the first embodiment, the reciprocating movement control of the movable core 13 is performed (between time t34 and time t35 in FIG. 7). Thereby, the air containing the oil in the core chamber 120 is discharged from the core chamber 120.

When the movable core 13 reciprocates after the engine stops as in the first embodiment, if oil remains in the valve timing adjustment unit 20, the valve timing adjustment is performed by the reciprocation of the spool 32 connected to the movable core 13. Oil is discharged from the oil discharge port 300 to the outside in the section 20 and the hydraulic control valve 30. Oil discharged from the oil discharge port 300 may be newly sucked into the core chamber 120 together with air.
Therefore, in the electromagnetic actuator according to the third embodiment, the control unit 17 first energizes the coil 11 with a current having a duty ratio of 100% so that the hydraulic pressure in the valve timing adjustment unit 20 becomes 0 after the engine is stopped. Next, the movable core 13 is reciprocated to discharge the air containing the oil in the core chamber 120. Thereby, it is possible to reliably prevent the air containing oil from being newly sucked by the reciprocating movement of the movable core 13 for discharging the air containing oil in the core chamber 120. Therefore, the fourth embodiment can achieve the effects (a) and (b) of the first embodiment and the effect (c) of the second embodiment.

  In the third embodiment, the oil pressure in the valve timing adjusting unit 20 is set to 0, so that the oil remaining in the valve timing adjusting unit 20 is adjusted when the valve timing is adjusted to a desired position when the engine is restarted. It is possible to prevent the movement of the vane rotor 23 from being hindered by the viscosity. Thereby, as the effect (d) of the third embodiment, the responsiveness of the valve timing at the time of cranking during engine restart can be further improved.

(Fourth embodiment)
Next, the electromagnetic actuator by 4th embodiment of this invention is demonstrated based on FIG. The fourth embodiment differs from the first embodiment in the method of oil discharge processing in the electromagnetic actuator after the engine is stopped. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

  FIG. 8 shows a flowchart of the oil discharge process in the electromagnetic actuator according to the fourth embodiment. FIG. 9 shows a characteristic diagram of oil discharge processing in the electromagnetic actuator according to the fourth embodiment. FIG. 9A is a characteristic diagram showing a change over time in the engine speed in the oil discharge process of the fourth embodiment. FIG. 9B is a characteristic diagram showing a temporal change of the hydraulic pressure in the valve timing adjusting unit 20 in the oil discharge process of the fourth embodiment. FIG. 9C is a characteristic diagram showing a change over time in the duty ratio of the current flowing through the coil 11 in the oil discharging process of the fourth embodiment.

  In the electromagnetic actuator according to the fourth embodiment, first, in S401, the ignition is turned OFF as in S101 of the first embodiment. When the ignition is turned off at time t40 shown in FIG. 9, the engine stops at time t41.

  Next, in S402, partial residual pressure removal control of the valve timing adjusting unit 20 is performed. In S <b> 402, the control unit 17 discharges “a certain amount of oil” out of the oil in the valve timing adjustment unit 20 while maintaining the state in which the intermediate lock member 24 is fitted in the fitting hole 215. Is allowed to flow through the coil 11 (from time t42 to time t43 in FIG. 9). As a result, the oil pressure of the oil remaining in the valve timing adjusting unit 20 becomes zero while the relative rotational phase of the vane rotor 23 with respect to the housing 21 is fixed to a predetermined phase.

  Next, in S403, similarly to S102 of the first embodiment, the reciprocating movement control of the movable core 13 is performed (from time t44 to time t45 in FIG. 9). Thereby, the air containing the oil in the core chamber 120 is discharged from the core chamber 120.

  In the electromagnetic actuator according to the fourth embodiment, after the engine is stopped, the control unit 17 first maintains a state in which the intermediate lock member 24 is fitted in the fitting hole 215 while maintaining the “fixed amount” in the valve timing adjusting unit 20. A current having a duty ratio α that allows the oil to be discharged to the outside flows through the coil 11. As a result, in the electromagnetic actuator according to the fourth embodiment, the relative rotational phase of the vane rotor 23 with respect to the housing 21 remains fixed at a predetermined phase by the intermediate lock member 24. Can be started. Therefore, the fourth embodiment has the effects (a), (b) of the first embodiment, and the effect (c) of the second embodiment, and an optimum valve as the effect (e) of the fourth embodiment. The engine can be started at the timing.

(Fifth embodiment)
Next, the electromagnetic actuator by 5th embodiment of this invention is demonstrated based on FIG. The fifth embodiment is different from the first embodiment in the method of oil discharge processing in the electromagnetic actuator after the engine is stopped. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

  FIG. 10 shows a flowchart of the oil discharge process in the electromagnetic actuator according to the fifth embodiment. FIG. 11 shows a characteristic diagram of oil discharge processing in the electromagnetic actuator according to the fifth embodiment. FIG. 11A is a characteristic diagram showing a change over time in the engine speed in the oil discharge process of the fifth embodiment. FIG. 11B is a characteristic diagram showing a change over time of the hydraulic pressure in the valve timing adjustment unit 20 in the oil discharge process of the fifth embodiment. FIG. 11C is a characteristic diagram showing a change over time in the amount of oil in the valve timing adjustment unit 20 in the oil discharge process of the fifth embodiment. FIG. 11D is a characteristic diagram showing a change over time in the duty ratio of the current flowing through the coil 11 in the oil discharge process of the fifth embodiment.

  In the electromagnetic actuator according to the fifth embodiment, first, in S501, the ignition is turned OFF as in S101 of the first embodiment. When the ignition is turned off at time t50 in FIG. 10, the engine stops at time t51.

  Next, in S502, the partial residual pressure removal control of the valve timing adjustment unit 20 is performed as in S402 of the fourth embodiment. The control unit 17 causes a current having a duty ratio α to flow through the coil 11 from time t52 to time t53. As a result, the oil pressure of the oil remaining in the valve timing adjusting unit 20 becomes 0 while the relative rotation phase of the vane rotor 23 with respect to the housing 21 is fixed to a predetermined phase (see FIG. 11B).

  Next, in S503, similar to S302 in the third embodiment, residual pressure removal control for discharging the oil remaining in the valve timing adjusting unit 20 is performed. The control unit 17 causes a current having a duty ratio of 100% to flow through the coil 11 from time t54 to time t55. As a result, the oil remaining in the advance chamber and the retard chamber is discharged from the oil discharge port 300, and the amount of oil in the valve timing adjusting unit 20 becomes 0 (see FIG. 11C).

  Next, in S504, similarly to S102 of the first embodiment, the reciprocating movement control of the movable core 13 is performed (between time t56 and time t57 in FIG. 11). Thereby, the air containing the oil of the core chamber 120 is discharged outside.

  In the fifth embodiment, after the engine is stopped, the control unit 17 causes a current having a duty ratio α to flow through the coil 11 so as to discharge a part of the oil remaining in the valve timing adjustment unit 20 first. Accordingly, a part of the oil remaining in the valve timing adjusting unit 20 is discharged while the relative rotation phase of the vane rotor 23 with respect to the housing 21 is fixed to a predetermined phase by the intermediate lock member 24. Next, the control unit 17 supplies a current having a duty ratio of 100% to the coil 11 so as to discharge the remaining oil in the valve timing adjustment unit 20. Thereby, it is possible to reliably prevent the air containing oil from being newly sucked by the reciprocating movement of the movable core 13 for discharging the air containing oil in the core chamber 120. Therefore, the fifth embodiment includes the effects (a) and (b) of the first embodiment, the effects (c) of the second embodiment, the effects (d) of the third embodiment, and the effects (e) of the fourth embodiment. ).

(Sixth embodiment)
Next, the electromagnetic actuator by 6th embodiment of this invention is demonstrated based on FIGS. The third embodiment is different from the first embodiment in the shape of the fixed core and the method of oil discharge processing in the electromagnetic actuator after the engine is stopped. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st embodiment, and description is abbreviate | omitted.

  FIG. 12 shows a schematic diagram of a valve timing adjusting device 2 including an electromagnetic actuator according to the sixth embodiment. The valve timing adjusting device 2 includes an electromagnetic actuator 40, a valve timing adjusting unit 20, a hydraulic control valve 30, and the like.

  The fixed core 42 provided in the electromagnetic actuator 40 has a communication path 424 formed in the second cylindrical portion 422 on the ground side in the gravity direction. The communication path 424 passes through the second cylindrical portion 422 in the vertical direction. The communication path 424 communicates the core chamber 120 on the opposite side of the movable core 13 from the hydraulic control valve 30 and the outside of the core chamber 120.

  FIG. 13 shows a characteristic diagram of oil discharge processing in the electromagnetic actuator 40. FIG. 13A is a characteristic diagram showing the change over time of the engine speed in the oil discharge process of the sixth embodiment, and FIG. 13B is the oil discharge process of the sixth embodiment. It is a characteristic view which shows the time change of the duty ratio of the electric current which flows through the coil 11 of.

  In the oil discharge process of the sixth embodiment, after the ignition is turned off at time t60 and the engine is stopped at time t61, the reciprocating control of the movable core 13 is performed. At this time, the control unit 17 causes a current having a duty ratio shown in FIG. 13 from time t62 to time t66 to flow through the coil 11. Specifically, the duty ratio is increased from 0% to 100% between time t62 and time t63. After increasing the duty ratio, the duty ratio remains constant at 100% between time t63 and time t64 as “predetermined time”. After the duty ratio is made constant, the duty ratio is reduced from 100% to 0% between time t64 and time t65. At this time, the control unit 17 controls the energization of the coil 11 so that the time from time t62 to time t63 is shorter than the time from time t64 to time t65. In the oil discharge process of the sixth embodiment, the duty ratio is changed a plurality of times, and the reciprocating control of the movable core 13 is repeated a plurality of times.

  In the oil discharge process of the sixth embodiment, the duty ratio is constant between the time zone in which the movable core 13 is moved to the hydraulic control valve 30 side and the time zone in which the movable core 13 is moved to the opposite side of the hydraulic control valve 30. A time zone is provided. Here, the operation | movement by the oil discharge process in the electromagnetic actuator 40 is demonstrated based on FIG. FIG. 14A shows a state of the electromagnetic actuator 40 in a state where a current having a duty ratio of 0%, that is, no current flows through the coil 11. FIG. 14B shows the state of the electromagnetic actuator 40 in a state where a current having a duty ratio of 100% flows through the coil 11.

  In the oil discharge process in the electromagnetic actuator 40, when the movable core 13 moves from the state shown in FIG. 14A to the hydraulic control valve 30 side, the air containing the oil in the core chamber 120 on the hydraulic control valve 30 side of the movable core 13 is As shown by a solid arrow F61 in FIG. 14B, the air flows into the core chamber 120 on the opposite side of the hydraulic control valve 30 of the movable core 13 through the air hole 132 (see FIG. 14B). When the duty ratio is constant and the movable core 13 is stopped on the hydraulic control valve 30 side, the oil contained in the air flowing into the core chamber 120 on the opposite side of the movable core 13 from the hydraulic control valve 30 falls according to gravity. It collects on the inner wall of the second cylindrical portion 122. The oil accumulated on the inner wall of the second cylindrical portion 122 passes through the communication path 424 as shown by the solid line arrow F62 in FIG. 14B due to the movement of the movable core 13 to the side opposite to the hydraulic control valve 30. And discharged to the outside of the core chamber 120.

  When the movable core 13 moves to the hydraulic control valve 30 side in the reciprocating movement control of the movable core 13, the air containing oil enters the core chamber 120 on the opposite side of the movable core 13 from the hydraulic control valve 30 through the air hole 132. Inflow. Therefore, in the sixth embodiment, oil contained in the air is discharged to the outside of the core chamber 120 using the communication path 424. At this time, a period of time during which oil contained in the air sufficiently drops and accumulates due to gravity is provided for the oil discharge process. Thereby, the oil contained in the air moving through the air hole 132 to the core chamber 120 on the side opposite to the hydraulic control valve 30 of the movable core 13 can be reliably discharged to the outside. Therefore, the sixth embodiment achieves the effects (a) and (b) of the first embodiment, and reliably discharges the oil flowing into the core chamber 120 on the opposite side of the hydraulic control valve 30 of the movable core 13. be able to.

(Other embodiments)
In the first to fifth embodiments, the lid portion has the communication path that communicates the core chamber and the outside. However, the communication path may not be provided.

  In the above-described embodiment, the movable core has air holes. However, there may be no air holes.

  In the above-described embodiment, the duty ratio of the current flowing through the coil is changed in a pulse shape in the reciprocation control of the movable core. However, the change in the duty ratio of the current is not limited to this.

  In the above-described embodiment, in the reciprocation control of the movable core, the maximum value of the duty ratio of the current flowing through the coil is 100%. However, the maximum value of the duty ratio may not be 100%.

  In the above-described embodiment, the control for changing the duty ratio from 0% to 100% is performed a plurality of times in the reciprocating movement control of the movable core that discharges the oil in the core chamber. However, the control for changing the duty ratio from 0% to 100% may be performed once.

  In the above-described embodiment, the control unit determines whether the engine is stopped based on the detection result output from the crank angle sensor. However, the method for detecting the state of the engine is not limited to this.

  As mentioned above, this invention is not limited to such embodiment, It can implement with a various form in the range which does not deviate from the summary.

DESCRIPTION OF SYMBOLS 10, 40 ... Electromagnetic actuator 11 ... Coil 12, 42 ... Fixed core 120 ... Core chamber 13 ... Movable core 14 ... Rod 16 ... Housing 163 ... Insertion hole 17 ... Control unit

Claims (7)

Solid and constant core (12, 42),
A movable core (13) movable relative to the fixed core;
A coil (11) that forms a magnetic field passing through the fixed core and the movable core when energized;
A rod (14) provided so as to be capable of reciprocating integrally with the movable core;
A housing (16) having a core chamber (120) that movably accommodates the movable core, and an insertion hole (163) that communicates with the core chamber and through which the rod is inserted;
And is provided opposite to a hydraulic control valve (30) for supplying oil to a valve timing adjustment unit (20) capable of adjusting the opening / closing timing of the intake valve or exhaust valve of the engine, and an electromagnetic for driving the hydraulic control valve In the actuator (10, 40), a control unit (17) electrically connected to the coil,
After the engine stops, the coil is energized so that the movable core reciprocates ,
A control unit that energizes the coil so that oil in the valve timing adjusting unit is discharged after the engine is stopped and before the movable core reciprocates . Solid and constant core (12, 42),
A movable core (13) movable relative to the fixed core;
A coil (11) that forms a magnetic field passing through the fixed core and the movable core when energized;
A rod (14) provided so as to be capable of reciprocating integrally with the movable core;
A housing (16) having a core chamber (120) that movably accommodates the movable core, and an insertion hole (163) that communicates with the core chamber and through which the rod is inserted;
And is provided opposite to a hydraulic control valve (30) for supplying oil to a valve timing adjustment unit (20) capable of adjusting the opening / closing timing of the intake valve or exhaust valve of the engine, and an electromagnetic for driving the hydraulic control valve In the actuator (10, 40), a control unit (17) electrically connected to the coil,
After pre-SL engine stops, and energizing the coil so that the movable core is reciprocated,
A control unit that energizes the coil to discharge a certain amount of oil in the valve timing adjustment unit after the engine has stopped, and then to discharge the remaining oil in the valve timing adjustment unit . Solid and constant core (12, 42),
A movable core (13) movable relative to the fixed core;
A coil (11) that forms a magnetic field passing through the fixed core and the movable core when energized;
A rod (14) provided so as to be capable of reciprocating integrally with the movable core;
A housing (16) having a core chamber (120) that movably accommodates the movable core, and an insertion hole (163) that communicates with the core chamber and through which the rod is inserted;
And is provided opposite to a hydraulic control valve (30) for supplying oil to a valve timing adjustment unit (20) capable of adjusting the opening / closing timing of the intake valve or exhaust valve of the engine, and an electromagnetic for driving the hydraulic control valve In the actuator (10, 40), a control unit (17) electrically connected to the coil,
After pre-SL engine stops, and energizing the coil so that the movable core is reciprocated,
A control unit that energizes the coil so that a certain amount of oil in the valve timing adjustment unit is discharged after the engine stops and before the movable core reciprocates . The movable core has an air hole (132) communicating the core chamber on the hydraulic control valve side of the movable core and the core chamber on the opposite side of the movable core from the hydraulic control valve;
The housing has a communication passage (424) that communicates the core chamber on the side opposite to the hydraulic control valve of the movable core and the atmosphere on the ground side,
Wherein, after the movable core is moved to the hydraulic control valve side, 請 Motomeko 1 wherein you energizing the movable core in a position moved to the hydraulic control valve side to the coil to stop a predetermined time 4. The control unit according to any one of 3 . The control unit energizes the coil such that a speed at which the movable core moves toward the hydraulic control valve is faster than a speed at which the movable core moves toward the opposite side of the hydraulic control valve. Item 5. The control unit according to any one of Items 1 to 4 . Solid and constant core (12, 42),
A movable core (13) movable relative to the fixed core;
A coil (11) that forms a magnetic field passing through the fixed core and the movable core when energized;
A rod (14) provided so as to be capable of reciprocating integrally with the movable core;
A housing (16) having a core chamber (120) that movably accommodates the movable core, and an insertion hole (163) that communicates with the core chamber and through which the rod is inserted;
And is provided opposite to a hydraulic control valve (30) for supplying oil to a valve timing adjustment unit (20) capable of adjusting the opening / closing timing of the intake valve or exhaust valve of the engine, and an electromagnetic for driving the hydraulic control valve In the actuator (10, 40), a control unit (17) electrically connected to the coil,
After pre-SL engine stops, and energizing the coil so that the movable core is reciprocated,
A control unit that energizes the coil such that the moving speed of the movable core toward the hydraulic control valve is faster than the moving speed of the movable core toward the opposite side of the hydraulic control valve . Wherein the control unit, the control unit according to any one of 請 Motomeko 1-6 you energizing the coil to a plurality of times reciprocating the movable core.

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