JP2001152819A - Valve driving device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve driving device for regulating valve clearance, without having to increase the size of the device with a simple structure. SOLUTION: A valve body and an armature shaft 22 are rotated during operation due to surge of first and second springs 41 and 71, and a distance between the valve body and the armature shaft 22 is changed by a distance changing means 80, when relative rotation is generated on the valve body and the armature shaft 22. The valve clearance can be regulated without having to increase the size of the device with the simple structure,. The distance changing means 80 has a valve clearance regulating member 81, provided with a spiral shaped end surface 81a and a third spring 82, and constitutes a rush adjustor for making the valve of the of the valve clearance zero. Failures in absorption of an armature main body can be prevented, and it is also possible to compensate clearance change by abrasion of members, such as the valve body and the valve clearance regulating member 81.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an internal combustion engine (hereinafter referred to as "internal combustion engine").
The present invention relates to a valve driving device that drives an intake valve or an exhaust valve of an “internal combustion engine” by an electromagnetic force.

[0002]

2. Description of the Related Art Conventionally, there has been known a valve driving device for driving an intake valve or an exhaust valve of an engine by electromagnetic force. In such a valve drive device, by controlling the opening / closing timing of an intake valve or an exhaust valve so that intake or exhaust is performed satisfactorily in accordance with operating conditions of the engine, improvement in engine stability, improvement in fuel efficiency, Alternatively, it is possible to reduce exhaust emissions.

For example, when the load of the engine is low, the amount of intake air is small, so that it is desirable that the amount of residual exhaust gas that deteriorates combustion in the cylinder of the engine is small. During a period in which the valve bodies of the intake valve and the exhaust valve are simultaneously open (overlap period), the intake side has a negative pressure due to the throttle and the exhaust side has a positive pressure. May worsen or misfire. For this reason, it is required that the closing timing of the exhaust valve is earlier and the opening timing of the intake valve is later than usual.
Further, by delaying the closing timing of the intake valve, pumping loss can be reduced and fuel efficiency can be improved. Therefore, at the time of idling and starting, it is desirable to control the basic phase so that the closing timing of the exhaust valve is early and the opening timing of the intake valve is late.

[0004] When the engine has a medium load or more, E
To control the GR amount, reduce pumping loss by internal EGR, and improve fuel efficiency and reduce exhaust emissions, it is necessary to make the intake-side valve opening timing earlier or the exhaust-side valve closing timing later. desirable.

Further, at full engine load, a large amount of air needs to be introduced into the cylinder of the engine. Therefore, the intake valve is closed early in the low speed range to prevent backflow to the manifold, and in the high speed range, air is It is desirable to close the intake valve late by using the inertia of the intake valve. Further, it is desirable that the exhaust side controls the exhaust valve to a phase in which exhaust pulsation can be used to the maximum.

[0006]

The electromagnetically driven valve driving device can satisfy the above-described demands on the intake and exhaust valve timings in accordance with an instruction from an electronic control unit (ECU). However, there are many problems to be solved in terms of noise, reliability, power consumption, manufacturing cost, and the like, as compared with a cam-driven valve driving device.

In a conventional valve driving device, for example, as shown in FIG. 6, the intake-side valve clearance changes in accordance with the temperature of the engine cooling oil.
As shown in (2), the exhaust-side valve clearance changes according to the temperature of the exhaust gas. Therefore, a predetermined clearance is provided between the valve stem and the armature shaft at normal temperature in order to absorb the difference in thermal expansion between the cylinder head, the housing, the valve body and the armature shaft and the amount of wear of the seat portion of the valve body. And
A method for reducing the above clearance has been proposed. However, in the method of reducing the change in clearance, it is necessary to detect the clearance, and it is inevitable that the seating speed control becomes complicated. Further, in the method using a damper for controlling the seating speed, if the valve clearance is set to about 0.3 mm, the electromagnetic force for sucking the armature is insufficient, and the suction fails.

Therefore, a hydraulic valve lifter using engine oil pressure, that is, a so-called fluid lash adjuster has been developed for a conventional engine. However, the above-mentioned fluid lash adjuster is difficult to use in an electromagnetically driven valve driving device in the following points.

[0009] An external hydraulic source is required. In the case of a conventional engine, an engine oil pump oil pressure and an engine oil can be used.However, an electromagnetically driven valve drive device uses a special oil having a smaller viscosity than the engine oil to lubricate the actuator. A dedicated oil pump is required, and the size of the device increases.

[0010] The mass of the fluid lash adjuster of about 10 grams is added to the movable part of the electromagnetically driven valve driving device, and the transition time of the movable part increases, and the responsiveness of the valve deteriorates.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and has as its object to provide a valve driving device that adjusts valve clearance with a simple configuration without increasing the size of the device. .

Another object of the present invention is to provide a valve driving device that suppresses an increase in the mass of a movable portion, reduces power consumption, and improves valve responsiveness.

[0013]

According to the valve driving device of the present invention, the distance changing means uses the relative rotation generated between the valve body and the armature shaft to rotate the valve body and the armature shaft. Change the distance between.
For this reason, when the valve body and the armature shaft rotate during operation due to the surge of the first and second urging means, and the valve body and the armature shaft rotate relative to each other, the distance changing means causes the valve body and the armature to rotate. The distance to the shaft is changed. Therefore, since no external hydraulic pressure source is required, the valve clearance can be adjusted with a simple configuration without increasing the size of the device. In addition, power consumption can be reduced by suppressing an increase in the mass of the movable portion, and the responsiveness of the valve can be improved.

According to the second aspect of the present invention, the first and second urging means are coil springs, and the first and second urging means are wound. Since the directions are opposite, both ends of the first and second urging means rotate in opposite directions when the first and second urging means expand and contract. Therefore, rotational torques in opposite directions are transmitted to the valve body and the mover shaft, and relative rotation occurs between the valve body and the mover shaft. Therefore, the distance between the valve body and the mover shaft is reliably changed by the distance changing means, and the valve clearance is reliably adjusted.

According to the valve driving device of the third aspect of the present invention, the valve clearance adjusting member provided at the connection portion between the valve body and the mover shaft has the end surface of the mover shaft on the valve body side or the valve body. It has a spiral end face that can contact the end face on the mover shaft side. For this reason, when the first or second stator sucks the mover body, the first and second urging means expand and contract to cause relative rotation of the valve body and the mover shaft, thereby causing the valve body of the mover shaft to rotate. Or the spiral end surface of the valve body, or the end surface of the valve body on the mover shaft side, and the distance between the valve body and the mover shaft is reduced.

According to the fourth aspect of the present invention, the third urging means adjusts the valve clearance in a direction in which the apparent shaft length including the mover shaft and the valve clearance adjusting member becomes longer. Since the member is biased, when the first stator sucks and holds the mover body, if there is a valve clearance (plus),
Works to eliminate valve clearance.

According to the valve driving device of the fifth aspect of the present invention, the first inner wall forming a hollow space in the axial direction at the center of the end of the valve body on the mover shaft side, and the valve of the mover shaft. A second inner wall that forms a hollow space in the axial direction at the center of the body-side end, and a third inner wall that forms a hollow space in the axial direction at the center of the valve clearance adjusting member are loosely fitted. Since the shaft member is provided, the spiral end faces of the valve clearance adjustment member and the mover shaft that come into contact with each other can slide around the shaft member without shifting in the radial direction. In addition, the valve body and the shaft of the mover shaft are prevented from tilting, and a lateral load is prevented from being generated in the bearing portion of the valve body and the mover shaft. Therefore, friction loss and power consumption due to reciprocating motion of the valve body and the mover shaft can be reduced, and stable operation can be obtained.

According to the valve driving device of the sixth aspect of the present invention, the distance changing means constitutes a lash adjuster for reducing the valve clearance to zero. A change in clearance due to wear of the member can be compensated.
Therefore, it is possible to reduce the influence of the change of the use environment temperature and the use deterioration, and obtain a stable operation.

According to the valve driving device of the present invention, the period from when the engine is stopped to when the first or second stator attracts the mover body at the time of cold start is defined as:
Excitation vibration changing means is provided to make the period longer than the period until the first or second stator attracts the mover body when the engine is started at room temperature. An increase in valve clearance caused by a difference in thermal expansion between the cylinder head, the housing, the valve body, and the mover shaft is restored by the temperature decrease after the engine is stopped. However, by performing the resonance excitation vibration of the valve driving device for a longer time at the next cold start than at the normal temperature start of the engine, the negative valve clearance due to the above-mentioned temperature drop can be eliminated.

[0020]

Embodiments of the present invention will be described below with reference to the drawings. 1 to 4 show a valve driving device according to an embodiment of the present invention. The valve driving device 100 of the present embodiment is a valve driving device that drives an intake valve of an engine by electromagnetic force. FIG. 2 shows a state in which the valve body 1 is half-open when no power is supplied.

The valve body 1 shown in FIG. 2 is controlled at a predetermined timing to open and close an intake port 3 for supplying fuel and air to a combustion chamber 2 of the engine. The valve body 1 is moved up and down in the axial direction by a stem 11 formed to extend toward a spring accommodating chamber 40 formed in the engine block 4. As shown in FIG. 1, an end portion 11a of the stem 11 has an end face 8 of a valve clearance adjusting member 81 described later.
An end surface 11b which can be brought into contact with 1b, and an inner wall 11c as a first inner wall which is formed at the center of a hollow space in the axial direction and into which a pin 83 described later is loosely fitted are formed. The valve body 1 has a stem guide 5 for guiding the movement in the axial direction.
Slidably held by the engine block 4.

In the spring accommodating chamber 40, a first spring 41 as a first urging means and a second spring 71 as a second urging means are accommodated. The first spring 41 is a compression coil spring. One end of the first spring 41 is provided on an inner bottom surface 65 of a spring groove 64 formed in a lower housing 63 described later.
And the other end abuts against the retainer 42. Since the retainer 42 is fixed to an end 11a of the armature shaft 22 described later by the cotter 45, the first spring 41 urges the valve body 1 in the valve opening direction.

The second spring 71 is a compression coil spring, one end of which contacts the lower retainer 72, and the other end of which contacts the inner bottom surface 46 of the spring accommodating chamber 40. Since the lower retainer 72 is fixed to the end 11a of the stem 11 of the valve body 1 by the cotter 75, the second spring 71 urges the valve body 1 in the valve closing direction. The winding direction of the second spring 71 is opposite to that of the first spring 41. Here, it is known that the coil springs whose end faces are not restricted from rotating in the circumferential direction rotate with each other in the direction opposite to the winding direction with elongation, and rotate with each other in the winding direction when contracted. For this reason, the retainer sides of the opposing compression coil springs rotate in opposite directions with expansion and contraction. In the first embodiment, for example, the first spring 41 is wound right, and the second spring 71 is wound left. As described above, the retainer sides of the opposing compression coil springs rotate in directions opposite to each other as they expand and contract. For example, when the first spring 41 is extended, the up retainer 42 and the armature shaft 22 are viewed from the right side when viewed from the valve body 1 side. The rotational torque is transmitted in the direction of rotation. At this time, the rotating torque is transmitted to the lower retainer 72 and the valve body 1 pressed against each other in a direction to rotate leftward.

As shown in FIGS. 1 and 3, the distance changing means 80 includes a valve body 1 and an armature shaft 2.
2 that changes the distance between the valve body 1 and the armature shaft 22 by using the relative rotation generated in the valve body 2, and includes a valve clearance adjusting member 81, a third spring 82, and a pin 83 for clearance fit. ing.

The valve clearance adjusting member 81 is provided at a connection portion between the valve body 1 and the armature shaft 22, has a substantially hollow cylindrical shape, and has an end surface on one end of the armature shaft 22 on the valve body 1 side. 22
b, and a stepped portion 81d that can contact a stepped portion 22d formed at an end 22a of the armature shaft 22 on the valve body 1 side, and a valve body at the other end. 1 of the armature shaft 22, that is, an end face 81 b that can abut on the end face 11 b of the stem 11.
have. Assuming that the helical angle of the spiral end face 81a is θ, θ is as small as about 1 mm in one round of the φ5 mm shaft, so that the end face does not slip due to the normal end face pressing in consideration of the friction coefficient between metals. Further, the valve clearance adjusting member 81 has an inner wall 81c as a third inner wall formed at the center in a hollow space in the axial direction, and a pin 83 is loosely fitted to the inner wall 81c.

The third spring 82 as the third biasing means is a torsion coil spring, one end of which is fixed to the armature shaft 22 and the other end of which is fixed to the valve clearance adjusting member 81. ing. Third
Spring 82 urges the valve clearance adjusting member 81 in a direction in which the step portion 81d is separated from the step portion 22d. That is, the third spring 82 urges the valve clearance adjustment member 81 in a direction in which the apparent shaft length including the armature shaft 22 and the valve clearance adjustment member 81 increases. The urging force of the third spring 82 is set to be negligibly smaller than the urging forces of the first and second springs 41 and 71.

The pin 83 as a shaft member is connected to an inner wall 22c of the armature shaft 22 and an inner wall 1 of the stem 11 to be described later.
1c and the inner surface of the valve clearance adjusting member 81 are loosely fitted. Therefore, the pin 83 is connected to the valve body 1
Of the stem 11 and the armature shaft 22 can be prevented to reduce the sliding resistance, thereby reducing the friction loss and power consumption due to the reciprocating motion of the valve body 1 and the armature shaft 22 and obtaining a stable operation. be able to.

The housing 60 includes an upper housing 61 having a substantially cylindrical shape and a middle housing 6 having a substantially cylindrical shape.
2 and a lower housing 63 having a substantially cylindrical shape.
It is fitted and fixed to the inner wall of the engine block 4 forming the spring accommodating chamber 40. The armature 20, the upper core 30 as a first stator, the lower core 50 as a second stator, a damper means 90, and a support arm 101 are housed in the housing 60.

The armature 20 as a mover comprises an armature main body 21 and an armature shaft 22. The armature body 21 is disposed between the upper core 30 and the lower core 50, and is made of a disk-shaped magnetic material such as iron.

The armature shaft 22 as a mover shaft has one end fitted into a substantially central portion of the armature main body 21 and joined to a support arm 101 via a connecting member 102 described later, and the other end. 22a is an end 1 of the stem 11 of the valve body 1 via the distance changing means 80.
1a.

The valve body 1 of the armature shaft 22
A valve clearance adjusting member 81 is provided on the side end 22a.
The end surface 22b that can contact the spiral end surface 81a of the above, the step portion 22d that can contact the step portion 81d of the valve clearance adjusting member 81, and the pin 83 that is formed in the center in a hollow space in the axial direction and is loosely fitted. Inner wall 22c as a second inner wall
Are formed. End face 22b and step 22d
The helical end face 81 is formed such that the end face 22b is in close contact with the helical end face 81a and slips between the helical end face 81a.
a and the shape corresponding to the step portion 81d.

The upper core 30 includes an upper housing 61
And is formed of a magnetic material such as iron. An upper coil 31 as a first coil portion is wound inside the upper core 30. When the upper coil 31 is energized, the upper core 30 attracts the armature body 21 and generates an electromagnetic force for moving the armature 20 and the valve body 1 in the valve closing direction.

The lower core 50 is housed in the lower housing 63, and is disposed opposite the upper core 30 with the armature body 21 interposed therebetween. The lower core 50 is formed of a magnetic material such as iron. A lower coil 51 as a second coil unit is wound inside the lower core 50. When the lower coil 51 is energized, the lower core 50 sucks the armature main body 21 and moves the armature 20 in the valve opening direction.
And an electromagnetic force for moving the valve body 1.

A middle housing 62 is provided between the upper core 30 and the lower core 50, and the amount of movement of the armature 20 is restricted by the thickness of the middle housing 62. Here, the armature 20 and the upper core 30
, The upper coil 31, the lower core 50, and the lower coil 51 constitute an electromagnetic actuator.

The damper means 90 exerts a damper function immediately before the armature main body 21 is seated on the upper core 30 or the lower core 50, and has an outer ring 92, an inner ring 93 provided in a cylindrical housing 91, and
Movable films 94 and 95 and movable cylinder 96 formed of rubber material
have.

The outer ring 92 is fixed to the inner peripheral wall of the housing 91. The outer ring 92, the inner ring 93 and the movable films 94, 9
Reference numeral 5 denotes a sealed container. This sealed container is filled with hydraulic oil. The movable cylinder 96 is formed with an annular projection 99 that can abut against annular members 97 and 98 fitted at a predetermined interval in the axial direction of the armature shaft 22. The movable films 94 and 95 and the movable cylinder 96 constitute a movable member.

A support arm 101 and a connecting member 102 are provided at an end of the armature shaft 22 on the side opposite to the valve body. The support arm 101 is made of an elastic member such as a leaf spring. One end is fixed to an end of the upper housing 61 on the side opposite to the engine block, and the other end is connected to the connecting member 10.
It is fixed to 2. The support arm 101 is provided point-symmetrically with respect to the center axis of the armature shaft 22. Further, since the urging force of the first and second springs 41 and 71 is set to be larger than the hysteresis of the deformation force accompanying the reversal of the deformation direction of the support arm 101, the support arm 1
The hysteresis of the deformation force of 01 is negligibly small. Therefore, the hysteresis of the deformation force of the support arm 101 is smaller than the hysteresis of the Coulomb friction of the conventional slide bearing. Also, the upper housing 6 of the support arm 101
A lift sensor (not shown) is provided in the vicinity of the mounting portion 1 and can detect the amount of movement of the armature shaft 22 based on the amount of elastic deformation of the support arm 101, such as a strain gauge. By arranging the lift sensor on the support arm 101, it is not necessary to secure a special installation place for the lift sensor.

The connecting member 102 is formed by the armature shaft 2
2 is connected to the support arm 101, for example, by fitting into a not-shown circumferential groove formed in the armature shaft 22, for example, to allow rotation about the axis of the armature shaft 22, and supporting the armature shaft 22. The movement in the axial direction with respect to the arm 101 is restricted. For this reason, the backlash in the axial direction of the armature shaft 22 can be prevented, and the operation stability can be improved.

In the valve driving apparatus 100 having the above-described structure, when the upper coil 31 and the lower coil 51 are not energized, the armature main body 21 is connected to the upper core 30 and the lower core 5.
0 so that the first spring 41
The set load of the second spring 71 is adjusted. At this time, the valve body 1 is in a half-open state as shown in FIG. During the operation of the engine, the upper coil 31 and the lower coil 51 are alternately energized, and the valve is repeatedly closed and opened.

Next, the operation of the distance changing means 80 will be described.
This will be described with reference to FIGS. First, when the upper core 30 sucks the armature main body 21 to contract the first spring 41 and expand the second spring 71, the valve clearance is adjusted in accordance with the upward movement of the armature shaft 22 in FIGS. The member 81 has a rightward direction from the end face 11b of the stem 11 and an armature shaft 22.
From the end face 22b, a rotational torque for rotating in the left direction is transmitted. Since the stem 11 and the armature shaft 22 are pressed against each other, if the above-described leftward rotation torque is T _s , T _s is represented by the following equation. T _S = T _SP · D _SP / D _S + F sin θ · cos θ × D _S / 2 where T _SP is a rotational torque for rotating one end face of the third spring 82 to the left. And D
_SP is the center diameter of the third spring 82, and _DS is
The center diameter of the spiral end face 81a, θ is the spiral end face 8
This is the vine winding angle of 1a.

From FIG. 5, (T _SP · D _SP / D _S · cos θ +
Fsin θ) / (D _S / 2) is the static friction force F _MS acting on the slope
== μFcos θ, slip on the slope. Here, μ is a coefficient of friction.

Assuming that the above-described rightward rotation torque is T _H , T _H is given by the following equation. Here _{T H = T SPH · D SP} / D SH ···, T SPH is a rotational torque to rotate the other end face of the third spring 82 to the right, D _SH
Is the center diameter of the end face 81b of the valve clearance adjusting member 81, equal to the center diameter D _S of the helical end surface 81a.

As shown in FIG. 5, when T _H / (D _S / 2) exceeds the static friction force F _MS = μFcos θ acting on the plane, the plane slides.
According to the above equations and the equations, when the respective rotational torques are compared, the rotational torque in the left direction is larger than the rotational torque in the right direction, and the user slides on a slope before sliding on a plane. As a result, the valve clearance adjustment member 81 slides on the end face 22b of the armature shaft 22, and the distance between the valve body 1 and the armature shaft 22 is reduced.

Next, the lower core 50 is attached to the armature main body 21.
When the first spring 41 expands and the second spring 71 contracts, the armature shaft 22 shown in FIGS.
3, the rotation torque T _{H for} rotating the valve 11 in the left direction is transmitted to the valve clearance adjusting member 81 from the end face 11b of the stem 11. Further, a rotation torque T _S expressed by the following equation for rotating the armature shaft 22 rightward is transmitted from the end face 22 b of the armature shaft 22. T _S = T _SP · D _SP / D _S -F sin θ · cos θ × D _S / 2 From the above expression and the expression, the rotational torque of the armature shaft 22 to be rotated leftward from the end face 11b of the stem 11 is larger. The rotation torque is larger than the rotation torque rotating rightward from the end face 22b, so that the vehicle slides on a flat surface without sliding on a slope. As a result, the valve clearance adjusting member 81 slides on the end face 11b of the stem 11, and the distance between the valve body 1 and the armature shaft 22 does not change.

The valve driving device 100 includes an armature 20
A pair of up and down movements correspond to the closing and opening movements of the valve, and the valve body 1 and the armature shaft 22 described above.
From the change in distance between the valve body 1 and the armature shaft 22, the distance between the valve body 1 and the armature shaft 22 tends to decrease in accordance with the operation of the valve driving device 100.

Next, the operation of the distance changing means 80 when the valve clearance occurs will be described with reference to FIGS. When the valve clearance increases from the state shown in FIG. 4A to the state shown in FIG. 4B, when the valve is closed, the distance between the spiral end face 81a of the valve clearance adjusting member 81 and the end face 22b of the armature shaft 22 is increased. There is a gap in However, since the valve clearance adjusting member 81 is urged by the third spring 82 shown in FIG. 3 in the direction in which the apparent shaft length extends, the valve clearance adjusting member 81 rotates so as to close the gap, As shown in FIG. 4C, the valve moves to a position where the valve clearance becomes zero.

Since the valve clearance adjusting member 81 is attached so as to be capable of relatively moving with respect to the armature shaft 22, the valve body 1 and the armature shaft 22 are connected to the first and second springs 4.
Even when the relative rotation is caused by the surge of 1 and 71, as described above, the distance between the valve body 1 and the armature shaft 22 is shortened at the position after the relative rotation, and the valve clearance. If there is (plus), the action of closing the valve clearance by rotating the valve clearance adjusting member 81 works without change. Therefore, the valve clearance adjusting member 81 relatively rotates with the point where the valve clearance is zero as a stable point, and functions as a zero lash adjuster. That is, the distance changing means 80 constitutes a lash adjuster that makes the valve clearance zero.

The engine block 4 and the housing 6
0, the increase in valve clearance caused by the difference in thermal expansion between the valve body 1 and the armature shaft 22 is restored by the temperature decrease after the engine is stopped. This phenomenon corresponds to having a negative valve clearance at the next cold start in the distance changing means 80. In order to eliminate the negative valve clearance, the upper core 30 or the lower core 50 during the cold start after the engine is stopped.
Is made longer than when the engine is at room temperature, for example, by slightly deviating the resonance frequency of resonance excitation adsorption. That is, by performing the resonance excitation vibration at the time of the cold start for a longer period of time than at the time of the normal temperature start of the engine, the negative valve clearance due to the above-mentioned temperature drop can be eliminated.

Next, the operation of the damper means 90 will be described. (1) When the valve is opened, the annular member 97 collides with the annular convex portion 99 immediately before the armature main body 21 is seated on the lower core 50. Then, the movable cylinder 96 moves downward in FIG. 2 together with the armature shaft 22, and the movable films 94 and 95 move downward in FIG. Then, a damper action is generated by the working oil filled in the sealed container. Therefore,
It is possible to prevent the armature main body 21 from directly colliding with the lower core 50 to generate a loud impact sound, or to prevent the armature main body 21 and the lower core 50 from being damaged.

(2) When the valve is closed, just before the armature main body 21 is seated on the upper core 30, the annular member 98 collides with the annular projection 99. And the armature shaft 22
At the same time, the movable cylinder 96 moves upward in FIG.
And 95 move upward in FIG. Then, a damper action is generated by the working oil filled in the sealed container. Therefore, the armature main body 21 is
Can be prevented from generating a loud impact sound due to direct collision with the armature, and from damaging the armature body 21 and the upper core 30.

In the embodiment of the present invention described above, the distance changing means 80 changes the distance between the valve body 1 and the armature shaft 22 using the relative rotation generated in the valve body 1 and the armature shaft 22. I do. Therefore, when the valve body 1 and the armature shaft 22 rotate during operation due to the surge of the first and second springs 41 and 71 and the valve body 1 and the armature shaft 22 rotate relative to each other, the distance changing means 80 causes the valve to rotate. The distance between the body 1 and the armature shaft 22 is changed. Therefore, since no external hydraulic pressure source is required, the valve clearance can be adjusted with a simple configuration without increasing the size of the device. In addition, power consumption can be reduced by suppressing an increase in the mass of the movable portion, and the responsiveness of the valve can be improved.

Further, in this embodiment, since the distance changing means 80 constitutes a lash adjuster for reducing the valve clearance to zero, the failure of the armature body 21 to be absorbed is prevented, and the valve body 1 and the valve clearance adjusting member 81 are prevented. It is possible to compensate for a change in clearance due to abrasion of members such as. Therefore, it is possible to reduce the influence of the change of the use environment temperature and the use deterioration, and obtain a stable operation.

In the embodiment of the present invention described above, the armature shaft 22 of the valve clearance adjusting member 81 is used.
Although the spiral end face 81a is formed at the end on the side of the valve body, a spiral end face may be formed at the end on the valve body side of the valve clearance adjusting member in the present invention.

Further, in this embodiment, the valve driving device 1 provided with the damper means 90 having a sealed container filled with hydraulic oil.
Although the present invention has been described with respect to an example in which the present invention is applied to 00, the present invention is applied to a valve driving device having damper means having means for supplying hydraulic oil to damper means and means for discharging hydraulic oil from the damper means. It is possible to do.

In the embodiment, the present invention is applied to the valve driving device that drives the intake valve by electromagnetic force. However, it is needless to say that the present invention can be applied to a valve driving device that drives the exhaust valve by electromagnetic force.

[Brief description of the drawings]

FIG. 1 is an enlarged view of a main part of FIG. 2, showing a distance changing unit of a valve driving device according to an embodiment of the present invention.

FIG. 2 is a longitudinal sectional view showing a state of the valve driving device according to an embodiment of the present invention when power is not supplied.

FIG. 3 is a schematic view showing a distance changing unit of the valve driving device according to one embodiment of the present invention.

FIGS. 4A, 4B and 4C are schematic diagrams for explaining the operation of the distance changing means of the valve driving device according to one embodiment of the present invention.

FIG. 5 is a schematic diagram for explaining an operation of a distance changing unit of the valve driving device according to one embodiment of the present invention.

FIG. 6 is a data diagram showing intake-side valve clearance in a conventional valve driving device.

FIG. 7 is a data diagram showing an exhaust-side valve clearance in a conventional valve driving device.

[Explanation of symbols]

 Reference Signs List 1 valve body 11 stem 11b end face 11c inner wall (first inner wall) 20 armature (movable element) 21 armature main body 22 armature shaft (movable element shaft) 22b end face 22c inner wall (second inner wall) 30 upper core (first stator) 31) Upper coil (first coil part) 41 First spring (first biasing means) 50 Lower core (second stator) 51 Lower coil (second coil part) 71 Second spring (second coil) Urging means) 80 distance changing means 81 valve clearance adjusting member 81a spiral end face 81b end face 81c inner wall (third inner wall) 82 third spring (third urging means) 83 pin (shaft member) 100 valve driving device

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3G016 BA38 CA04 CA07 CA27 CA32 CA45 DA01 DA11 DA16 DA23 GA00 3G092 AA11 DA01 DA02 DA07 DG02 DG09 FA00 FA09 FA14 FA48 FA49 FA50 GA01 3H106 DA07 DA25 DA32 DB02 DB12 DB26 DB32 DC02 DD07 EE04 EE22 EE48 GC29 KK17

Claims (7)

[Claims] 1. A mover having a valve body of an intake valve or an exhaust valve of an internal combustion engine, a mover shaft connected to the valve body, and a mover body made of a magnetic material, and sucking the mover body. A first stator having a first coil portion for generating an electromagnetic force for moving the valve body and the mover in a valve closing direction, and facing the first stator across the mover body. A second stator having a second coil portion arranged to generate an electromagnetic force for attracting the mover body and moving the valve body and the mover in a valve opening direction by suctioning the mover body; First urging means for urging the mover in the valve opening direction; and a first urging means disposed opposite to the first urging means for urging the valve body or the mover in the valve closing direction. 2 urging means, and the valve A distance changing unit that changes a distance between the valve body and the mover shaft by using a relative rotation generated in a body and the mover shaft. 2. The method according to claim 1, wherein the first and second urging means are coil springs, and the winding directions of the first and second urging means are opposite to each other. The valve driving device according to claim 1. 3. The distance changing means is provided at a connection portion between the valve body and the mover shaft, and is provided at an end surface of the mover shaft on the valve body side or on a position of the valve body on the mover shaft side. 3. The valve driving device according to claim 1, further comprising a valve clearance adjusting member having a spiral end surface capable of contacting the end surface. 4. A third urging means for urging the valve clearance adjusting member in a direction in which an apparent shaft length including the mover shaft and the valve clearance adjusting member becomes longer. The valve driving device according to claim 3, comprising: 5. A distance changing means comprising: a first inner wall forming a hollow space in the axial direction at a center of an end of the valve body on the side of the mover shaft; A second inner wall that forms a hollow space in the axial direction at the center of the end portion, a third inner wall that forms a hollow space in the axial direction at the center of the valve clearance adjusting member, The valve driving device according to claim 3, further comprising a shaft member that is loosely fitted to the second and third inner walls. 6. The valve driving device according to claim 1, wherein said distance changing means forms a lash adjuster for reducing a valve clearance to zero. 7. A period until the first stator or the second stator attracts the mover main body at the time of a cold start after the internal combustion engine is stopped is defined as the first period at the time of normal temperature start of the internal combustion engine. The valve according to any one of claims 1 to 6, further comprising: an excitation vibration changing unit that extends the period until the first stator or the second stator attracts the mover main body. Drive.