JPH02161114A - Valve system control device for internal combustion engine - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention A4 Purpose of the Invention (]) Industrial Field of Application The present invention relates to an engine valve supported on an engine body so as to be openable and closable;
An internal combustion engine comprising: a valve spring that biases the engine valve in the valve-closing direction; and a valve driving means interposed between the valve-driving cam and the engine valve to transmit force in the valve-opening direction from the valve-driving cam to the engine valve. It relates to engine valve control devices.

(2) Conventional technology In the past, in addition to controlling the opening and closing of intake valves or exhaust valves as engine valves through the cooperative action of a valve drive cam and a valve spring, they were also controlled by the operation of an electromagnetic actuator depending on the operating state of the engine. A device capable of controlling opening and closing is already known (see Japanese Utility Model Application No. 59-52I11).

(3) Problems to be Solved by the Invention The present applicant has proposed an engine valve opening/closing control device that maximizes the suction force of an electromagnetic actuator to improve engine performance ( Special request 1986
-123647) However, in this model, the engine valve is opened by energizing the electromagnetic actuator, and then closed all at once by the spring force when demagnetized, so the valve closing timing can be controlled, but inertial supercharging is effective. There was a problem in that variable control of the valve opening timing, which can be used in other applications, was not possible.

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a valve train control device for an internal combustion engine that can control the opening timing and closing timing of an engine valve with a simple configuration. do.

B1 Structure of the Invention (1) Means for Solving Issues According to the present invention, the valve driving means includes a valve opening elastic member that exerts an elastic force in the direction of opening the engine valve, and Between the valve drive cam and the valve drive cam, there is a first holding means capable of holding the engine valve in the valve closing position while accumulating the valve opening force generated by the valve drive cam in the valve opening elastic member, and a first holding means that can hold the engine valve in the valve opening position. The first holding means is configured to be able to switch between a holding state and a holding release state in order to control the opening timing of the engine valve according to the operating state of the engine. 2. The holding means is configured to be switchable between a holding state and a holding release state in order to control the closing timing of the engine valve.

(2) Effect According to the above configuration, the engine valve is held in the closed position by the first holding means regardless of the operating state of the engine and regardless of the opening/closing operation of the engine valve by the valve drive cam and the valve spring. The valve-opening force can be stored in the valve-opening elastic member in the valve-closed state. Therefore, when the holding state by the first holding means is released, the engine valve opens suddenly. Further, the open state of the engine valve can be maintained by the second holding means,
By releasing the holding state, the engine valve can be closed at any time by the valve spring.

(3) Examples Examples of the present invention will be explained below with reference to the drawings.
First, in FIG. 1 showing a first embodiment of the present invention, a combustion chamber 2 and an intake boat 3 communicating with the combustion chamber 2 are formed in a cylinder rad l of an engine body E, and the intake boat 3 is connected to an intake system including a fuel supply device 4.

Further, the cylinder head 1 is provided with an intake valve 5 as an engine valve capable of opening and closing the combustion chamber 2 side end of the intake port 3 at the front. The intake valve 5 is composed of a valve stem 5a and a valve body 5b, and the valve stem 5a is slidably fitted into a valve guide 6 fixed to the cylinder head I.
b can be seated on the valve seat 7 at the open end of the intake boat 3 on the combustion chamber 2 side from the combustion chamber 2 side.

A spring retainer 9 is connected to the upper end of the valve shaft portion 5a via a cock 8.
is installed. A valve spring 11 made of a compression coil spring is compressed between the spring retainer 9 and a spring seat 10 formed on the cylinder head 1 facing the spring retainer 9, and the elastic force of this valve spring 11 is applied to the intake valve. 5 in the valve closing direction. The spring retainer 9 is made of a magnetic material, and constitutes a first electromagnetic actuator A1 as a first holding means together with an electromagnet 13, which will be described later.
4 constitutes a second electromagnetic actuator A2 as a second holding means.

A cam holder (not shown) provided on the cylinder head l rotatably supports a valve drive camshaft 14 which is interlocked and connected to a crankshaft (not shown). A valve drive means 16 is provided between the intake cam 15 as a valve drive cam that is integrally provided on the valve drive camshaft 14 and the intake valve 5 for transmitting the force in the valve opening direction by the intake cam 15 to the intake valve 5. is interposed.

Referring also to FIG. 2, the valve driving means 16 includes a rocker shaft I7 fixedly disposed in parallel above the valve camshaft 14 between the valve camshaft 14 and the intake valve 5, and an intake cam 15. a first rocker arm 18 supported on the rocker shaft 17 so as to swing while sliding against the upper end of the intake valve 5; a second rocker arm 19 supported on the rocker shaft 17 so as to swing while contacting the upper end of the intake valve 5; 18.19
A torsion spring 20.degree. 20 is provided as a valve-opening elastic member that is interposed therebetween and exerts a spring force in the direction in which the intake valve 5 is opened.

A collar 22 is attached to the rocker shaft 17 via a cylindrical sliding metal 21. This collar 22 is basically formed into a cylindrical shape, and retaining rings 23, 23 that abut both ends of the collar 22 are fitted onto the sliding metal 21. color 22
Drum parts 22a, 22a for winding the torsion springs 20, 20 are provided at both axial ends of the collar 22, and the parts near the axial center of the collar 22, that is, both drum parts 22
between a and 22a, the first and second rocker arms 18°19
The base end is rotatably supported.

The first rocker arm 18 extends from the rocker shaft 17 toward the intake cam 15, and the cam surface of the intake cam 15 is in sliding contact with the lower surface of the tip of the first rocker arm 18. Further, since the second rocker arm 19 does not have its base in sliding contact with the base of the first rocker arm 18, the rocker shaft I
7 to the intake valve 5 side. A tappet screw 24 that abuts the upper end of the valve shaft portion 5a of the intake valve 5 is screwed into the tip of the second rocker arm 19 so as to be movable forward and backward. Furthermore, a locking nut 25 is screwed into the tappet screw 24 and comes into contact with the upper surface of the tip of the second rocker arm 19 in order to maintain the adjusted forward and backward positions.

Locking pins 26.21, which are parallel to the rocker shaft 17, are fixed to the first and second rocker arms 18.19 so as to protrude from both sides, and are wound around the drum parts 22a, 22a of the collar 22, respectively. Torsion spring 2
One end of 0,20 is the locking pin 26 of the first rocker arm 18.
, and the other end is engaged with the locking pin 27 of the second rocker arm 19, respectively. This causes the first and second rocker arms 18.19 to
8 toward the intake cam 15 side, and the second' rocker arm 19 toward the intake valve 5 side. Moreover, the elastic force of both torsion springs 20, 20 is set to be stronger than that of the valve spring 1112. Therefore, the valve train camshaft 14
When the intake cam 15 rotates, the intake cam 15 presses the intake valve 5 downward via the valve drive means 16, and can slide it in the valve opening direction, that is, in the downward direction.

Referring also to FIG. 3, an annular electromagnet 13 is fixed to the cylinder head 1, facing the upper surface of the spring retainer 9 and surrounding the valve shaft 5a of the intake valve 5. The first electromagnetic actuator A1 is configured together with the magnetic body 9 which also serves as the spring retainer. Further, the electromagnet body 13 has a small diameter hole 2 that slides into contact with the valve shaft portion 5a of the intake valve 5.
8 and a large-diameter hole 29 having a larger diameter than the small-diameter hole 28, a through-hole 30 is formed in which a large-diameter hole 29 having a larger diameter than the small-diameter hole 28 is coaxially connected in order from the bottom, and the valve shaft portion 5a of the intake valve 5 is movable in the axial direction. and is inserted into the through hole 30.

The magnetic body 9 is attracted to the electromagnet 13 by excitation of the solenoid in the electromagnet 13 . The adsorption force of the first electromagnetic actuator A1 and the spring force of the valve spring 11 are set to be stronger than the elastic force of the torsion springs 20, 20 in the valve driving means 16. Therefore, when the electromagnet 13 is energized, the intake valve 5 is held in its closed position regardless of the rotation of the valve drive camshaft 14, and the valve opening force generated by the intake cam 15 at that time is accumulated in the torsion springs 20, 20. become.

An annular recess 31 is provided on the inner surface of the intermediate portion of the large diameter hole 29 in the through hole 30 of the electromagnetic body 13 . Further, at the upper end of the valve shaft portion 5a inserted into the through hole 30, there is a cap-shaped valve piece 32 that is slidably fitted into the large diameter hole 29 of the through hole 30.
is fitted. Moreover, the valve piece 32 is connected to the intake valve 5.
When the valve piece 32 is in the closed position, the upper part of the valve piece 32 projects upward from the upper end of the through hole 30 and is fitted onto the valve shaft 5a, and the tappet screw 24 is inserted into the valve piece 3.
2. Furthermore, an oil supply hole 33 communicating with the annular recess 31 of the through hole 30 is bored in the electromagnetic body 13, and this oil supply hole 33 is connected to an oil supply source (not shown).

On the other hand, an annular electromagnetic body 34 is fixed to the cylinder head l, facing the lower surface of the spring retainer 9 and surrounding the valve shaft portion 5a of the intake valve 5. Together, they constitute a second electromagnetic actuator At. The magnetic body 9 is attracted to the electromagnet 34 by excitation of the solenoid in the electromagnet 34 . The adsorption force of the second electromagnetic actuator A2 is set to be stronger than the spring force of the valve spring 11. Therefore, if the electromagnet 34 is energized when the intake valve 5 is opened, the intake valve 5 is maintained at its closed position regardless of the rotation of the valve drive camshaft 14.

The solenoid of the electromagnet body 13 and the solenoid of the electromagnet body 34 are provided with a control circuit C that operates by detecting the operating state of the engine.
are connected, and energization and de-energization of the electromagnet body 13 and the electromagnet body 34 are switched and controlled by a signal from the control circuit C. Furthermore, detection signals such as engine speed, temperature, throttle opening, and intake air amount are input to the control circuit C as signals for detecting the operating state of the engine.

Next, the operation of the first embodiment will be explained with reference to FIGS. 4, 5, and 6. When the valve camshaft 14 is rotationally driven by engine operation, the intake cam 15 and the valve In cooperation with the spring 11, the intake valve 5 is driven to open and close at a predetermined timing. Thus, the opening lift amount of the intake valve 5 relative to the rotation angle of the valve drive camshaft 14 draws a lift curve as shown by the dashed line in FIG.

By the way, when the engine is in a specific operating state, for example, in a low-load operating state, while the inside of the base of the intake cam 15 is in sliding contact with the first rocker arm 18, as shown in FIG. Before the magnetic body 9 becomes the electromagnet 1, the electromagnetic body 13 is energized under the control of the control circuit C.
Let it adsorb to 3.

Next, as the intake cam 15 rotates, the higher portion of the intake cam 15 comes into sliding contact with the first rocker arm 18.
The first rocker arm 18 is rotated clockwise in FIG. 1, and the rotation force is a torsion spring.

20. A pressing force is also applied to the second rocker arm 19 in the clockwise direction in FIG. Because it is stronger than the explosive force of 20,20,
The second rocker arm I9 is prevented from rotating, and the first rocker arm 18 only rotates while twisting the torsion springs 20, 20, as shown in FIG. As a result, the intake valve 5 is maintained at its closed position, and the valve opening force exerted by the intake cam 15 is accumulated in the torsion springs 20, 20.

When the valve train camshaft 14 continues its rotation and the rotation angle reaches, for example, near point P in FIG. 4, that is, just before the lift amount by the intake cam 15 reaches its maximum, the electromagnet body is When the power supply to the magnetic body 13 is cut off, the force that attracts the magnetic body 9 is released. As a result, the torsion spring 20
, 20 is suddenly released, and the 6th valve opening force is suddenly released.
As shown in the figure, the intake valve 5 is suddenly opened by the elastic force of the torsion springs 20, 20, and the valve opening lift amount increases linearly as shown by the thick solid line in FIG. As a result, the air-fuel mixture flowing through the intake system flows into the combustion chamber 2 at once.

By the way, if the internal combustion engine is in the intake stroke in which the piston descends and the intake valve 5 is in the closed state as shown in FIG.
Due to the downward movement of the piston, the inside of the combustion chamber 2 has a much higher negative pressure than the conventional one, and in this state, when the intake valve 5 opens instantaneously as shown in FIG. The intake air flowing into combustion chamber 2 enters a supercharging state due to a high inertia effect, and an increased amount of intake air is supplied to combustion chamber 2, achieving a supercharging effect in a low-load operating state and improving output.

Moreover, when the holding state is released by the first electromagnetic actuator A1, the valve piece 32 attached to the valve shaft portion 5a of the intake valve 5 slides downward in the through hole 30 of the electromagnet body 13, but the valve piece 32 is When fitted to the lower part of the diameter hole 29, hydraulic pressure is trapped between the lower surface of the valve piece 32 and the step between the small diameter hole 28 and the large diameter hole 29, so that the downward movement speed of the valve piece 32, that is, the intake valve 5 The valve opening speed is relaxed and the trapped hydraulic pressure is released into the valve piece 32.
In response to the gradual leakage from between the small-diameter holes 28, the intake valve 5 slowly opens, thereby achieving damping of the sudden valve opening speed.

When the lift amount of the intake valve 5 reaches the maximum, the control circuit C
Under the control, the electromagnet 34 is energized to attract the magnetic body 9 to the electromagnet 34. As a result, the second electromagnetic actuator A2 is activated, and the intake valve 5 is maintained at its valve position during this time.
The intake valve 5 remains open regardless of the rotational position of the intake cam 15.

When the electromagnet 34 is demagnetized, the intake cam 5 is operated to close regardless of the cam profile by the spring force of the valve spring 11, as shown by the large solid line in FIG. After coming into contact with the tappet screw 24 of the drive means 16, the valve is closed by drawing a normal lift curve due to the cooperation of the intake cam 15 and the valve spring 11.

In this way, the opening timing and closing timing of the intake valve 5 can be adjusted.
By controlling the switching between the holding state and the holding release state of the first and second electromagnetic actuators A1 and A2, it is possible to set the setting arbitrarily, and it is possible to perform appropriate valve train control according to the operating state of the engine.

Moreover, in the valve driving means 16, the torsion spring 20.20
By arranging the rocker shaft 17 around the rocker shaft 17, it is possible to reduce the inertial weight. Also, the valve camshaft 1
4 is not disposed directly above the intake valve 5, and an increase in the overall height due to the valve operating camshaft 14 being disposed above the intake valve 5 can be avoided.

Note that the first and second electromagnetic actuators AI.

The holding action by A2 can be performed at any timing, as shown by the thin solid line in FIG. 4, regardless of the operating state of the engine. That is, both electromagnetic actuators A,,A2
It is possible to arbitrarily change the valve opening and closing timings between immediately after the start of the cam lift and until the maximum lift, and between the maximum lift and immediately before the end of the cam lift. Furthermore, if the power to both electromagnetic actuators A, A2 is always cut off, the opening/closing timing can be obtained in accordance with the cam profile, and if the relative rotation of the two-end hook arms 18 and 19 is prevented, the cam profile can be adjusted. This allows for reliable opening/closing timing. Moreover, by continuing to energize the first electromagnetic actuator A1 during the cam lift, the state on the valve body can be obtained.

7, 8, and 9 show a second embodiment of the present invention, and parts corresponding to the first embodiment are given the same reference numerals.

A support tube 36 extending obliquely upward along the axial direction of the intake valve 5 is integrally formed on the cylinder throat 1, and a bearing half 37 formed on the support tube 36 is fixed to the upper surface of the support tube 36. The valve train camshaft 1 is
4 is rotatably supported. An intake cam 15 provided on the valve drive camshaft 14 is connected to the intake valve 5 via a valve lifter 40 as a valve driving means, which will be described later.

A hollow cylinder portion 39 that connects the intake cam 15 and the intake valve 5 is formed in the support tube 36 of the cylinder head l, and the valve lifter 40 is disposed within the hollow cylinder portion 39.
is accommodated. This valve lifter 40 includes a lifter lower part 41 which has a hollow cylinder shape with a bottom and is fitted into the hollow cylinder part 39 so as to be slidable up and down, and a lifter lower part 41 which is slidably fitted into the lifter lower part 41 from its open upper part. a cap-shaped lifter upper part 42; two lifter springs 43, 44 as valve-opening elastic members that are compressed between the lifter lower part 4I and the lifter upper part 42 and urge them to mutually extend; It is comprised of a set nut 45 that is screwed into the opening part of the lower part 41 of the lifter and engages with it to regulate the upper limit position of the upper part 42 of the lifter.

A projecting pin 46 is integrally provided on the lifter lower part 41 and projects from the center of its lower surface, and the lower end of the projecting pin 46 is brought into contact with the upper end of the valve shaft portion 5a of the intake valve 5.

Further, the cam surface of the intake cam 15 is brought into contact with the upper surface of the lifter upper section 42 . Further, the elastic force of the lifter springs 43 and 44 is set to be stronger than that of the valve spring 11. Therefore, when the valve drive camshaft 14 rotates, the intake cam 15 presses the intake valve 5 downward via the valve lifter 40, and can slide in the valve opening direction, that is, downward.

An electromagnet 13 is fixed to the lower part of the support cylinder 36, which together with the upper surface of the spring retainer 9 constitutes a first electromagnetic actuator A, and to the cylinder head l, together with the lower surface of the spring retainer 9, constitutes a second electromagnetic actuator A. The electromagnetic body 34 is fixed as in the first embodiment. Furthermore, a contact portion between the upper end of the valve shaft portion 5a of the intake valve 5 and the protruding pin 46 integral with the lifter lower portion 42 is inserted into the hollow interior of the electromagnetic body 13. Further, the adsorption force of the first electromagnetic actuator A1 and the spring force of the valve spring 11 are set to be stronger than the elastic force of the lifter springs 43 and 44,
The adsorption force of the second electromagnetic actuator A is set to be stronger than the spring force of the valve spring 11.

An annular hydraulic chamber 47 is formed between the outer circumferential surface of the lifter lower part 41 and the inner circumferential wall of the support cylinder 36 in the valve lifter 40, and this hydraulic chamber 47 has an oil supply port 48 formed in the support cylinder 36 and an oil supply port 48 formed in the support cylinder 36. The oil drain port 49 is in communication with the hydraulic chamber 47.
A hydraulic circuit, such as an engine lubricating oil circuit, is communicated within the chamber 47, and pressure oil is circulated within the chamber 47.

The pressure oil that has flowed into the hydraulic chamber 47 is then transferred to the lifter lower part 41.
When the valve lifter 40 lifts, it acts on a downward pressure-receiving surface 50 formed on the outer circumferential surface of the valve lifter 40 to provide a buffering effect and a lubricating effect to the valve lifter 40.

According to this second embodiment, the first electromagnetic actuator A1
As shown in FIG. 8, the intake valve 5 can be held in the closed position regardless of the rotational position of the intake cam 15, and the second electromagnetic actuator A2 As a result, the open state of the intake valve 5 can be maintained as shown in FIG. 9, and the same effects as in the first embodiment can be achieved.

FIGS. 10, 11, and 12 show a third embodiment of the present invention, and parts corresponding to each of the above embodiments are given the same reference numerals.

A valve drive means 55 is interposed between the intake valve 5 and the intake cam 15, and the valve drive means 55 includes a rocker arm 56 which is rotatably supported on the rocker shaft 17 and is not in sliding contact with the intake cam 15. a sliding plunger 57 that contacts the upper end of the valve shaft portion 5a of the intake valve 5 and is supported by the rocker arm 56 so as to be able to slide freely; and a valve-opening plunger 57 that is interposed between the rocker arm 56 and the sliding plunger 57. It includes torsion springs 5B, 5B as elastic members.

The rocker arm 56 is supported by the rocker shaft 17 via a collar 59. The sliding plunger 57 also has an essentially cylindrical stopper 60 that slidably fits into the rocker arm 56 to define the lowest position of the sliding plunger 57 relative to the rocker arm 56.
The stopper 60 is screwed in such a manner that its relative position in the axial direction is variable, and a locking nut 61 for fixing the position of the stopper 60 is screwed therein. That is, in the rocker arm 56,
A hole is bored in which a large diameter hole 62 and a small diameter hole 63 are coaxially connected sequentially from above, and the stopper 60 has a large diameter portion 60a that is slidably fitted in the large diameter hole 62 and a small diameter hole 63. A small diameter portion 60b that is slidably fitted is provided. The step between the large-diameter portion 60a and the small-diameter portion 60b abuts the step between the large-diameter hole 62 and the small-diameter hole 63, thereby defining the lowest position of the stopper 60, that is, the sliding plunger 570a with respect to the arm 56. Ru. Moreover, rocker arm 5
By supplying hydraulic pressure to the annular chamber 64 defined between the stopper 60 and the stopper 60, a damping effect is achieved when the sliding plunger 57 slides downward.

An arm member 66 is fixed to the lower part of the sliding plunger 57 via a lever 65. That is, the arm member 66 consists of a disc part 66a and bottle-shaped engaging parts 66b, 66b that protrude from the disc part 66a along the -1 diameter line, and the diameter becomes smaller toward the top. disc part 6
By press-fitting the plunger 65 into the hole 67 provided in the center of the arm member 66, the sliding plunger 57
Fixed.

One end of the torsion springs 58, 58 is connected to the opening/locker arm 56 so as to be parallel to the rocker shaft 17 and protrude to both sides.
The other end of the arm member 66 is engaged with both engaging portions 66b, 66b of the arm member 66. This torsion spring 58.degree. 58 exerts an elastic force in the direction of bringing the rocker arm 56 into sliding contact with the intake cam 15, and in the direction of bringing the sliding plunger 57 into contact with the intake valve 5.

The other configurations are the same as those in the first and second embodiments, and the upper surface of the spring retainer 9 and the electromagnet body 13 constitute the first electromagnetic actuator AI, and the lower surface of the spring retainer 9 and the electromagnet body 34 constitute the first electromagnetic actuator AI. A second electromagnetic actuator A2 is constituted by the first electromagnetic actuator A,
The adsorption force of the valve spring 11 and the spring force of the torsion spring 58
．． 58, and the adsorption force of the second electromagnetic actuator A2 is set larger than the spring force of the valve spring 11.

According to this third embodiment, the first electromagnetic actuator A,
By energizing the electromagnetic body 13, the intake valve 5 can be held in a closed state, and by controlling the timing to release the holding state, the opening timing of the intake valve 5 can be controlled. Also, the second electromagnetic actuator A! The open state of the intake valve 5 can be maintained, and the closing timing of the intake valve 5 can be controlled by controlling the timing to release the held state, so that the same effect as in each of the above embodiments can be obtained. can be played.

As still other embodiments of the present invention, the tenth to twelfth
The rocker arm in the illustrated embodiment may be brought into contact with the intake cam, and the sliding plunger supported on the rocker arm may be brought into contact with the intake cam.

In each of the above embodiments, a case has been described in which the device of the present invention is applied to an intake valve opening/closing mechanism of an internal combustion engine, but it is also possible to apply this to an exhaust valve opening/closing mechanism.

C1 Effects of the Invention As described above, according to the present invention, the valve driving means includes a valve opening elastic member that exerts an elastic force in the valve opening direction of the engine valve, and the valve driving means is provided with a valve opening elastic member that exerts an elastic force in the valve opening direction of the engine valve. The first holding means is capable of holding the engine valve in the valve-closing position while accumulating the valve-opening force generated by the valve-driving cam in the valve-opening elastic member, and the second holding means is capable of holding the engine valve in the valve-opening position. The first holding means is configured to be able to switch between a holding state and a holding release state in order to control the opening timing of the engine valve according to the operating state of the engine, and the second holding means is configured to be able to switch between a holding state and a holding release state to control the opening timing of the engine valve. Since it is configured to be able to switch between a holding state and a holding release state in order to control the valve timing, by controlling the switching timing between the holding state and the holding release state of both holding means, the optimum opening can be achieved according to the operating state of the engine. The valve and valve closing timing can be set, and the intake and exhaust inertia effects can be enhanced to increase the intake efficiency or exhaust efficiency.

[Brief explanation of the drawing]

1 to 6 show a first embodiment of the present invention, in which FIG. 1 is a longitudinal sectional side view, FIG. 2 is a sectional view taken along the line ■-■ of FIG. 3, and FIG. Figure 4 is an enlarged view of part m in the figure, Figure 4 is a diagram showing the relationship between the valve opening lift amount and the rotation angle of the valve drive cam, and Figure 5 is a diagram showing the state in which the valve close position is held by the first holding means. FIG. 6 is a corresponding vertical side view, and FIG. 6 is a vertical side view corresponding to FIG.
9 to 9 show a second embodiment of the present invention, FIG. 7 is a longitudinal sectional side view, and FIG. 8 is a longitudinal sectional view corresponding to FIG. 7 showing the state in which the valve is held in the closed position by the first holding means. The side view and FIG.
10 to 12 show a third embodiment of the present invention, FIG. 10 is a longitudinal side view, FIG. 11 is a plan view of FIG. 10, and FIG. The figure is number 11
It is a sectional view taken along the line xn-xn in the figure. 5... Intake valve as engine valve, 1... Valve spring, 15
... Intake cam as a valve operating cam, 16.55... Valve driving means, 18... First rocker arm, 19... Second rocker arm, 20.58... As an elastic member for opening the valve. Torsion spring, 40... Valve lifter as valve driving means, 41... Lifter lower part, 42... Lifter upper part, 4
3.44...Lifter spring as elastic member for valve opening, 5
6...Rocker arm, 57...Sliding plunger, A
1... A first electromagnetic actuator as a first holding means, A2... A second electromagnetic actuator as a second holding means, E... Engine body, Fig. 4, valve camshaft rotation angle; 5 figures! S11 Figure 12 Figure 101

Claims (5)

[Claims] (1) An engine valve supported by the engine body so as to be openable and closable, a valve spring that biases the engine valve in the valve closing direction, and a valve cam that transmits the force in the valve opening direction from the valve cam to the engine valve. and a valve driving means interposed between the engine valves, the valve driving means comprising a valve opening elastic member that exerts an elastic force in the valve opening direction of the engine valve, Between the engine valve and the valve drive cam, there is a first holding means capable of holding the engine valve in the valve closing position while accumulating the valve opening force generated by the valve drive cam in the valve opening elastic member, and a first holding means that can hold the engine valve in the valve closing position. A second holding means that can be held in position is interposed, and the first holding means is configured to be switchable between a holding state and a holding release state in order to control the opening timing of the engine valve according to the operating state of the engine. A valve control device for an internal combustion engine, wherein the second holding means is configured to be switchable between a holding state and a holding release state in order to control the closing timing of the engine valve. (2) The valve control device for an internal combustion engine according to item (1), wherein at least one of the first and second holding means is comprised of an electromagnetic actuator. (3) In the valve driving means, an elastic member for opening the valve is interposed between the first rocker arm on the valve drive cam side and the second rocker arm on the engine valve side that can swing around a common axis with the first rocker arm. The valve control device for an internal combustion engine according to item (1), characterized in that the device is equipped with a valve control device for an internal combustion engine. (4) The valve driving means includes a valve opening elastic member interposed between the upper part of the lifter on the valve drive cam side and the lower part of the lifter on the engine valve side that is slidably fitted to the upper part of the lifter. The valve control device for an internal combustion engine according to item (1), characterized in that: (5) In the valve driving means, a valve opening elastic member is interposed between a rocker arm that slides in contact with the valve drive cam and a sliding plunger that is slidably fitted into the rocker arm and comes into contact with the engine valve. The valve control device for an internal combustion engine according to item (1), characterized in that the device comprises: