JP2001234718A - Electromagnetic intake and exhaust device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an electromagnetic intake and exhaust device capable of reducing generation of sound in opening and closing an intake and exhaust valve, and improving the control of the intake and exhaust valve. SOLUTION: Since the damper force applied to the exhaust valve open side is larger than the damper force applied to the exhaust valve closing side, the intake valve open side or the intake valve closing side, when the damper works with residual pressure in the exhaust cylinder, the damper means stands for a shock at high speed at first, and generation of sound at the time of opening the exhaust valve can surely be reduced. The damper action of the intake valve closing side is set not to be caused above a designated rotating speed of an engine, so that during high speed rotation of the engine, the intake valve can be closed early so as to rapidly compress air-fuel mixture in transition to the compression stroke of the engine. The moving speed of the piston 150 in the occurrence of the damper action is controlled so that a region where the moving speed of the piston 150 becomes constant is secured. Accordingly, the seating speed control of a valve body 1 can be controlled favorably.

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 an electromagnetic intake / exhaust 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 an electromagnetic intake / exhaust device that drives an intake valve or an exhaust valve of an engine by an electromagnetic force. In such an electromagnetic intake / exhaust device, by controlling the opening / closing timing of an intake valve or an exhaust valve so that intake or exhaust is performed well in accordance with operating conditions of the engine, the stability of the engine is improved, and the fuel efficiency is improved. It is possible to improve or 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 members of the intake valve and the exhaust valve are simultaneously opened (overlap period), the intake side is at a pressure lower than atmospheric pressure by the throttle, and the exhaust side is at a pressure higher than atmospheric pressure. May blow back to the intake side, resulting in worse combustion 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]

SUMMARY OF THE INVENTION
The requirements for the intake-side and exhaust-side valve timings described above can be satisfied by instructions from the 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 particular, it is difficult to reduce the noise generated when the valve member collides with the stopper and the valve seat when opening and closing the valve. The moving speed of the valve member of the electromagnetic intake / exhaust device is determined by the mass of the valve member, the urging force of the spring for urging the valve member, the voltage value of the applied voltage, and the timing of application. If the applied voltage is not controlled, the reciprocating speed of the valve member at the time of opening and closing is constant regardless of the engine speed, so that the same level of sound is generated during idle operation as during normal operation. Will be felt as noise.

Therefore, there has been proposed an electromagnetic air intake / exhaust device which reduces the generation of noise when the valve is opened and closed by using damper means for reducing the speed at which the reciprocating member approaches both ends in the reciprocating direction. Such a damper means of the electromagnetic air intake / exhaust device has the following features.

(1) The speed at which the reciprocating member approaches both ends in the reciprocating direction when the intake and exhaust valves are opened and closed is reduced. (2) With the damper means using fluid pressure, the reciprocating member operates at a short distance approaching both ends in the reciprocating direction when opening and closing the intake and exhaust valves, and locks the reciprocating member at both ends in the reciprocating direction. In this case, there is a section in which the speed energy is absorbed when the motor is driven, and a section in which the damper force due to the fluid pressure balances the external force. (3) The locking speed is made constant by locking the reciprocating member at both ends in the reciprocating direction during the constant speed section of (2).

[0010] However, in the above-mentioned conventional electromagnetic intake / exhaust device, although the structure of the damper means has been proposed, no consideration has been given to the damper action of the damper means over the entire operating range of the engine. In particular, if the damper function of the damper means is developed in the entire operation range of the engine, it may take time to move to the next operation before the intake and exhaust valves are fully closed and fully opened in the high speed range, which may cause inconvenience. It is conceivable to limit the return time of the reciprocating member by providing an orifice in the passage where the working fluid of the damper means flows, but there are cases where it is desired to make the damper function effective in the high speed range, and the control of the intake and exhaust valves is insufficient. Met.

SUMMARY OF THE INVENTION The present invention has been made to solve such a problem, and it is an electromagnetic type air intake / exhaust apparatus which reduces the generation of noise when opening / closing an intake / exhaust valve and improves the control of the intake / exhaust valve. The purpose is to provide.

[0012]

According to the electromagnetic intake / exhaust device of the present invention, when the intake / exhaust valve member reciprocates, the speed of the intake / exhaust valve member toward both ends of the reciprocal movement is reduced. This damper means has a characteristic of a damper action on the exhaust valve opening side different from a characteristic of a damper action on the exhaust valve closing side, the intake valve opening side or the intake valve closing side. For this reason, it is possible to reduce the generation of noise when opening and closing the intake and exhaust valves, and to control the opening and closing timing of the intake valve or the exhaust valve so that the intake or exhaust is favorably performed according to the operating conditions of the engine. Stability, fuel efficiency, or exhaust emissions can be reduced.

According to the electromagnetic intake / exhaust device of the second aspect of the present invention, the damper means is configured such that the damper force when the damper acts on the exhaust valve opening side is on the exhaust valve closing side, the intake valve opening side or the intake valve closing side. Since the damper force is larger than the damper force at the time of the damper action, the damper means can withstand the impact due to the initially large speed at the time of the damper action when there is residual pressure in the exhaust cylinder. Therefore, generation of noise when the exhaust valve is opened can be reliably reduced.

According to the third aspect of the present invention, when the intake / exhaust valve member approaches both ends in the reciprocating movement direction, the movable member moves together with the intake / exhaust valve member so that the working fluid is fluidized. Flow through the resistance passage. Therefore,
Since the speed at which the intake / exhaust valve member approaches both ends in the reciprocating movement direction is reduced, noise generated when the intake / exhaust valve member is locked at both ends in the reciprocating movement direction can be reduced.

Further, since the working fluid is sealed in the sealed container, there is no need to supply the working fluid to the damper means and to discharge the working fluid from the damper means. Therefore, since the damper means can be modularized, the mounting of the damper means is easy.

Further, the fluid resistance means is characterized in that the gap of the fluid resistance passage on the exhaust valve opening side is smaller than the gap of the fluid resistance passage on the exhaust valve closing side, the intake valve opening side or the intake valve closing side. Generation of sound at the time can be reliably reduced.

According to the electromagnetic intake / exhaust device of the fourth aspect of the present invention, the movable member has a movement start position on the exhaust valve opening side on the exhaust valve closing side, the intake valve opening side or the intake valve closing side. Since it is farther from the fully open position, the generation of noise when the exhaust valve is opened can be reliably reduced.

According to the electromagnetic intake / exhaust device of the fifth aspect of the present invention, the intake / exhaust valve member allows the valve not to be opened to the fully open position when the rotation speed of the engine is high. Since the amount of the exhaust valve that does not fully open due to the operation of the damper means is less than 0.5% of the total valve lift, it is possible to reduce the generation of noise when the exhaust valve is opened without substantially reducing the performance of the engine. .

According to the electromagnetic intake / exhaust device of the present invention, when the intake / exhaust valve member reciprocates, the damper means for reducing the speed of the intake / exhaust valve member toward both ends of the reciprocation is provided by the intake air The characteristic of the damper action on the valve closing side is
It is different from the characteristic of the damper action on the exhaust valve closing side or the exhaust valve opening side. For this reason, it is possible to reduce the generation of noise when opening and closing the intake and exhaust valves, and to control the opening and closing timing of the intake valve or the exhaust valve so that the intake or exhaust is favorably performed according to the operating conditions of the engine. Stability, fuel efficiency, or exhaust emissions can be reduced.

According to the electromagnetic intake / exhaust device of the present invention, the damper means is set so that the damper function on the intake valve closing side does not appear above a predetermined rotational speed of the engine. For this reason, the intake valve can be quickly closed at the time of high engine rotation, and the air-fuel mixture can be rapidly compressed at the time of transition to the compression stroke of the engine.

According to the electromagnetic intake / exhaust device of the present invention, when the intake / exhaust valve member approaches both ends in the reciprocating direction, the movable member moves together with the intake / exhaust valve member so that the working fluid is fluidized. Flow through the resistance passage. Therefore,
Since the speed at which the intake / exhaust valve member approaches both ends in the reciprocating movement direction is reduced, noise generated when the intake / exhaust valve member is locked at both ends in the reciprocating movement direction can be reduced.

Further, since the working fluid is sealed in the sealed container, there is no need to supply the working fluid to the damper means and to discharge the working fluid from the damper means. Therefore, since the damper means can be modularized, the mounting of the damper means is easy.

Further, after the piston moves in one direction together with the movable member, the piston does not move in the opposite direction together with the movable member. The piston is urged in the opposite direction by the urging force of the urging means, and the working fluid flows through the one-way orifice member by the differential pressure generated in the fluid chamber partitioned by the piston, so that the piston tends to return to the original position. The return speed is determined by the flow path area and flow path length of the one-way orifice if the temperature of the working fluid is the same. Therefore, the piston can be returned at a desired speed by adjusting the flow path area and the flow path length of the one-way orifice. If the return speed of the piston is constant, the position at which the piston returns is determined by the time until the piston starts returning and starts moving in one direction again with the movable member. This time increases or decreases depending on the reciprocating speed of the reciprocating member and the movable member. Therefore, by adjusting the flow path area and flow path length of the one-way orifice,
The piston can be returned to a desired position according to the reciprocating speed of the intake / exhaust valve member and the movable member.

According to the electromagnetic intake / exhaust device of the ninth aspect of the present invention, the damper means moves the piston when the damper function is exerted so that an area where the piston moves at a constant speed is secured. Is controlled. Therefore, by controlling the application time of the applied voltage, the seating speed control of the intake / exhaust valve member can be favorably performed.

According to the electromagnetic intake / exhaust device of the tenth aspect of the present invention, the intake / exhaust valve member is seated without changing the control speed range from the moving speed of the piston when the damper function of the damper means appears. Is controlled. Therefore, the intake and exhaust valves can be controlled well.

[0026]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 4 shows an electromagnetic air intake and exhaust device according to an embodiment of the present invention. The electromagnetic intake / exhaust device 100 of this embodiment is an electromagnetic intake / exhaust device that drives an intake valve of an engine by electromagnetic force. FIG. 4 shows a state in which the valve body 1 is half-open when power is not supplied. An electromagnetic intake / exhaust device that drives an exhaust valve of an engine by an electromagnetic force is obtained by changing a characteristic of a damper function of a damper unit 90 in an electromagnetic intake / exhaust device 100 shown in FIG.
Other configurations are the same as those of the electromagnetic intake / exhaust device 100 shown in FIG.

A valve body 1 as an intake valve member is controlled to open and close an intake port 3 for supplying fuel and air to a combustion chamber 2 of the engine at a predetermined timing. The valve body 1
Spring accommodation room 40 formed in engine block 4
Is moved up and down in the axial direction by a stem 11 formed to extend toward. As shown in FIG.
1a, an end surface 11b that can be brought into contact with an end surface 81b of a valve clearance adjusting member 81 described later, and an inner wall 11c that 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. Have been. Also valve body 1
Is slidably held with respect to the engine block 4 by a stem guide 5 for guiding movement in the axial direction.

A first spring 41 and a second spring 71 are accommodated in the spring accommodating chamber 40. The first spring 41 is a compression coil spring, one end of which contacts an inner bottom surface 65 of a spring groove 64 formed in a lower housing 63 to be described later via a spring seat 66, and the other end thereof is Apparitainer 42
Is in contact with 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 as they expand and contract. In the present 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 FIG. 5, the distance changing means 80
The distance between the valve body 1 and the armature shaft 22 is changed by using the relative rotation generated in the valve body 1 and the armature shaft 22. The valve clearance adjustment member 81, the third spring 82, and the clearance fit are used. Pins 83.

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 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 is a torsion coil spring, one end of which is connected to the armature shaft 2.
2 and the other end is fixed to a valve clearance adjusting member 81. The third spring 82 biases 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
Of the valve clearance adjusting member 81 in the direction in which the apparent shaft length including the armature shaft 22 and the valve clearance adjusting member 81 becomes longer.
Is energizing. 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 is loosely fitted to the inner wall 22c of the armature shaft 22, the inner wall 11c of the stem 11, and the inner wall of the valve clearance adjusting member 81, which will be described later.
Therefore, the pin 83 can prevent the axis of the stem 11 of the valve body 1 and the armature shaft 22 from tilting to reduce the sliding resistance, and reduce the friction loss and the power consumption due to the reciprocating motion of the valve body 1 and the armature shaft 22. Reduction and stable operation can be obtained.

The housing 60 includes a substantially cylindrical upper housing 61 and a substantially cylindrical middle housing 6.
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. In the housing 60, the armature 20, the upper core 30, and the lower core 5 are provided.
0, damper means 90, and support arm 101 are accommodated.

The armature 20 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 has one end fitted into a substantially central portion of the armature main body 21 and joined to the support arm 101 via a connecting member 102 described later, and the other end 22a connected to the distance changing means. It is connected to the end 11a of the stem 11 of the valve body 1 via 80.

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 is formed. The helical end face 81a and the stepped portion 81d are arranged such that the end face 22b is in close contact with the helical end face 81a and slips between the end face 22b and the helical end face 81a.
It has a shape corresponding to d.

The upper core 30 includes an upper housing 61
And is formed of a magnetic material such as iron. An upper coil 31 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 to the upper core 30 with the armature main body 21 interposed therebetween. The lower core 50 is formed of a magnetic material such as iron. A lower coil 51 is wound inside the lower core 50. When the lower coil 51 is energized, the lower core 50 attracts the armature body 21 and generates an electromagnetic force for moving the armature 20 and the valve body 1 in the valve opening direction.

A middle housing 62 is provided between the upper core 30 and the lower core 50. The 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 drive unit.

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. The C-shaped annular members 97 and 98 are fitted at predetermined intervals in the axial direction of the armature shaft 22.

A male screw 91a is formed on the outer peripheral wall of a cylindrical housing 91, and the housing 91 is screwed to a support member (not shown). Outer ring 92
It is formed of an upper member 113 and a lower member 114, and is fixed to the inner peripheral wall of the housing 91. Inner ring 9
3 is formed by an upper member 116 and a lower member 117. A movable wheel 122 is provided between the upper member 113 and the upper member 116. The movable film 94 made of a rubber material includes an upper member 113, an upper member 116, and a movable wheel 122.
And each is baked. The movable wheel 123 is arranged between the lower member 114 and the lower member 117.
The movable film 95 made of a rubber material is baked on the lower member 114, the lower member 117, and the movable wheel 123, respectively. The outer ring 92, the inner ring 93, and the movable films 94 and 95 constitute a sealed container, and the sealed container is filled with hydraulic oil.

The movable tube 96 has a tube portion 131, a lower flange portion 132, and an upper flange portion 135. Tube part 1
An annular protrusion 99 is formed substantially at the center in the axial direction of 31 toward the center. The upper flange portion 135 is the movable wheel 122
In addition, an upper flange portion 135 is screwed to the outer periphery of the cylindrical portion 131 opposite to the lower flange portion 132 so that the lower flange portion 132 contacts the movable ring 123. The movable films 94 and 95, the movable wheels 122 and 123, and the movable cylinder 9 described above.
Reference numeral 6 denotes a movable member.

The outer peripheral wall and the inner peripheral wall of the bidirectional orifice member 140 are fitted to the outer ring 92 and the inner ring 93, respectively, and are accommodated between the movable film 94 and the movable film 95. The bidirectional orifice 141 as a fluid resistance passage is formed to penetrate the bidirectional orifice member 140 in the moving direction of the armature shaft 22, and
0 communicates with the second hydraulic oil chamber 161. Further, the bidirectional orifice member 140 has a recess 14 which opens in the direction in which the armature shaft 22 reciprocates.
2 are formed. A total of two bidirectional orifices 141 are provided on the opposite side in the radial direction.
Are alternately opened in each direction of reciprocating movement, and a total of six openings are formed. The bidirectional orifice 141 and the sliding clearance 163 are formed such that a damper force generated when hydraulic oil flows through the bidirectional orifice 141 and a sliding clearance 163 described later acts on the axis of the armature shaft 22. The C-shaped stoppers 145 and 146 are fitted at both axial ends of the bidirectional orifice member 140, respectively. Stoppers 145 and 146 are springs 15
5 restricts the movement of the piston 150 due to the urging force.

The piston 150 is formed in a cylindrical shape with a bottom, and is supported by a concave portion 142 as a cylinder so as to be able to reciprocate. A through hole 152 is formed at the bottom of the piston 150.
Are formed. One end of the spring 155 abuts the inner peripheral bottom of the recess 142, and a long plate-shaped spring seat 156 is provided.
Is in contact with the other end. A leaf spring 157 having a U-shaped cross section is joined to the spring seat 156. Spring 155
Urges the spring seat 156, the disc 158 as the check valve member is urged toward the bottom of the piston 150 by the leaf spring 157. When the disc 158 is in close contact with the bottom of the piston 150, the through hole 152 and the one-way orifice 151 are closed. One-way orifice member 159 formed of a resin material is accommodated in through hole 152. The one-way orifice member 159 has a rectangular one-way orifice 151 formed from the outer periphery toward the center.

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 device 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.

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.

Since the valve clearance adjusting member 81 is mounted 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, when the armature shaft 22 moves downward in FIG. 3, the annular member 97 collides with the annular projection 99. Then, the movable cylinder 96 moves downward in FIG. 3 together with the armature shaft 22. Then, the movable wheel 122 and the movable membrane 94 move downward in FIG. 3, and the volume of the first hydraulic oil chamber 160 decreases. In addition, the movable wheel 123 and the movable film 95 move downward in FIG. 3, and the volume of the second hydraulic oil chamber 161 increases. The hydraulic oil moves from the first hydraulic oil chamber 160 to the second hydraulic oil chamber 161 through the bidirectional orifice 141.

When the movable cylinder 96 moves downward in FIG. 3, the piston 150 in contact with the movable
And the volume of the piston chamber 162 decreases.
The hydraulic oil in the piston chamber 162 moves to the first hydraulic oil chamber 160 through a sliding clearance 163 as a fluid resistance passage formed between the recess 142 and the piston 150.

As described above, when the movable cylinder 96 moves downward in FIG. 3 together with the armature shaft 22, the hydraulic oil is supplied to the bidirectional orifice 141 and the sliding clearance 163.
Flow, the movable cylinder 96 receives the damper force, so that the moving speed of the armature shaft 22 and the movable cylinder 96 decreases.

(2) When the armature shaft 22 moves upward in FIG. 3 when the valve is closed, the piston 150 shown in FIG.
The hydraulic oil flows through the sliding clearance 163 and the bidirectional orifice 141 formed between the piston 150 and the concave portion 142 which open in the opposite direction, and the movable cylinder 96 receives a damper force. The moving speed of the shaft 22 and the movable cylinder 96 decreases. At this time, the piston 150, which has moved downward in FIG. 3 together with the armature shaft 22 and the movable wheel 122, is biased upward in FIG. 3 by the biasing force of the spring 155, so that the pressure in the first hydraulic oil chamber 160 is increased. Since the pressure is higher than the pressure in the piston chamber 162, the disk 158
Move away from the bottom of the Then, the working oil flows from the first working oil chamber 160 to the piston chamber 162 through the one-way orifice 151, and the piston 150 returns to the upper side in FIG. Here, since the damper unit 90 is used as a damper unit for the intake valve of the engine, the moving time of the armature shaft 22 to the end by the damper unit 90 is constant regardless of the engine rotation speed. This is undesirable because the valve opening angle or the valve closing angle becomes long in the operating region where the engine rotation speed is high. In order to avoid this, the return position of the piston 150 is set to a position short of being locked by the stoppers 145 and 146 at the time of high engine rotation. The diameter of the one-way orifice 151 can be selected so that, for example, when the engine rotation speed is 2000 rpm or more, the one-way orifice 151 does not return to the position where it is locked by the stoppers 145 and 146.

The damping characteristics of the damper means 90 for reducing the moving speed of the armature shaft 22 include the diameter and length of the bidirectional orifice 141, the clearance and length of the sliding clearance 163, the stroke length of the movable cylinder 96, and the operation. It is determined by the viscosity of the oil and the like. Therefore,
In the damper means of the electromagnetic intake and exhaust device that drives the exhaust valve of the engine by electromagnetic force, by changing the diameter and length of the bidirectional orifice, the clearance and length of the sliding clearance, and the stroke length of the movable cylinder, At the time of the damper action when there is residual pressure in the exhaust cylinder, the damper force at the time of the damper action on the exhaust valve opening side is reduced to the exhaust valve closing side, the intake valve opening side, or the intake valve so that the damper means can withstand the initially large speed. It can be set to be larger than the damping force when the damper acts on the valve closing side. Since the viscosity of the hydraulic oil increases and decreases according to the temperature, the damping characteristic of the damper means fluctuates due to a change in the viscosity of the hydraulic oil. Therefore, in order to prevent the fluctuation of the damping characteristic due to the fluctuation of the viscosity of the hydraulic oil due to the temperature change,
It is possible to form each member with materials having different coefficients of thermal expansion.

Next, the relationship between the damper force and the external force during the operation of the damper will be described. The equation of motion of the armature and the pressure of the damper piston chamber can be approximately expressed by the following equations. ^{m · d 2 x / dt 2} + c · dx / dt + kx = -AP + F E -F f ··· dP / dt = KA / V · dX / dt-dQ / dt ^{··· dQ / dt = πh 3 /} 12μL · (1- (e / h) 2) · (P-P 0) ··· m: spring-mass system mass, c: coefficient of viscosity, k: spring constant,
x: Armature displacement A: Damper piston area, P: Damper piston chamber pressure dP / dt: Damper piston chamber pressure change rate, F _E : Electromagnetic force, F _f : Dry friction force K: Bulk modulus of hydraulic oil in damper piston chamber , V: damper piston chamber volume dQ / dt: leakage flow rate from damper piston gap, h:
Damper piston gap μ: viscosity of working oil in the damper piston chamber, L: damper piston seal length e: eccentricity, P ₀ : atmospheric pressure Here, the equation and the equation are established after the damper piston abuts.

Using the above formulas, formulas and formulas, it is possible to construct a simulation of an electromagnetic intake / exhaust device provided with a damper means. Here, the lift amount, the armature speed, and the damper piston chamber pressure when the armature is seated during the damper operation will be described using the simulation results shown in FIG. FIG. 2 shows the initial velocity per damper piston at 0.6 m / s and 0.2 m / s. The simulation is started from a state where the valve body is kept at the open position. At this time, if the hold current that keeps the valve body in the open position is turned off,
As the eddy current generated in the armature and the lower core disappears, the electromagnetic force decreases, and the damping motion of the spring mass system starts.
When the armature has passed the neutral position, a voltage is applied to the upper coil to generate an electromagnetic force for attracting the valve body to the closed position. The armature lifts due to the catch current and the catch electromagnetic force generated by the applied voltage, and is displaced larger than the damping motion trajectory of the spring mass system, and the energy of the spring mass system increases to the speed at which the spring mass system collides with the upper core. It is all-electronic control to accurately control the increased energy and seat the vehicle at a speed of several cm / s without failure. Damper control is to cause a collision with the damper means at a relatively high speed, and to seat without failure at a speed of several cm / s using the energy absorbing power of the damper means.

The following can be said from the simulation results shown in FIG. a. As the speed at the start of contact with the damper piston is higher, the damper stroke required for the speed energy absorption section is longer, and the constant speed stroke is shorter. b. The greater the speed at which the damper piston starts to contact, the shorter the time from when the hold current is turned off to when it is seated. c. The engine rotation speed at which the speed control by the damper means is not effective is the rotation speed at which the engine is seated during the speed energy absorption section (if the speed is too high, the engine will be seated before absorbing the speed energy).

Further, from the above equations, the equations and the equations and the simulation results shown in FIG. 2, the following can be considered. In the constant velocity section shown in FIG. 2, after the velocity energy absorption section ends and the inertia term m · d ² x / dt ² becomes smaller in the equation (the terms c · dx / dt and F _{f become} negligible). small), kx = -AP + F _E becomes damper piston chamber pressure P determined by relations appear. x may be considered as substantially constant since it does not vary greatly at the position where feeling that damper action, and P = 1 / A · (kx -F E). Damper piston chamber pressure P is gradually increased by receiving the electromagnetic force F _E is changed by a slight displacement of the lift amount x of the armature. Since the leak flow rate dQ / dt from the damper piston gap is determined from the equation by this pressure P,
dQ / dt = 0 and thinking, V = dx / dt = V / KA · dQ / dt = πVh 3 / 12μLKA next, d. Armature moving speed is 3 of piston clearance
It is proportional to the power.

FIG. 1 will be described based on the above considerations. First, the target value of the armature and the seating speed of the valve body of the electromagnetic intake and exhaust device provided with the damper means is equal to or less than the valve seating speed of the electromagnetic intake and exhaust device not provided with the damper means. The means for achieving this target value will be described below.

The characteristics of the damper action are set differently on the intake valve closing side, the intake valve opening side, the exhaust valve closing side, and the exhaust valve opening side. The intake valve closing side rapidly compresses the air-fuel mixture at the time of transition to the compression stroke of the engine, so that the constant speed section is not extended more than necessary. For this reason, the intake valve closing side is provided with a temperature-compensated orifice for restricting the return of the damper piston so that the damper effect does not appear above a predetermined rotation speed of the engine.

The damper piston gap on the exhaust valve opening side is made smaller than the damper piston gap on the exhaust valve closing side, the intake valve opening side or the intake valve closing side, and / or the starting position of the damper piston on the exhaust valve opening side is exhausted. Make the damper piston closer to the start position of the damper piston on the valve closing side, intake valve opening side or intake valve closing side (increase the damper stroke). To endure. Here, FIG. 6 shows the result of the seating control of the electromagnetic drive unit alone corresponding to the case where there is residual pressure in the exhaust cylinder. As can be seen from FIG. 6, when the exhaust valve is opened by the spring force, the residual pressure in the exhaust cylinder becomes a large resistance and causes loss of the potential energy stored as bending of the spring. It is a very difficult task to control the seating speed while supplementing this loss energy with electromagnetic force. As shown in FIG. 6, in the case of an electromagnetic air intake / exhaust device provided with a damper means, as shown in FIG. 6, for a large starting speed per damper piston (the damper stroke is so small that the starting speed per damper piston is almost the same as the seating speed) The gap of the damper piston is reduced so that the seating speed can be controlled.

The damper piston gap on the exhaust valve opening side is made smaller than the damper piston gap on the exhaust valve closing side, the intake valve opening side or the intake valve closing side, and / or the starting position of the damper piston on the exhaust valve opening side is exhausted. By setting the damper piston closer to the valve closing side, intake valve opening side or intake valve closing side than the starting position, it takes a long time to fully open the valve. (When the full valve lift is 8 mm, the damper stroke is at most about 100 μm, so that the engine performance is hardly affected). As a result, the armature seating speed on the exhaust valve opening side is smaller than the armature seating speed on the exhaust valve closing side, the intake valve opening side, or the intake valve closing side.

On the intake valve closing side, the rotation speed of the engine at which the speed control by the damper means is not effective is the rotation speed at which the engine is seated during the collision speed absorption period, and is higher than the piston full return rotation speed.

According to the simulation results shown in FIG. 2, there is a constant speed section after the speed energy absorption section, and it is as described above that the damper speed control is realized by sitting in this section. This means that the damper speed can be controlled if the damper piston returns by the necessary stroke for the speed energy absorption section, and can be realized in a short period (at a large rotation speed). In this case, since the rotation speed of the engine depends on the speed at which the damper piston starts to hit, the speed at which the engine hits is set to a low speed, and the control is shifted to the sitting speed control. Since the damper stroke is at most 0.1 mm, it is possible to control the seating speed in the section where the damper stroke in the speed energy absorption section remains in the voltage-on timing of the same voltage application timing control as the speed control at the start of the damper piston.

In the embodiment of the present invention described above, the characteristic of the damper function on the intake valve closing side is different from the characteristic of the damper function on the intake valve opening side, the exhaust valve closing side or the exhaust valve opening side. The characteristic of the damper action on the valve opening side is different from the characteristic of the damper action on the exhaust valve closing side, the intake valve opening side or the intake valve closing side. For this reason, it is possible to reduce the generation of noise when opening and closing the intake and exhaust valves, and to control the opening and closing timing of the intake valve or the exhaust valve so that the intake or exhaust is favorably performed according to the operating conditions of the engine. Stability, fuel efficiency, or exhaust emissions can be reduced.

Further, in this embodiment, since the damper force at the time of the damper action on the exhaust valve opening side is larger than the damper force at the time of the damper action on the exhaust valve closing side, the intake valve opening side or the intake valve closing side, the exhaust cylinder The damper means can withstand the impact due to the initially large speed during the operation of the damper when there is an internal residual pressure.
Therefore, generation of noise when the exhaust valve is opened can be reliably reduced.

Further, in the present embodiment, the damper function on the intake valve closing side is set so as not to be exerted at a speed equal to or higher than the predetermined rotational speed of the engine. For this reason, the intake valve can be quickly closed at the time of high engine rotation, and the air-fuel mixture can be rapidly compressed at the time of transition to the compression stroke of the engine.

Further, in this embodiment, the moving speed of the piston 150 when the damper function is exerted is controlled so that a region where the moving speed of the piston 150 is constant is secured. Therefore, by controlling the application time of the applied voltage, the seating speed control of the valve body 1 can be favorably performed.

Further, in the present embodiment, the piston 150 when the damper function of the damper means 90 is developed
The valve body 1 is controlled so as to be seated without changing the control speed range from the moving speed. Therefore,
The intake valve can be controlled well.

In the embodiment of the present invention described above, the armature shaft 22 of the valve clearance adjusting member 81
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.

In this embodiment, the housing 60 and the armature 20 have a circular shape. However, in the present invention, the housing and the armature may have a rectangular shape.

In the present embodiment, an example is described in which the present invention is applied to the electromagnetic air intake / exhaust device 100 provided with the damper means 90 having a sealed container filled with hydraulic oil. It is possible to apply the present invention to an electromagnetic air intake / exhaust device provided with a damper means provided with a means for supplying oil and a means for discharging hydraulic oil from the damper means.

[Brief description of the drawings]

FIG. 1 is a simulation diagram showing a relationship between an engine rotation speed and a seating speed of an intake / exhaust valve of an electromagnetic intake / exhaust device according to an embodiment of the present invention.

FIG. 2 is a simulation diagram showing a lift amount, a moving speed, and a fluid pressure in a damper unit when an intake / exhaust valve of an electromagnetic intake / exhaust device according to an embodiment of the present invention is seated.

FIG. 3 is a longitudinal sectional view showing a damper means of the electromagnetic air intake and exhaust device according to one embodiment of the present invention.

FIG. 4 is a longitudinal sectional view showing a state of the electromagnetic air intake and exhaust device according to one embodiment of the present invention when power is not supplied.

FIG. 5 is a longitudinal sectional view showing a distance changing means of the electromagnetic air intake and exhaust device according to one embodiment of the present invention.

FIG. 6 is a diagram showing a lift amount, a voltage, a fluid pressure in a damper means, and a lift amount on an exhaust valve opening side of an electromagnetic intake / exhaust device according to an embodiment of the present invention;
It is a data figure which shows a moving speed and electric current.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Valve body (suction and exhaust valve member) 11 Stem 20 Armature 21 Armature main body 22 Armature shaft 30 Upper core 31 Upper coil 41 First spring 50 Lower core 51 Lower coil 71 Second spring 80 Distance changing means 81 Valve clearance adjusting member 82 Third Spring 83 Pin 90 Damper means 94, 95 Movable membrane (movable member, sealed container) 96 Movable cylinder (movable member) 100 Electromagnetic intake / exhaust device 112 Outer ring (sealed container) 115 Inner ring (sealed container) 122, 123 Movable wheel (movable) Member, sealed container) 140 bidirectional orifice member 141 bidirectional orifice (fluid resistance passage) 150 piston 155 spring (biasing means) 158 disk (check valve member) 159 one-way orifice member 151 one-way orifice 16 3 Sliding clearance (fluid resistance passage)

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI theme coat ゛ (reference) // F16K 31/06 385 F16K 31/06 385A F term (reference) 3G018 AB09 BA38 CA12 DA65 EA04 EA31 FA07 GA31 GA32 3G092 AA11 DA01 DA02 DA07 EA03 FA14 GA18 HE01Z 3H106 DA07 DA25 DB02 DB12 DB26 DB32 DC02 DD04 EE33 FA08 GC07 GC29 KK12 KK17 3J069 AA39 AA50 CC09 EE01 EE02

Claims (10)

[Claims] An intake / exhaust valve member for intermittently connecting a combustion chamber with an intake passage or an exhaust passage of an internal combustion engine by reciprocating; an electromagnetic drive unit for driving the intake / exhaust valve member; And damper means for reducing the speed of the intake / exhaust valve member toward both ends of the reciprocation when the member reciprocates, wherein the damper means has a characteristic of a damper action on the exhaust valve opening side on the exhaust valve closing side, An electromagnetic air intake / exhaust device, which is different from a characteristic of a damper action on an intake valve opening side or an intake valve closing side. 2. The damper device according to claim 1, wherein a damper force at the time of a damper action on the exhaust valve opening side is larger than a damper force at the time of the damper action on the exhaust valve closing side, the intake valve opening side or the intake valve closing side. The electromagnetic air intake and exhaust device according to claim 1. 3. The sealed container according to claim 1, wherein the damper means includes: a sealed container that seals a working fluid; and the suction container moves together with the suction and exhaust valve member when the suction and exhaust valve member approaches both ends in the reciprocating direction. A movable member for moving the working fluid in the container, and a fluid resistance passage through which the working fluid in the sealed container flows, and the working fluid flows through the fluid resistance passage when the movable member moves together with the reciprocating member. Resistance means, wherein the fluid resistance means that the gap of the fluid resistance passage on the exhaust valve opening side is smaller than the gap of the fluid resistance passage on the exhaust valve closing side, the intake valve opening side or the intake valve closing side. 3. The electromagnetic air intake / exhaust device according to claim 2, wherein: 4. The movable member, wherein a movement start position on the exhaust valve opening side is farther from a fully open position than a movement start position on the exhaust valve closing side, the intake valve opening side, or the intake valve closing side. 3. The electromagnetic intake and exhaust device according to 3. 5. The electromagnetic intake / exhaust device according to claim 3, wherein the intake / exhaust valve member allows the valve not to open to the fully open position when the rotation speed of the internal combustion engine is high. 6. An intake / exhaust valve member that reciprocates to communicate between an intake passage or an exhaust passage of an internal combustion engine and a combustion chamber, an electromagnetic drive unit that drives the intake / exhaust valve member, and the intake / exhaust valve. And damper means for reducing the speed of the intake / exhaust valve member toward both ends of the reciprocal movement when the member reciprocates, wherein the damper means has a characteristic of a damper action on the intake valve closing side on the intake valve opening side. An electromagnetic intake / exhaust device characterized in that the characteristics of the damper action on the exhaust valve closing side or the exhaust valve opening side are different. 7. The electromagnetic intake / exhaust device according to claim 6, wherein the damper means is set so that a damper function on the intake valve closing side does not appear above a predetermined rotational speed of the internal combustion engine. 8. The sealed container, wherein the damper means comprises: a sealed container which seals a working fluid; and wherein the intake / exhaust valve member moves together with the intake / exhaust valve member when approaching both ends in the reciprocating direction. A movable member for moving the working fluid in the container, and a fluid resistance passage through which the working fluid in the sealed container flows, and the working fluid flows through the fluid resistance passage when the movable member moves together with the reciprocating member. A resistance means, a piston which moves in one direction together with the movable member, and which is housed in the sealed container and supports the piston in a reciprocating manner, and a side where the piston moves in one direction together with the movable member is closed. A biasing means for biasing the piston in a direction opposite to a direction in which the piston moves in one direction together with the movable member; A one-way orifice member having a one-way orifice attached to a through-hole penetrating the ton in the axial direction; and a biasing means for biasing the one-way orifice member toward the one-way orifice member. The electromagnetic intake / exhaust device according to claim 7, further comprising: a check valve member that prevents the one-way orifice from flowing in a biasing direction. 9. The damper means controls the moving speed of the piston when a damper action is exerted so that a region where the moving speed of the piston is constant is secured. 8. The electromagnetic intake and exhaust device according to 8. 10. The intake / exhaust valve member is controlled so as to be seated without changing a control speed range from a moving speed of the piston when a damper function of the damper means is exerted. An electromagnetic intake and exhaust device according to claim 9.