JP2000291416A - Solenoid driven valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce energy required to drive a zero rush adjuster by preventing unnecessary driving force from applying to the zero rush adjuster provided for a solenoid driven valve. SOLUTION: Solenoid driven valves 40, 42 are provided with zero rush adjusters 64, interposed between an intake valve 44 and an armature shaft 66, and between an exhaust valve 46 and the armature shaft 66. The zero rush adjusters 64 are extended by a supply of hydraulic pressure, when the solenoid driven valves 40, 42 are closed, thereby preventing generation of a gap between the intake valve 44 and the armature 66. When a cylinder halt control is under operation on an internal combustion engine 10, a hydraulic pump 106 supplying hydraulic pressure to the zero rush adjusters 64 corresponding to the solenoid driven valves 40, 42 of a cylinder, whose operation is halted, is stopped.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electromagnetically driven valve, and more particularly, to a solenoid operated valve provided with a zero lash adjuster interposed between a valve body and an armature to drive a part of the electromagnetically driven valve under a predetermined condition. The present invention relates to an electromagnetically driven valve in which a drive suspension control for suspending operation is performed.

[0002]

2. Description of the Related Art Conventionally, for example, Japanese Patent Application Laid-Open No. 10-2524
An electromagnetically driven valve disclosed in Japanese Patent Publication No. 26 is known. The electromagnetically driven valve includes a valve body that functions as an intake valve or an exhaust valve of an internal combustion engine, an armature that works in conjunction with the valve body, and a valve opening that applies electromagnetic force to the armature in the valve opening direction and the valve closing direction, respectively. And a valve closing electromagnet. Therefore, according to the above-mentioned conventional electromagnetically driven valve, the valve element can be opened and closed by exciting each electromagnet alternately.

Further, in the above-mentioned conventional electromagnetically driven valve, a gap is formed between the armature and the valve body in a state where the armature is attracted by the valve closing electromagnet and the valve body is seated on the valve seat. Is configured. According to this configuration, even when the relative displacement between the valve body and the armature occurs due to the thermal expansion of the valve body and wear of the seating surface between the valve body and the valve seat, the relative displacement is absorbed by the gap. Thus, the valve can be reliably displaced until the valve is seated on the valve seat. However, if a gap is formed between the valve element and the armature, the armature collides with the valve element when the valve element is opened, so that a collision noise is generated, and the operating noise of the electromagnetically driven valve increases. Would.

[0004] In order to prevent such an increase in the operating noise, it is conceivable to provide a zero lash adjuster between the valve body and the armature. The zero lash adjuster is a mechanism that expands and contracts according to the relative displacement between the valve body and the armature.
By providing the zero lash adjuster, it is possible to reduce the operation noise by absorbing a relative displacement between the valve element and the armature, while preventing a gap from being formed between the valve element and the armature.

[0005]

However, in a zero-lash adjuster configured to extend when a driving force (for example, hydraulic pressure) is applied from the outside, a power source (for example, a hydraulic pump) is required to make the zero-lash adjuster function. Required. Extra energy is required to operate such a power source.

In an internal combustion engine in which an intake valve and an exhaust valve are constituted by electromagnetically driven valves, to improve fuel efficiency,
During low-load, low-speed operation or the like, the operation of a particular cylinder may be stopped by stopping fuel injection while seating the valve body on the valve seat. In this case, in the cylinder whose operation has been stopped, the opening and closing drive of the valve element is stopped. Further, in the above-described internal combustion engine, it is conceivable to stop the opening / closing drive of some valve bodies in the cylinder. When the opening / closing drive of the valve body is stopped in this way, even if no driving force is applied to the zero lash adjuster of the electromagnetically driven valve, there is no possibility that the operating noise will increase. That is,
It is not necessary to apply a driving force to the zero lash adjuster of the electromagnetically driven valve whose opening / closing drive is stopped.

[0007] The present invention has been made in view of the above points, and by preventing unnecessary driving force from being applied to a zero lash adjuster provided in an electromagnetically driven valve,
An object of the present invention is to provide an electromagnetically driven valve capable of reducing energy required for driving a zero lash adjuster.

[0008]

The above object is achieved by the present invention.
As described in the above, a valve body that functions as an intake valve or an exhaust valve of an internal combustion engine, an armature that drives the valve body, and a driving force is provided between the valve body and the armature. A zero-rush adjuster that extends by following a change in the distance between the valve element and the armature, and in an electromagnetically driven valve, a drive suspension control unit that suspends opening and closing driving of some electromagnetically driven valves under a predetermined condition. And a driving force reducing means for stopping or reducing the application of the driving force to the zero lash adjuster of the electromagnetically driven valve whose opening / closing drive is suspended by the drive suspension control means. Is achieved by

In the present invention, the opening / closing drive of some of the electromagnetically driven valves is stopped under a predetermined condition. In the electromagnetically driven valve in which the opening and closing drive is stopped, no operation noise is generated due to the collision between the armature and the valve body. Therefore, it is not necessary to apply a driving force to the zero lash adjuster of such an electromagnetically driven valve. In the present invention, the application of the driving force to the zero lash adjuster of the electromagnetically driven valve whose opening / closing drive is stopped is stopped or reduced. Therefore, unnecessary driving force is prevented from being applied to the zero lash adjuster, so that the energy required to drive the zero lash adjuster can be reduced.

[0010]

FIG. 1 is a sectional view of a main part of an internal combustion engine 10 having an electromagnetically driven valve according to an embodiment of the present invention. FIG. 2 is a diagram showing the internal combustion engine 10 according to the present embodiment as viewed from the arrow III shown in FIG. Internal combustion engine 10 of the present embodiment
Includes an electronic control unit (hereinafter, referred to as an ECU) 11, and is controlled by the ECU 11.

As shown in FIG. 1, the internal combustion engine 10 includes a cylinder block 12. Inside the cylinder block 12, a cylinder 14 and a water jacket 16 are provided.
Are formed. As shown in FIG. 2, the internal combustion engine 10
It has four cylinders # 1 to # 4. FIG. 1 shows a cylinder 14 corresponding to one of these cylinders.

A piston 18 is slidably housed in the cylinder 14. Piston 18 inside cylinder 14
Above above, a combustion chamber 20 is defined. A lower head 24 is provided above the cylinder block 12. The lower head 24 has an intake port 26 and an exhaust port 28 that open to the combustion chamber 20. The opening of the intake port 26 to the combustion chamber 20 and the opening of the exhaust port 28 to the combustion chamber 20 have valve seats 3 respectively.
0, 32 are formed.

A cylinder head spacer 36 is disposed above the lower head 24 via a heat insulating plate 34. The heat insulating plate 34 is a sheet-like member made of a heat insulating material such as bakelite, for example.
It has a function of suppressing transmission of high heat generated at 0 to the cylinder head spacer 36 from the lower head 24. An upper head 38 is fixed to an upper portion of the cylinder head spacer 36.

The upper head 38, the cylinder head spacer 36, and the lower head 24 have an electromagnetically driven valve 40,
42 are stored. The electromagnetically driven valve 40 includes an intake valve 44 that connects or disconnects the intake port 26 and the combustion chamber 20. On the other hand, the electromagnetically driven valve 42 is connected to the exhaust port 28.
An exhaust valve 46 for conducting or shutting off the combustion chamber 20 is provided. As shown in FIG. 2, the intake valve 44 and the exhaust valve 46
Are provided for each cylinder. The electromagnetically driven valve 40 and the electromagnetically driven valve 42 have the same configuration. Therefore, the structure and operation of the electromagnetically driven valve 40 will be described below as a representative thereof.

As shown in FIG. 1, the electromagnetically driven valve 40 is provided integrally with the intake valve 44 and has a valve shaft 48 extending upward. Inside the lower head 24, a valve guide 5 is provided.
0 is provided. The valve shaft 48 is slidably held in the axial direction by a valve guide 50. Lower head 2
4, a spring holding space 52 formed in a cylindrical shape is provided at a portion surrounding substantially the upper half of the valve shaft 48. The upper end of the valve guide 50 is exposed inside the spring holding space 52. A valve stem seal 54 is mounted around the vicinity of the upper end of the valve guide 50 in the spring holding space 52.

A cotter 56 is mounted near the upper end of the valve shaft 48. The cotter 56 is a substantially cylindrical member having a wedge-shaped outer peripheral surface having a larger diameter as it goes upward in FIG. 1 and having an inward projection on the inner peripheral surface. The protrusion on the inner peripheral surface of the cotter 56 is fitted into a concave portion provided on the outer peripheral surface of the valve shaft 48. A lower retainer 58 is fitted around the outer periphery of the cotter 56.

A spring seat 60 is provided on the bottom surface of the spring holding space 52. Between the spring seat 60 and the lower retainer 58, there is disposed a lower spring 62 that generates an urging force in a direction to separate them. The lower spring 62 biases the intake valve 44 upward through the lower retainer 58, that is, in a direction toward the valve seat 30. Hereinafter, the direction in which the intake valve 44 moves toward the valve seat 30 is referred to as a valve closing direction, and the direction in which the intake valve 44 moves away from the valve seat 30 is referred to as a valve opening direction.

An armature shaft 66 is provided above the valve shaft 48 with a zero lash adjuster 64 therebetween.
And are arranged coaxially. Zero lash adjuster 64
Will be described later in detail. A cotter 68 having a vertically symmetric configuration with the cotter 56 is mounted on the upper end of the armature shaft 66. An applicator 70 is fitted around the cotter 68. The lower end of the upper spring 72 is in contact with the upper surface of the upper retainer 70. A cylindrical upper case 74 is provided around the upper spring 72. An adjuster bolt 76 is screwed onto the upper part of the upper case 74. The upper end of the upper spring 72 is in contact with an adjuster bolt 76 via a spring guide 78. The upper spring 72 includes an upper retainer 70.
Urges the armature shaft 66 downward.

An armature 80 is joined to the outer periphery of the central portion of the armature shaft 66 in the axial direction. The armature 80 is a disk-shaped member made of a soft magnetic material. Above the armature 80, an upper coil 82 and an upper core 84 are provided. Further, a lower coil 86 and a lower core 88 are provided below the armature 80. Upper coil 82 and lower coil 86
Are accommodated in annular grooves 84a and 88a formed in the upper core 84 and the lower core 88, respectively. The upper coil 82 and the lower coil 86 are electrically connected to the ECU 11. The ECU 11 supplies a command signal to the upper coil 82 or the lower coil 86 so that the intake valve 44 opens and closes properly.

The upper core 84 and the lower core 88 are provided with through holes 84b and 88b, respectively, penetrating the central portions thereof. An upper bush 90 is provided at the upper end of the through hole 84b of the upper core 84. A lower bush 92 is provided at the lower end of the through hole 88b of the lower core 88.
Are arranged. The armature shaft 66 is slidably held in the axial direction by an upper bush 90 and a lower bush 92. Flanges 84c and 88c are provided at the upper end of the upper core 84 and the lower end of the lower core 88, respectively.

The cylinder head spacer 36 has a cylindrical lash adjuster holding space 36 penetrating therethrough.
a is formed coaxially with the spring holding space 52. Inside the lash adjuster holding space 36a,
The zero lash adjuster 64 described above is held. An upwardly protruding ridge 36b is provided near the opening of the lash adjuster holding space 36a on the upper surface of the cylinder head spacer 36. Further, the ridge 36
A cylindrical portion 36c is formed at the top of b.

In the upper head 38, a cylindrical core holding space 38a penetrating the upper and lower portions thereof is formed coaxially with the spring holding space 52 and the lash adjuster holding space 36a. The upper core 84 has its flange portion 84c in contact with the upper head 38 via a shim 94,
Further, the lower cores 88 are each provided with a core holding space 38 such that the flange portion 88c abuts on the upper head 38.
a. Flange portion 84 of upper core 84
c is sandwiched between the upper head 38 and a flange portion 74a formed at the lower end of the upper case 74. Further, the flange portion 88 c of the lower core 88 is sandwiched between the upper head 38 and the lower bracket 96. Then, the upper case 74 and the lower bracket 96
Are fixed to the upper head 38 by the fixing bolts 98 and 99, so that the upper core 84 and the lower core 88 are fixed at a predetermined interval.

In the state where the upper core 84 and the lower core 88 are fixed as described above, a predetermined gap is formed between the raised portion 36b of the cylinder head spacer 36 and the lower surface of the lower core 88. The adjuster bolt 76 is adjusted so that the neutral position of the armature 80 is located at the midpoint between the upper core 84 and the lower core 88.

The cylinder head spacer 36 is provided with oil supply paths 100 and 102 communicating with each other.
The oil supply passage 102 is provided in the lash adjuster holding space 36a.
It is opened at a predetermined position on the inner wall surface of the. A hydraulic pump 106 is connected to the oil supply path 100 via a hydraulic pipe 104. The hydraulic pump 106 is provided for each cylinder and is configured as an electric pump. The on / off state of the hydraulic pump 106 is controlled by the ECU 11. A regulator 108 is provided in the hydraulic piping 104. The regulator 108 is connected to the hydraulic pump 10
The ECU 6 supplies the oil sucked from the oil tank 110 to the ECU 11
The pressure is adjusted to a hydraulic pressure in accordance with the control signal supplied from the controller and supplied to the oil supply paths 100 and 102. Hereinafter, the oil supply path 100,
The oil pressure supplied to 102 is referred to as a supply oil pressure Pe.

The cylinder head spacer 36 further includes
An oil recovery hole 112 is provided. Oil recovery hole 112
The upper end is a raised portion 36b of the cylinder head spacer 36.
, And penetrates vertically through the cylinder head spacer 36 such that the lower end opens into the spring holding space 52. The oil recovery hole 112 collects the oil leaked upward from the zero lash adjuster 64 and causes the oil to flow into the spring holding space 52.
It has a role to supply lubricating oil for the valve shaft 6 and the valve shaft 48. In addition, the upper part of the oil recovery hole 112 is the processing hole 112a,
With the configuration of 12b, a large opening area of the oil recovery hole 112 to the upper surface of the cylinder head spacer 36 is secured.

Next, the operation of the electromagnetically driven valve 40 will be described. When an exciting current is supplied to the upper coil 82, the armature 80
, An electromagnetic force in a direction toward the upper core 84 acts.
Therefore, as shown in FIG. 1, the armature 80 is opposed to the upper core 84 against the urging force of the upper spring 72.
Is displaced until it touches. Hereinafter, the position where the armature 80 contacts the upper core 84 is referred to as the armature 80, the armature shaft 66, or the fully closed position of the intake valve 44. In this state, the intake valve 44 sits on the valve seat 30, and the intake valve 44 is closed.

When the supply of the current to the upper coil 82 is stopped with the intake valve 44 closed as described above,
The electromagnetic force required to hold the armature 80 in the fully closed position disappears. Therefore, when the supply of current to the upper coil 82 is stopped, the armature shaft 66, together with the intake valve 44, is urged by the upper spring 72 to start a single-vibration movement downward. For this reason,
When the intake valve 44 separates from the valve seat 30, the intake valve 44 is opened. When the exciting current is supplied to the lower coil 86 at the time when the displacement amount of the armature shaft 66 reaches a predetermined value, an electromagnetic force for urging the armature 80 toward the lower core 88 is generated.

When the electromagnetic force acts on the armature 80, the kinetic energy lost by friction is compensated for, and
The armature 80 is displaced until it comes into contact with the lower core 88 against the urging force generated by the lower spring 62. Hereinafter, the position where the armature 80 contacts the lower core 88 is referred to as the armature 80, the armature shaft 66, or the fully open position of the intake valve 44.

In this state, when the supply of the exciting current to the lower coil 86 is stopped, the electromagnetic force necessary to hold the armature 80 at the fully open position disappears. Therefore, the intake valve 44 and the armature shaft 66 start a single-vibration motion upward by the urging force generated by the lower spring 62. When the exciting current is supplied to the upper coil 82 at the time when these displacement amounts reach a predetermined value, the kinetic energy lost due to friction is compensated by the electromagnetic force generated by the upper coil 82, and the armature 80 becomes the upper core 84.
Is displaced until it touches. When the armature 80 is in contact with the upper core 84, the intake valve 44 is seated on the valve seat 30, and the intake valve 44 is again closed.

As described above, according to this embodiment, the current is alternately supplied to the upper coil 82 and the lower coil 86 at an appropriate timing, so that the intake valve 44 is repeatedly switched between the fully closed position and the fully opened position. Can be reciprocated. In the present embodiment, the above-mentioned zero lash adjuster 64 is provided between the intake valve 44 and the armature shaft due to a difference in thermal expansion between the intake valve 44 and the lower head 24 and wear of the seating surface between the intake valve 44 and the valve seat 30. It has a function of preventing a gap from being formed between both members by absorbing the relative displacement with respect to 66. Hereinafter, the configuration and operation of the zero lash adjuster 64 will be described.

FIG. 3 is an enlarged sectional view showing the zero lash adjuster 64 and its peripheral portion. In addition, FIG.
The state realized in a situation where the armature 80 and the intake valve 44 are in the fully closed position is shown. As shown in FIG. 3, the zero lash adjuster 64 includes a plunger body 120. The plunger body 120 is slidably disposed in the lash adjuster holding space 36a in the axial direction. The plunger body 120 is a substantially cylindrical member whose one end (the lower end in FIG. 3) is closed. The plunger body 120 includes a spring holding portion 120a provided at a lower end thereof, and a plunger holding portion 120b having a larger diameter than the spring holding portion 120a. The plunger 122 is disposed on the plunger holding portion 120b so as to be slidable in the axial direction. A hydraulic chamber 124 is defined between the lower bottom surface of the plunger 122 in FIG. 3 and the lower bottom surface of the spring holding portion 120a.

The plunger 122 has, on its outer peripheral surface, a large-diameter portion 122a sliding on the inner peripheral surface of the plunger holding portion 120b, and a small-diameter portion 1 provided at the upper end in FIG.
22b. On the other hand, the plunger holder 120
A stopper ring 126 is press-fitted into the upper end of the inner peripheral surface of b. The stopper ring 126 is
Has a smaller inner diameter than the outer diameter of the large diameter portion 122a. Therefore, the plunger holder 1 of the plunger 122
The upward displacement inside the inner portion 20b is caused by the step between the large diameter portion 122a and the small diameter portion 122b and the stopper ring 126.
Is regulated by contact with Plunger 122
Has a reservoir chamber 128 that opens upward, and a communication passage 130 that communicates the reservoir chamber 128 with the hydraulic chamber 124.

The hydraulic chamber 124 is provided with a retainer 132 and a plunger spring 134. Plunger spring 134 urges plunger 122 upward via retainer 132. A check ball 136 and a check ball spring 138 are disposed inside the retainer 132. The check ball spring 138 passes the check ball 136 to the communication passage 130.
Is urged toward the opening. Check ball 136
And the check ball spring 138 is connected to the hydraulic chamber 124.
It functions as a check valve that opens only when the pressure on the side becomes lower than that on the reservoir chamber 128 side.

The zero lash adjuster 64 also has a reservoir cap 140. The reservoir cap 140 is a cylindrical member having one end (the lower end in FIG. 3) closed. The reservoir cap 140 is slidably disposed in the lash adjuster holding space 36a such that the bottom surface of the reservoir cap 140 contacts the upper end surface of the plunger 122. On the lower bottom surface of the reservoir cap 140, an overflow recess 142, which is partially cut away, is provided. The overflow recess 142 is located in the reservoir 1
28 is always in communication.

The lower end surface of the armature shaft 66 is in contact with the inner bottom surface of the reservoir cap 140. on the other hand,
The upper end surface of the valve shaft 48 is in contact with the outer bottom surface of the plunger body 120. The oil supply passage 102 is provided on the inner peripheral surface of the lash adjuster holding space 36a so as to communicate with the overflow recess 142 in the state shown in FIG. 3, that is, in a state where the armature 80 and the intake valve 44 are in the fully closed position. It is open.

In the state shown in FIG.
When the power supply to the armature shaft is cut off, the urging force in the valve opening direction acts on the armature shaft 66 as described above. The force in the valve opening direction is applied from the reservoir cap 140 to the plunger 12.
2 is transmitted. When the force transmitted to the plunger 122 exceeds the urging force of the plunger spring 134, the plunger 122 is pressed downward, so that the hydraulic chamber 124
The oil inside is pressurized. For this reason, the hydraulic pressure in the hydraulic chamber 124 becomes higher than the hydraulic pressure in the reservoir chamber 128, and the communication path 1
30 is closed by a check ball 136. When the communication passage 130 is closed, the hydraulic chamber 124 and the reservoir chamber 12 are closed.
The transfer of oil between 8 and is prohibited. Therefore, the driving force transmitted to the plunger 122 is transmitted to the plunger body 120 via the hydraulic chamber 124, and the zero lash adjuster 64 is displaced in the valve opening direction together with the armature shaft 66 and the intake valve 44.

In the process in which the zero lash adjuster 64 is displaced in the valve opening direction, the oil in the hydraulic chamber 124 is pressurized, so that the oil from the hydraulic chamber 124 passes through the sliding surface between the plunger 122 and the plunger body 120. Gradually leaks out,
The lash adjuster 64 shrinks by a small amount corresponding to the oil leak. After the armature 80 has been displaced until it comes into contact with the lower core 88, when the energization of the lower coil 86 is stopped, the armature 80 starts to be displaced in the valve closing direction. When the intake valve 44 is seated on the valve seat 30, the urging force of the lower spring 62 does not act on the plunger body 120. On the other hand, even after the intake valve 44 is seated on the valve seat 30, the armature 80 is further displaced in the valve closing direction by a minute amount corresponding to the contraction of the lash adjuster 64 in the process of displacing the intake valve 44 in the valve opening direction. I do. In this case, the plunger 122 attempts to slide upward with respect to the plunger body 120 following the reservoir cap 140 by the urging force of the plunger spring 134, and the hydraulic pressure in the hydraulic chamber 124 decreases.

Then, the hydraulic chamber 124 becomes the reservoir chamber 128
When the pressure becomes lower than that, the check ball 136 is
By being separated from the opening 30, the hydraulic chamber 124 and the reservoir chamber 128 communicate with each other. As described above, when the intake valve 44 is seated on the valve seat 30, the oil supply passage 102 and the overflow recess 142 communicate with each other. Therefore, when the hydraulic chamber 124 and the reservoir chamber 128 communicate with each other, the oil of the supply hydraulic pressure Pe supplied from the hydraulic pump 106 to the oil supply path 100 is supplied from the oil supply path 102 to the hydraulic chamber 124 via the reservoir chamber 128. As a result, the plunger 122 slides upward while maintaining the state of being in contact with the reservoir cap 140.

As described above, when the intake valve 44 reaches the fully closed position, the oil of the supply oil pressure Pe is supplied to the zero lash adjuster 64, and the zero lash adjuster 64 is extended, so that the intake valve 44 and the armature are connected. Shaft 66
Is prevented from forming a gap therebetween. Further, the change in the interval between the valve shaft 48 and the armature shaft 66 caused by the difference in thermal expansion between the intake valve 44 and the lower head 24 and the wear of the seating surface between the intake valve 44 and the valve seat 30 are time-dependent. It occurs slowly, and the change in the interval that occurs while the intake valve 44 makes one reciprocation between the fully closed position and the fully open position is extremely small. For this reason, the above-described change in the interval is caused by the zero lash adjuster 64 contracted while the intake valve 44 is opened,
It is absorbed in the process of elongating when the intake valve 44 is closed.

In this embodiment, the intake valve 44 and the exhaust valve 46 are provided for some of the cylinders (for example, the # 1 and # 3 cylinders in FIG. 2) when the internal combustion engine 10 is operating at a low load and a low speed. Is held at the fully closed position, and the fuel injection is stopped, whereby control for stopping the operation of the cylinder is performed. Hereinafter, this control is referred to as cylinder deactivation control. According to the cylinder deactivation control, the pumping loss in the cylinder whose operation is deactivated is reduced, and the fuel injection amount is reduced, so that the fuel efficiency can be improved.

In the cylinder stopped as described above, the intake valve 4
4 and the opening / closing operation of the exhaust valve 46 are stopped. For this reason, in such a situation, even if the hydraulic pressure is not supplied to the zero lash adjuster 64, there is no possibility that inconveniences such as an increase in the operating noise of the electromagnetically driven valves 40 and 42 are caused. Therefore, in the present embodiment, the supply of the hydraulic pressure to the zero lash adjuster 64 corresponding to the electromagnetically driven valves 40 and 42 of the stopped cylinder is stopped during the execution of the cylinder stop control.

FIG. 4 shows a flowchart of an example of a control routine executed by the ECU 11 in the internal combustion engine 10 of this embodiment to realize the above functions. The routine shown in FIG. 4 is a periodic interrupt routine that is started every predetermined time. When the routine shown in FIG. 4 is started, first, the process of step 200 is executed. In step 200, it is determined whether or not the cylinder deactivation control is being performed in the internal combustion engine 10. When the cylinder deactivation control is not performed, all the electromagnetically driven valves 4 mounted on the internal combustion engine 10
It is necessary to supply a predetermined oil pressure to the 0, 42 zero lash adjusters 64. Therefore, when such a determination is made, the process of step 202 is executed next.
On the other hand, when the cylinder deactivation control is being performed, there is no need to supply hydraulic pressure to the zero lash adjusters 64 of the electromagnetically driven valves 40 and 42 whose opening and closing drive is stopped. Therefore, if such a determination is made, then step 20
4 is executed.

In step 202, a process for turning on all the hydraulic pumps 106 is executed. When the process of step 202 is performed, a predetermined hydraulic pressure is supplied to the zero lash adjusters 64 of all the electromagnetically driven valves 40 and 42 mounted on the internal combustion engine 10 thereafter. When the process of step 202 ends, the current routine ends.

In step 204, a process for specifying the cylinder whose operation is suspended by the cylinder suspension control is executed. In step 206, a process of turning off the hydraulic pumps 106 corresponding to the deactivated cylinders specified in step 204 and turning on the hydraulic pumps 106 corresponding to the cylinders other than the deactivated cylinders is executed. When the processing of step 206 is performed, the internal combustion engine 1
The supply of the hydraulic pressure to the zero lash adjuster 64 corresponding to the electromagnetically driven valves 40 and 42 of the cylinders of which the operation is suspended by the cylinder suspension control is stopped. When the process of step 206 ends, the current routine ends.

According to the above processing, when the cylinder deactivation control is being performed, the hydraulic pump 106 corresponding to the cylinder whose operation has been deactivated can be stopped. The electromagnetically driven valve 40 whose opening and closing drive is stopped by the cylinder deactivation control,
For the zero lash adjuster 64 included in the 42,
There is no need to supply hydraulic pressure. For this reason, according to the present embodiment, it is possible to prevent unnecessary supply of hydraulic pressure to the zero lash adjusters 64 of the electromagnetically driven valves 40 and 42 mounted on the internal combustion engine 10. Therefore, according to the present embodiment, the power consumption of the hydraulic pump 106 functioning as the power source of the zero-lash adjuster 64 is reduced by limiting the hydraulic pump 106 that is in operation during the execution of the cylinder deactivation control. be able to.

As described above, in this embodiment, the supply of the hydraulic pressure to the zero lash adjusters 64 of the electromagnetically driven valves 40 and 42 whose opening / closing drive is stopped is stopped. When the supply of the hydraulic pressure to the zero lash adjuster 64 is stopped, the oil in the hydraulic chamber 124 does not leak through the sliding surface between the plunger 122 and the plunger body 120. Further, in the electromagnetically driven valves 40 and 42 in which the opening / closing drive is stopped, it is not necessary to supply oil leaking from the hydraulic chamber 124 as lubricating oil for the armature shaft 66 and the valve shaft 48. Therefore, according to the present embodiment, it is possible to reduce the amount of leaking oil and to supply the lubricating oil according to the operation state of the armature shaft 66 and the valve shaft 48. I have.

In the above embodiment, the ECU 11
However, by executing the cylinder deactivation control, the electromagnetically driven valves 40, 4
By stopping the opening / closing drive of the second drive unit, the “drive suspension control unit” according to the first embodiment executes the processing of step 206, so that the “drive force reduction unit” according to the first embodiment executes
Each has been realized. By the way, in the above embodiment, the opening and closing drive of all the electromagnetic drive valves 40 and 42 provided in a specific cylinder is stopped by executing the cylinder deactivation control. The opening and closing drive of the drive valves 40 and 42 may be stopped. That is, when the internal combustion engine 10 is operating at a low load and at a low speed, the intake air amount and the exhaust amount of the internal combustion engine 10 are small.
It is not necessary to open and close. In such a case, some of the intake valves 44 and the exhaust valves 46 are held at the fully closed position. However, the electromagnetically driven valves 40 and 40 corresponding to the intake valves 44 and the exhaust valves 46 held at the fully closed position are used. By stopping the supply of the hydraulic pressure to the zero lash adjuster 64 at 42, the power consumption of the hydraulic pump 106 can be reduced. In this case, the hydraulic pump 106 is
What is necessary is just to provide corresponding to the group of the electromagnetically driven valves 40 and 42 in which the opening and closing drive is always performed, and the group of the electromagnetically driven valves 40 and 42 in which the opening and closing drive can be stopped.

In the above-described embodiment, the hydraulic pump 106 is provided for each cylinder, and the supply of the supply hydraulic pressure to the zero lash adjuster 64 is stopped by stopping the hydraulic pump 106. However, the present invention is not limited to this. When a common hydraulic pump is provided for all cylinders, the supply of hydraulic pressure to the zero lash adjusters 64 of the electromagnetically driven valves 40 and 42 is cut off. The obtained shutoff valve may be provided, for example, in the hydraulic pipe 104, and the supply of the hydraulic pressure may be shut off by driving the shutoff valve during the execution of the cylinder deactivation control. In such a configuration, as described above, the zero lash adjuster 64
When the supply of hydraulic pressure to the hydraulic pump is cut off, the power consumption of the hydraulic pump is reduced by reducing the discharge flow rate of the hydraulic pump,
As a result, power saving of the system is achieved.

In the above embodiment, the hydraulic pump 106 is stopped during the execution of the cylinder deactivation control. However, the method of reducing the power consumption of the hydraulic pump 106 is not limited to this. Hydraulic pump 106
Oil pressure Pe supplied to the oil supply passages 100 and 102 from the
May be reduced. When the supply oil pressure Pe decreases, the load on the hydraulic pump 106 decreases, and power saving of the hydraulic pump 106 is achieved. Therefore,
In this embodiment, the power consumption of the hydraulic pump 106 can be reduced by reducing the supply hydraulic pressure Pe instead of stopping the hydraulic pump 106 during the execution of the cylinder deactivation control.

In the above embodiment, the regulator 10
8, the supply oil pressure Pe can be reduced. However, in a configuration in which the regulator 108 is not provided,
The supply oil pressure Pe may be changed by changing the number of revolutions of the hydraulic pump 106, or the supply oil Pe may be changed intermittently by driving the hydraulic pump 106 according to the drive time.

Further, in the above embodiment, the zero lash adjuster 64 functions by applying the hydraulic pressure as the driving force. However, the present invention is not limited to this. A zero lash adjuster that functions by applying a force as a driving force may be used.

[0052]

As described above, according to the present invention, it is necessary to drive the zero lash adjuster by preventing unnecessary driving force from being applied to the zero lash adjuster of the electromagnetically driven valve. Energy can be reduced.

[Brief description of the drawings]

FIG. 1 is a sectional view of a main part of an internal combustion engine equipped with an electromagnetically driven valve according to an embodiment of the present invention.

FIG. 2 is a diagram showing the internal combustion engine of the present embodiment as viewed in the direction of arrow III shown in FIG.

FIG. 3 is an enlarged cross-sectional view of a zero lash adjuster provided in the electromagnetically driven valve of the embodiment and a peripheral portion thereof.

FIG. 4 is a flowchart of an example of a control routine executed in the internal combustion engine of the embodiment.

[Explanation of symbols]

 Reference Signs List 10 internal combustion engine 11 electronic control unit (ECU) 40, 42 electromagnetically driven valve 44 intake valve 46 exhaust valve 48 valve shaft 64 zero lash adjuster 66 armature shaft 80 armature 106 hydraulic pump

Continued on the front page (72) Inventor Isao Matsumoto 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Corporation (72) Inventor Shoji Katsumada 1 Toyota Town Toyota City, Aichi Prefecture Toyota Motor Corporation (72) Invention Person Masaaki Tanaka 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Corporation (72) Inventor Keiji Yoeda 1 Toyota Town, Toyota City, Aichi Prefecture Toyota Motor Corporation F-term (reference) 3G016 AA18 BB02 BB31 BB40 CA13 CA16 CA19 CA27 CA33 CA36 CA59 DA18 DA22 DA23 GA00 3H106 DA07 DA25 DB02 DB12 DB26 DB32 DC02 DC17 DD05 DD06 EE20 EE48 FB43 GC29 KK17

Claims (1)

[Claims] 1. A valve element that functions as an intake valve or an exhaust valve of an internal combustion engine, an armature that drives the valve element, and a driving force is provided between the valve element and the armature. A zero-rush adjuster that extends by following a change in the distance between the valve element and the armature, and a drive stop control unit that stops opening and closing of some of the electromagnetic drive valves under a predetermined condition. And a driving force reducing unit that stops or reduces the application of the driving force to the zero lash adjuster of the electromagnetically driven valve whose opening / closing drive is suspended by the drive suspension control unit. .