JPH0216314A - Valve system controller for internal combustion engine - Google Patents

Abstract

PURPOSE:To enable an optimum valve opening time to be set, by providing interveniently between an engine valve and a valve system cam a retaining means which retains the engine valve at a valve closing position as it accumulates under pressure the force of valve opening which is caused by the valve system cam, at a valve opening elastic member, and controlling the time of the release of its retaining state. CONSTITUTION:An air intake valve 5 provided at a cylinder head 1, has its valve shaft portion 5a which is put into a valve guide 6 slidably, and the valve 5 is energized in a valve closing direction by means of compression coil springs 11,12 interveniently furnished between a spring retainer 9 provided at the upper end of the valve shaft portion 5a and a spring seat 10 formed at the cylinder head 10. In this instance, the spring retainer 9 is formed out of a magnetic body, and this retainer 9 together with an annular electromagnetic body 13 provided in opposition to its upper surface and in such a manner as surrounds the valve shaft portion 5a, constitute an electromagnetic actuator A which works as a retaining means. And the retainer 9 is attract at the time of the excitation of the electromagnetic body 13, and the air intake valve 5 is retained at its valve closing position without relation to the rotation of a valve system camshaft 14, and an arrangement is made so that valve opening may by possible at the time of deexcitation.

Description

Detailed Description of the Invention A0 Objective of the Invention (1) Industrial Application Field The present invention provides an engine valve that is 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 Conventionally, in addition to controlling the opening and closing of intake valves or exhaust valves as engine valves by the joint operation of a valve drive cam and a valve spring, it is 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 Publication No. 59-52111).

(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 not possible. There was a problem in that variable control of valve opening timing, which could be effectively utilized, was not possible.

Therefore, the applicant has proposed that regardless of the rotational position of the valve drive cam,
The engine valve is held in a closed state against the elastic force of the valve-opening elastic member, and when the holding state is released, the engine valve is opened by the elastic force of the valve-opening elastic member. We have already proposed a method that controls the opening timing of engine valves (
Patent application No. 62237706) has been filed. However, under specific operating conditions such as high-speed engine operating conditions, there is a desire to open and close the engine valves in a manner that reliably corresponds to the cam profile of the valve drive cam, without requiring the above-mentioned valve opening timing control. In this case, the valve closing value of the holding means (If you try to open or close the engine valve without performing the holding action, the valve opening elastic member provided in the valve driving means will respond to the cam profile accurately due to the elastic actuation of the valve opening elastic member. There is a possibility that the desired opening/closing operation characteristics cannot be obtained.

The present invention has been made in view of the above circumstances, and includes a state in which the opening timing of the engine valve is controlled and a state in which the engine valve is opened and closed in accordance with the cam profile of the valve drive cam without performing valve opening timing control. It is an object of the present invention to provide a valve train control device for an internal combustion engine that can switch between states in which the engine is turned on and off with a simple configuration.

B0 Structure of the Invention (1) Means for Solving the Problems 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 A holding means is interposed between the valve cam and the engine valve to hold the engine valve in the closed position while accumulating the valve-opening force generated by the valve-driving cam in the valve-opening elastic member. The engine valve 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 depending on the state, and the valve driving means is provided with a locking mechanism that prevents elastic operation of the valve opening elastic member.

(2) Effect According to the above configuration, when the lock mechanism is in the inactive state, the holding means is activated regardless of the engine operating state and regardless of the opening/closing operation of the engine valve by the valve cam and valve spring. The engine valve can be held in the closed position, and a valve opening force can be accumulated in the valve opening elastic member in the closed state. Therefore, when the holding state by the holding means is released, the engine valve will be closed.

Open your mouth violently. Furthermore, when the locking mechanism is activated, the valve opening elastic member does not perform elastic operation, so the engine valve opens and closes in accordance with the cam profile of the valve operating cam.

(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 port 3 communicating with the combustion chamber 2 are formed in a cylinder head l of an engine body E. , and is connected to an intake system including a fuel supply device 4.

The cylinder head 1 also has a combustion chamber 2 of the intake boat 3.
An intake valve 5 is provided as an engine valve whose side opening end can be opened and closed. This intake valve 5 is composed of a valve stem part 5a and a valve body part 5b, the valve stem part 5a is slidably fitted into a valve guide 6 fixed to the cylinder head 1, and the valve body part 5b
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 attached to the upper end of the valve stem portion 5a via a retainer 8.
is installed. A valve spring 11.12 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. The generated force urges the intake valve 5 in the valve closing direction.

The spring retainer 9 is made of a magnetic material and constitutes an electromagnetic actuator A as a holding means together with an electromagnet 13 to be described later.

A cam holder (not shown) provided on the cylinder head 1 rotatably supports a valve drive cam drawer 14 which is interlocked and connected to a crankshaft (not shown). A valve drive means 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 valve drive cam 15 to the intake valve 5. 16 is interposed.

The valve driving means 16 includes a rocker shaft 17 fixedly arranged in parallel above the valve camshaft 14 between the valve camshaft 14 and the intake valve 5, and a rocker shaft 17 that slides in sliding contact with the intake cam 15 and swings. a first rocker arm 18 as a first driving member supported on the shaft 17; a twentieth rocker arm 19 as a second driving member supported on the rocker shaft 17 so as to swing while contacting the upper end of the intake valve 5; Torsion springs 20 and 20 are provided as valve opening elastic members which are interposed between the two-end hook arms 18 and 19 and exert a spring force in the opening direction of the intake valve 5.

In FIG. 2, a collar 22 is attached to the rocker shaft 17 via a cylindrical sliding metal 21. As shown in FIG. 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. A torsion spring 20 is provided at both ends of the collar 22 in the axial direction.
drum parts 22a, 22a are provided for winding the collar 20, and the proximal ends of the first and second rocker arms 18, 19 are located between the drum parts 22a, 22a in a portion closer to the center of the collar 22 in the axial direction. 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. Further, the second rocker arm 19 slides its base into contact with the base of the first rocker arm 18 while the rocker shaft 1
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 nand 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 26.27, 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 springs 11, 12. 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. An electromagnetic actuator A is configured together with the magnetic body 9 which also serves as the spring retainer. Also, the electromagnet body 13
, a small diameter hole 28 that comes into sliding contact with the valve shaft portion 5a of the intake valve 5;
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. hole 30
inserted into.

The magnetic body 9 is attracted to the electromagnet 13 by excitation of the solenoid in the electromagnet 13 . The adsorption force of the electromagnetic actuator A and the spring force of the valve springs 11 and 12 are set to be stronger than the elastic force of the torsion springs 20 and 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 stored in the torsion spring 20.20. become.

A buffer mechanism DI is provided between the intake valve 5 and the electromagnetic body 13 to alleviate the drastic opening operation of the intake valve 5. This buffer mechanism includes a hydraulic chamber 34 that can limit the amount of leakage between a stepped portion 32a provided at the upper end of the intake valve 5 and the electromagnet 13. That is, a cap-shaped valve piece 32 that slidably fits into the large diameter hole 29 of the through hole 30 is fitted to the upper end of the valve shaft portion 5a that is inserted into the through hole 30. A hydraulic chamber 34 is defined between the stepped portion 32a and the stepped portion 30a between the small diameter hole 28 and the large diameter hole 29. Further, 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, and an oil supply hole 33 communicating with the annular recess 31 is bored in the electromagnet body 13. Connected. Furthermore, a gap is formed between the outer surface of the valve stem portion 5a and the inner surface of the small diameter hole 29, which is large enough to leak the hydraulic pressure in the hydraulic chamber 34 when the hydraulic pressure in the hydraulic chamber 34 increases. Furthermore, the valve piece 32 is fitted onto the valve shaft portion 5a such that the upper part of the valve piece 32 projects upwardly from the upper end of the through hole 30 when the intake valve 5 is in the closed position, - 1, -ζ screw 24 abuts against the valve piece 32.

In FIG. 4, a locking mechanism R8 is provided between the first and second rocker arms 18, 19 in the valve drive means 16. This long mechanism R1 has torsion springs 20, 20
A locking member 51 that is capable of preventing relative rotation of the two rocker arms 18 and 19 against the spring force of the second rocker arm 19 and is slidably fitted to the second rocker arm 19;
The second rocker arm 1 faces the back side of the locking member 51 in order to exert hydraulic pressure that brings the second rocker arm 1 into contact with the first rocker arm 18.
9, and a return spring 53 that urges the locking member 51 in a direction to contract the hydraulic chamber 52.

The second rocker arm 19 has a bottomed sliding hole 54 that opens toward the first rocker arm 18 side, and a double cylindrical spring bearing member 55 is installed at the open end of the sliding hole 54. The locking member 51, which is screwed and slidably fitted into the sliding hole 54, is guided by the spring receiving member 55 and moves the second rocker arm 1 in the direction in which it comes into contact with the second rocker arm 1 on the 20th day.
It is possible to protrude from 9. Further, the return spring 53 is compressed between the spring receiving member 55 and the locking member 51.

Further, the hydraulic chamber 52 is defined between the lock member 51 and the closed end of the sliding hole 54, and this hydraulic chamber 52 is
It communicates with a passage 56 bored in the second rocker arm 19. Moreover, the passage 56 connects the collar 22 and the sliding metal 2 to the hydraulic pressure supply passage 57 provided in the locker cabinet 1-1.
1, and the hydraulic pressure supply path 57 is connected to a hydraulic pressure supply source (not shown).

According to this locking mechanism R8, when hydraulic pressure is supplied to the hydraulic chamber 52, the locking member 51 protrudes toward the first rocker arm 18 against the spring force of the return spring 53, and the locking member 51
By abutting the tip of the first rocker arm 18,
Relative rotation of both Ronca arms 1819 against the spring force of torsion springs 20, 20 is prevented.

A control circuit C is connected to the solenoid of the electromagnetic body 13 and operates by detecting the operating state of the engine.
energization and de-energization of the electromagnet 13 are switched and controlled by signals from the electromagnet 13. 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. 5, 6, and 7. When the valve drive camshaft 14 is rotationally driven by engine operation, the intake cam 15 and the valve In cooperation with the springs 11 and 12, the intake valve 5 is driven to open and close at a predetermined timing. The opening lift amount of the intake valve 5 with respect 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. The electromagnet 13 is energized under the control of the control circuit C before the spring retainer 9 is energized.
■Adsorb it to the stone body 13.

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 rotational force is transmitted via the torsion spring 20, 20, and a pressing force is also applied to the second rocker arm 19 in the clockwise direction in FIG. However, as mentioned above, the spring force of the electromagnetic actuator A and the valve springs 11 and 12 is equal to the force of the torsion springs 20 and 20.
6, the second rocker arm 19 is prevented from rotating, and as shown in FIG.
The tenth anchor arm 18 only rotates while twisting 0.20. 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. 5, that is, just before the lift a by the intake cam 15 reaches its maximum, the control circuit C controls i? When the power to the magnet body 13 is cut off, the force that attracts the spring retainer 9 is released. As a result, the valve opening force accumulated in the torsion springs 20, 20 is suddenly released, and as shown in FIG. Lift amount is 5th
It increases linearly as shown by the large solid line in the figure. 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 is brought into a supercharged state under 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.

When the holding state is released by the ff1la actuator A, the buffer mechanism operates, and when the valve piece 32 fits into the lower part of the large diameter hole 29, the hydraulic pressure is trapped in the hydraulic chamber 34 between the stepped portions 32a and 30a, so that the valve The downward movement speed of the piece 32, that is, the opening speed of the intake valve 5, is relaxed, and as the trapped hydraulic pressure gradually leaks from between the valve stem 5a and the small diameter hole 28, the intake valve 5 is opened. The valve opening operation is relaxed.

After the lift amount of the intake valve 5 reaches the maximum, the intake valve 5 is closed while drawing a normal lift curve due to the cooperative action of the intake cam 15 and the valve springs 11 and 12.

Furthermore, in the valve driving means 16, by arranging the torsion spring 2020 around the rocker shaft 17, it is possible to reduce the inertial weight. In addition, the valve train camshaft 14
is not disposed directly above the intake valve 5, and an increase in overall height due to the valve operating camshaft 14 being disposed above the intake valve 5 can be avoided.

The valve-closing holding action by the electromagnetic actuator A can be performed at any timing, as shown by the solid line in FIG. 5, regardless of the operating state of the engine. That is, the valve opening timing can be arbitrarily changed from immediately after the start of the cam lift to the maximum lift, and from the maximum lift to just before the end of the cam lift. In addition, if the energization to electromagnetic actuator 8 is continued during the cam lift, the valve body state will be changed to 1.
'J can.

For example, when the engine is in a high-load operating state, the electromagnetic actuator A is de-energized and hydraulic pressure is supplied to the hydraulic chamber 52 in the lock mechanism R1. By doing so, the lock member 51 comes into contact with the tenth deer arm 18, thereby preventing the relative rotation of the double-ended hook arms 18, 19 due to the elastic force of the torsion springs 20, 20.

Therefore, even if the torsion springs 20, 20 are interposed in the valve drive means 16, the second rocker arm 19 can be caused to follow the first rocker arm 1 while preventing the elastic operation of the torsion springs 20, 20. Intake cam 15
The intake valve 5 can be driven to open and close using the same cam profile.

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

A locking mechanism R2 is provided between the first and second rocker arms 18,19. This lock mechanism R2 includes a lock member 51 that is slidably fitted to the second rocker arm 19, and a hydraulic chamber 5 that is formed facing the back surface of the lock member 51.
2, a return spring 53 that exerts a biasing force in the direction of separating the lock member 51 from the first rocker arm 18, and a fitting portion as a locking portion provided on the first rocker arm 18 to fit the tip of the lock member 51. A recess 58 is provided.

According to this second embodiment, hydraulic pressure is supplied to the hydraulic chamber 52 to cause the locking member 51 to protrude toward the tenth anchor arm 18,
By fitting the locking member 51 into the fitting recess 58, the relative rotation of the locking arms 18 and 19 is prevented, and if the locking mechanism R2 is operated in this way,
The intake valve 5 can be driven to open and close in accordance with the cam profile of the intake cam 5.

10, 11, 12, 13, 14 and 15 show a third embodiment of the present invention,
Portions corresponding to those in the first embodiment are given the same reference numerals.

A valve driving means 35 is interposed between the intake valve 5 and the intake cam 15, and the valve driving means 35 includes a first valve drive means 35 that is not in sliding contact with the intake cam 15 and is rotatably supported on the rocker shaft 17. A rocker arm 36 as a driving member, a sliding plunger 37 as a second driving member supported by the rocker arm 36 so as to be able to freely slide without contacting the upper end of the valve shaft portion 5a of the intake valve 5; Torsion springs 3B, 3B are provided as valve opening elastic members interposed between the dynamic plungers 37.

The rocker arm 36 is supported by the rocker shaft 17 via a collar 39. The sliding plunger 37 also has an essentially cylindrical stopper 40 that slidably fits into the rocker arm 36 to define the lowest position of the sliding plunger 37 relative to the rocker arm 36.
The stopper 40 is screwed in such a manner that its relative position in the axial direction is variable, and a stopper nut 41 is screwed in to fix the position of the stopper 40 . In other words, the rocker arm 36 has
A hole is drilled in which a large diameter hole 42 and a small diameter hole 43 are coaxially connected sequentially from above, and the stopper 40 has a large diameter portion 40a that is slidably fitted in the large diameter hole 42 and a small diameter hole 43. A small diameter portion 40b that is slidably fitted is provided. The step between the large diameter portion 40a and the small diameter portion 40b comes into contact with the step between the large diameter hole 42 and the small diameter hole 43, thereby defining the lowest position of the stopper 40, that is, the sliding plunger 37 with respect to the rocker arm 36. be done.

Moreover, a buffer mechanism D2 is provided between the rocker arm 36 and a stopper 40 fixed to the sliding plunger 37, and this buffer mechanism Dz protects the hydraulic chamber 44 defined between the rocker arm 36 and the stopper 40. The hydraulic chamber 44 communicates with a hydraulic pressure supply passage 60 in the rocker shaft 17 via a passage 49 bored in the rocker arm 36. This buffer mechanism D2 includes a stopper 40 and a rocker arm 3.
By leaking hydraulic pressure from the gap between 6 and 6, a buffering effect is achieved when the sliding plunger 37 slides downward.

An arm member 46 is fixed to the lower part of the sliding plunger 37 via a stopper 45. That is, the arm member 46 consists of a disc part 46a and pin-shaped locking parts 46b, 46b that protrude from the disc part 46a along one diameter line, and the diameter becomes smaller toward the top. disc part 4
The arm member 46 moves into the sliding plunger 37 by press-fitting the plunger 45 into the hole 47 provided in the center of the arm member 46.
Fixed.

One end of the torsion springs 38, 3B is respectively engaged with a locking pin 48 fixed to the rocker arm 36 so as to be parallel to the rocker shaft 17 and protrude to both sides, and the other end is engaged with a locking pin 48 fixed to the rocker arm 36 so as to be parallel to the rocker shaft 17. 46b, 46b.

This torsion spring 38.degree. 38 exerts an elastic force in the direction of bringing the rocker arm 36 into sliding contact with the intake cam 15, and in the direction of bringing the sliding plunger 37 into contact with the intake valve 5.

A locking mechanism R3 is provided between the rocker arm 36 and the sliding plunger 37. This locking mechanism R1 engages with an annular locking groove 61 as a locking portion provided on the outer surface of the large diameter portion 40a of the stopper 40 that is substantially integrated with the sliding plunger 37. The locking member 62 has a substantially U-shaped engagement claw 62a at its tip and is disposed on the rocker arm 36 so as to be movable forward and backward.

A sliding hole 63 having an axis perpendicular to the axis of the sliding plunger 37 is bored in the rocker arm 36, and a cap 66 is provided at the end of the sliding hole 63 on the opposite side from the sliding plunger 37. Obstructed. Furthermore, an actuating piston 65 defining a hydraulic chamber 64 between it and the camp 66 is slidably fitted in the sliding hole 63, and the engaging claw 62a at the tip is connected to the sliding plunger 37 of the sliding hole 63. The proximal end of the locking member 62 inserted into the sliding hole 63 so as to be able to protrude from the side open lower end is fixed to the actuating piston 65. Also, the operating piston 6
A return spring 67 is interposed between the locking member 62 and the locking member 62 in the sliding hole 63. The member 62 is urged.

A passage 68 communicating with the hydraulic chamber 64 is bored in the rocker arm 36, and this passage 68 is connected to the hydraulic pressure supply passage 60.
It is constantly connected to a hydraulic pressure supply path 69 that is bored in the rocker shaft 17 independently of the rocker shaft 17 .

Moreover, the hydraulic pressure supply path 69 is connected to a hydraulic pressure supply source (not shown), and when hydraulic pressure from the hydraulic pressure supply source is supplied to the hydraulic chamber 64, the actuating piston 65 is moved to the locking member 6.
The engaging pawl 62a at the tip of No. 2 is operated in the direction of protruding from the sliding hole 63.

Further, an annular groove 70 is provided on the outer surface of the intermediate portion of the actuating piston 65, and when the actuating piston 65 is moved to a position where the engagement claw 62a at the tip of the locking member 62 protrudes from the sliding hole 63, the annular groove 70 is inserted into the annular groove 70. At a position corresponding to 70, an engaging ball 71 that can engage with the annular groove 70 is disposed in the middle of the sliding hole 63.

That is, the engaging ball 71 is supported by the rocker arm 36 in a manner movable in the radial direction of the actuating piston 65 between a position where it engages with the annular groove 70 and a position where it releases the engaged state. The oil pressure of the passage 68 acts on the back surface of the ball 71.

On the other hand, a stopper 4 substantially integrated with the sliding plunger 37
The locking groove 61 provided at 0 is arranged at a position where the engaging pawl 62a of the locking member 62 can engage when the sliding plunger 37 moves relative to the rocker arm 36 to the lowest position.

Further, as in the first embodiment, the electromagnetic actuator A is constituted by the electromagnetic body 13 fixed to the cylinder head 1 and the spring retainer 9.

According to this third embodiment, by energizing the electromagnetic body 13 of the electric 6n actuator A, the sliding plunger 37 can be operated even when the rocker arm 36 is in sliding contact with the high part of the intake cam 15 as shown in FIG. By moving the intake valve 5 upward relative to the rocker arm 36, the intake valve 5 can be held in the open position, and at this time, the torsion springs 3B, 3B
The valve opening force accumulated in the valve opening force can be suddenly applied to the intake valve 5 as shown in FIG. 15 in response to the release of the holding state by the electromagnetic actuator A, so that the intake valve 5 can be opened instantly. At this time, the valve opening operation speed can be moderated by the buffer mechanism D2.

Furthermore, when the engine is in a high-load operating state, the locking member 62 is
The engaging claw 62a at the tip of the engaging claw 62a can be engaged with the annular recess 61, and by maintaining this state by engaging the engaging ball 71 with the annular groove 70, the rocker arm 36 and the sliding plunger 37 are substantially connected. It is possible to open and close the intake valve 5 in a manner that reliably corresponds to the cam profile of the intake cam 15.

Moreover, in this third embodiment, in order to ensure surface pressure against the rocker shaft 17, the support length of the rocker arm 36 relative to the rocker shaft 17 can be made relatively long. Furthermore, the structure is simple, which is advantageous in terms of machinability such as drilling and ensuring accuracy.

FIG. 16 shows a fourth embodiment of the present invention, in which a locking mechanism R4 is provided between the rocker arm 36 and the sliding plunger 37.

This locking mechanism R4 includes a locking nut 4 screwed onto the upper end of the sliding plunger 37 to maintain the position of the striker 40.
1' (the position shown by the chain line in FIG. 16) and the position where the engagement state is released (the position shown by the solid line in FIG. 16). a locking member 73, an actuating piston 75 disposed on the rocker arm 36 so as to be movable back and forth in order to press the locking member 73 toward the engagement position; The locking member 73, which includes a hydraulic chamber 76 and is provided in the rocker arm 36 facing the back, is formed into a substantially U-shape in cross section so as to fit and engage the locking nut 41' from above, and its base end is supported on the rocker arm 36 by a support shaft 74 having an axis perpendicular to the axis of the sliding plunger 37 .

On the other hand, a sliding hole 77 having an axis perpendicular to the axis of the sliding plunger 37 is bored in the rocker arm 36, and the end of the sliding hole 77 on the opposite side from the sliding plunger 37 is capped. It is closed at 78. Moreover, the sliding hole 77
An operating piston 75 defining a hydraulic chamber 76 between it and the cap 78 is slidably fitted therein, and the tip of the operating piston 75 is brought into contact with the back surface of the proximal end of the locking member 73 .

In addition, the inner surface of the proximal end of the locking member 73 and the rocker arm 3
A return spring 79 is interposed between 6 and 6, and this return spring 79 urges the actuating piston 75 in the direction in which the lock member 73 rotates toward the disengaged position, that is, in the direction in which the volume of the hydraulic chamber 76 contracts. do.

The hydraulic chamber 76 is constantly communicated with a hydraulic pressure supply passage 69 in the Roncassion 1f via a passage 68 of the rocker arm 36. Further, an engagement ball 8 that engages with an annular groove 80 of the piston 75 when the locking member 73 rotates to the engagement position is provided in an annular groove 80 provided on the outer surface of the intermediate portion of the operating piston 75.
1 is disposed in the middle of the sliding hole 77, as in the third embodiment.

In this fourth embodiment as well, as in the third embodiment, the locking mechanism R4 prevents the relative operation of the rocker arm 36 and the sliding plunger 37, and the intake valve 5 is connected to the intake cam 1.
It can be opened and closed along the cam profile of 5.

17 to 21 show a fifth embodiment of the present invention, and parts corresponding to each of the above embodiments are given the same reference numerals.

A support tube 86 extending upward along the axial direction of the intake valve 5 is integrally formed on the cylinder head l, and a bearing half 87 formed on the support tube 86 is fixed to the upper surface of the support tube 86. The valve drive camshaft 14 is rotatably supported by the bearing cap 88 . An intake cam 15 provided on the valve drive camshaft 14 is connected to the intake valve 5 via a valve lifter 90 serving as a valve driving means.

A hollow cylinder portion 89 that connects the intake cam 15 and the intake valve 5 is formed in the support tube 86 of the cylinder head 1, and the valve lifter 90 is disposed within the hollow cylinder portion 89.
is accommodated. This valve lifter 90 includes a lifter lower part 91 as a first driving member which is shaped like a hollow cylinder with a bottom and is fitted into the hollow cylinder part 89 so as to be slidable up and down, and a lifter lower part 91 as a first driving member which is slidably fitted into the lifter lower part 91 from the open upper part. A cap-shaped lifter upper part 92 serving as a second driving member that is movably fitted, and a valve-opening elastic member that is compressed between the lifter lower part 91 and the lifter upper part 92 and urges them to extend each other. as 2
The set nand 95 is screwed onto the open upper part of the lifter lower part 91 and engages with it to regulate the upper limit position of the lifter upper part 92.

A projecting pin 96 is integrally provided on the lifter lower part 91 and projects from the center of its lower surface, and the lower end of the projecting pin 96 abuts 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 92 . Further, the elastic force of the lifter springs 93 and 94 is set to be stronger than that of the valve springs 11 and 12. Therefore, when the valve drive camshaft 14 rotates, the intake cam 15 presses the intake valve 5 downward via the valve lifter 90, and can slide in the valve opening direction, that is, downward.

An electromagnet 13 that constitutes the electromagnetic actuator A together with the upper surface of the spring retainer 9 is fixed to the lower part of the support cylinder 86 . Further, a contact portion between the upper end of the valve shaft portion 5a of the intake valve 5 and a protruding pin 96 integrated with the lower lifter portion 91 is inserted into the hollow interior of the electromagnet body 13.

A buffer mechanism is provided between the lifter lower part 91 and the support tube 86. This buffer mechanism D3 is a lifter lower part 91.
An annular hydraulic chamber 9 is provided between the outer circumferential surface of the support tube 36 and the inner circumferential wall of the support tube 36.
7 is provided, and this hydraulic chamber 97 is provided with a support cylinder 86.
An oil supply port 98 and an oil drain port 99 formed in the hydraulic chamber 97 communicate with each other, and a hydraulic circuit, such as an engine lubricating oil circuit, is communicated with the hydraulic chamber 97 so that pressure oil circulates within the chamber 97. It has become. The pressure oil that has flowed into the hydraulic chamber 97 is transferred to the downward pressure receiving surface 1 formed on the outer peripheral surface of the lifter lower part 41.
00 to provide a buffering effect and a lubricating effect to the valve lifter 90 when the valve lifter 90 lifts.

Further, a locking mechanism R3 is interposed between the lifter lower part 91 and the lifter upper part 92 which is slidably fitted into the lifter lower part 91.

This locking mechanism R5 includes a locking member 102 that is slidably fitted into a bottomed sliding hole 101 provided in the center of the lifter lower part 91, and a space between the locking member 102 and the closed end of the sliding hole 101. Hydraulic chamber 103 formed in and lock member 1
An abutment pin 104 that can come into contact with the upper end of the lifter upper part 92 and protrudes from the center of the lifter upper part 92, and a locking member 102 and the lifter upper part 92 to exert a spring force in the direction of contracting the volume of the hydraulic chamber 103. and a return spring 105 interposed therein.

The locking member 102 has an oil passage 10 communicating with the hydraulic chamber 103.
6 is bored, and the lifter lower part 91 is provided with an oil passage 107 that always communicates with the oil passage 106 regardless of the relative movement position with respect to the lock member 102.
An oil passage 108 is provided which always communicates with the oil passage 107 regardless of the vertical position of the oil passage 109.
It is connected to a hydraulic power supply source (not shown) via.

Further, the axial length of the abutment pin 104 is such that the locking member 102 remains stable even when the lifter lower part 91 and the lifter upper part 92 move relative to each other to the maximum extent in a state where no hydraulic pressure is supplied to the hydraulic chamber 103. It is set to such an extent that it does not come into contact with the upper end.

According to the fifth embodiment, if the intake valve 5 is held in the closed position by the electromagnetic actuator A, the intake valve 5 is kept in the closed state regardless of the rotational position of the intake cam 15, as shown in FIG. When the valve is held in the closed position by the electromagnetic actuator A, the stored spring force of the lifter springs 93 and 94 causes the intake valve 5 to open as shown in FIG. Moreover, when the lift I of the intake valve 5 is near the maximum when the intake valve 5 is opened,
Hydraulic pressure is trapped in the hydraulic chamber 97 of the buffer mechanism, and the hydraulic pressure leaks from the gap between the lifter lower part 91 and the support tube 86. Therefore, in a region where the energy released by the lifter springs 93, 94 is large, the opening operation of the intake valve 5 is relaxed by the buffering action of the buffering mechanism D3.

Further, when hydraulic pressure is supplied to the hydraulic chamber 103 of the locking mechanism R7, the locking member 102 rises and comes into contact with the abutment bin 104, as shown in FIG. 20, and the lifter upper part 92 moves downward relative to the lifter lower part 91. will be prevented. Therefore, as shown in FIG. 21, when the lifter upper part 92 is pushed down by the intake cam 15, the lifter lower part 91 is also integrally driven downward, and the intake valve 5 is driven to open and close in accordance with the cam profile of the intake cam 15. be able to.

The fifth embodiment can also provide the same effects as those of the embodiments described above.

FIG. 22 shows a sixth embodiment of the present invention, and parts corresponding to those in the fifth embodiment are given the same reference numerals.

The valve lifter 90' serving as a valve driving means includes a lifter lower part 91' serving as a first driving member which is slidably fitted into the hollow cylinder portion 88 of the support tube 86, and a lifter lower part 91' which is slidably fitted into the hollow cylinder 88. Lifter upper part 92 as a second driving member to be fitted
', and a pair of lifter springs 93 and 94 interposed between the lifter lower part 91' and the lifter upper part 92', and a locking mechanism R6 is interposed between the lifter lower part 91' and the lifter upper part 92'. will be established.

The upper end of a protruding pin 96' that abuts the upper end of the intake valve 5 is screwed into the center of the lower part of the lifter 91'.

Further, a cylindrical portion 110 extending upward is coaxially protruded from the upper center of the lower lifter 91', and a bottle 111 protruding from the lower center of the upper lifter 92', which is in sliding contact with the intake cam 15, slides into the cylindrical portion 101. are movably fitted. Also, bottle 11
A screw member 114 that can engage with a locking stepped portion 112 provided at the upper end of the cylindrical portion 110 is screwed onto the tip of the cylindrical portion 110 . Therefore, the relative movement of the lifter lower part 91' and the lifter upper part 92' in the direction away from each other is restricted by the screw member 114 engaging with the locking step 112.

The locking mechanism R6 includes a protruding pin 96 within the cylindrical portion 110.
A hydraulic chamber 113 is formed between the upper end of the bottle 111 and the lower end of the bottle 111, and when hydraulic pressure is supplied to this hydraulic chamber 113, the bottle 111, that is, the lower part of the lifter 9
2' is prevented from moving downward relative to the lifter lower part 91'.

The protruding pin 96' has an oil passage 11 communicating with the hydraulic chamber 113.
5 is provided, and this oil passage 115 is always in communication with the oil passage 108 provided in the support cylinder 36.

This sixth embodiment can also provide the same effects as the fifth embodiment.

In each of the above embodiments, the case where the device of the present invention is applied to the intake valve opening/closing mechanism of an internal combustion engine has been explained, but it is also possible to apply this to the opening/closing mechanism of the exhaust valve. When the valve is suddenly opened, pressurized exhaust gas flows into the exhaust system all at once, increasing exhaust inertia and improving exhaust efficiency, thereby increasing output.

C0 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 has a valve opening elastic member that exerts an elastic force in the valve opening direction of the engine valve. is equipped with a holding means 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. The valve driving means is configured to be able to switch between a holding state and a holding release state in order to control the valve opening timing, and the valve driving means is provided with a locking device on the side that can prevent the elastic actuation of the valve opening elastic member. By controlling the holding state release timing, it is possible to set the optimal valve opening timing according to the operating condition of the engine, increase the intake and exhaust inertia effects, and increase the intake efficiency or exhaust efficiency. This also makes it possible to prevent the elastic member for opening the valve from springing and to drive the engine valve to open and close according to the profile of the valve operating cam.

[Brief explanation of the drawing]

1 to 7 show a first embodiment of the present invention, FIG. 1 is a vertical side view, FIG. 2 is a sectional view taken along the line ■-■ in FIG. 1, and FIG. Figure 4 is an enlarged view of part ■ in the figure, Figure 4 is a longitudinal cross-sectional view of the main part showing the locking mechanism attached to the valve driving means, Figure 5 shows the relationship between the valve opening lift i and the rotation angle of the valve drive cam. 6 is a vertical sectional side view corresponding to FIG. 1 showing a state in which the valve closed position is held by the holding means, and FIG. 7 is a longitudinal sectional side view corresponding to FIG. 1 showing a state in which the holding is released by the holding means.
8 and 9 show a second embodiment of the present invention, FIG. 8 is a vertical sectional view of the main part corresponding to FIG. 4, and FIG. 9 is a [X-IXX line diagram of FIG. 10 to 15 show a third embodiment of the present invention, in which FIG. 10 is a longitudinal sectional side view, and FIG. 11 is a XI-XI line diagram of FIG. 10.
The figure is the x n - x n sg sectional view of Fig. 11,
The figure shows the locking mechanism, and FIG. 14 shows a vertical cross-sectional side view of the cylinder showing the state in which the valve is held in the closed position by the holding means. FIG. 15 shows the cylinder held by the holding means. FIG. 16 is a longitudinal sectional side view corresponding to FIG. 10 showing the released state, FIG. 16 is a longitudinal sectional side view of main parts corresponding to FIG. 13 of the fourth embodiment of the present invention, and FIGS. Fig. 17 is a vertical side view showing the valve in the closed state, Fig. 18 is a longitudinal side view showing the valve closed position held by the holding means, and Fig. 19 is the valve closed position held by the holding means. 20 is a vertical sectional side view corresponding to FIG. 17 when the locking mechanism is activated, FIG. 21 is a vertical sectional side view corresponding to FIG. 19 when the locking mechanism is activated, and FIG. FIG. 7 is a longitudinal sectional side view of the locking mechanism according to the sixth embodiment of the invention when it is in operation;

Claims (9)

[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, A holding means is interposed between the engine valve and the valve driving cam, and the holding means can hold 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. , 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, and the valve driving means includes a locking mechanism that can prevent the elastic actuation of the valve opening elastic member. A valve control device for an internal combustion engine, characterized in that a valve control device for an internal combustion engine is attached. (2) The valve driving means includes first and second driving members that are relatively displaceable, and a valve opening elastic member interposed between both the driving members, and the locking mechanism is configured such that the valve opening elastic member is elastic. Item (1), characterized in that the hydraulic chamber is interposed between the two drive members and has a hydraulic chamber capable of exerting a hydraulic pressure in a direction to prevent relative displacement of the two drive members against the generated force. Valve control system for internal combustion engines. (3) between the first rocker arm on the valve drive cam side as the first drive member and the second rocker arm as the second drive member that can swing around a common axis with the first rocker arm;
The valve control device for an internal combustion engine according to item (2), characterized in that a locking mechanism is provided. (4) a lower part of the lifter on the engine valve side as a first driving member;
The internal combustion engine according to item (2), characterized in that a locking mechanism is interposed between the upper part of the lifter on the valve operating cam side as the second driving member movable relative to the lower part of the lifter. Valve control device. (5) The valve driving means includes first and second driving members that are relatively displaceable, and a valve opening elastic member interposed between both the driving members, and the locking mechanism includes the first and second driving members that are relatively movable. The internal combustion engine according to item (1), characterized in that a locking member that can be engaged with one of the driving members is disposed on the other driving member so as to be operable between an engaged position and a disengaged position. Engine valve control device. (6) The locking mechanism includes a locking portion provided on one of a first rocker arm on the valve drive cam side serving as a first driving member and a second rocker arm that is swingable around a common axis with the first rocker arm; (5) a locking member disposed on the other of the first and second rocker arms so as to be movable back and forth between a position in which it engages with the stop portion and a position in which the engaged state is released; ) A valve control device for an internal combustion engine as described in item 2. (7) The valve driving means includes a rocker arm as a first driving member that slides in contact with the valve driving cam, a sliding plunger as a second driving member that is slidably supported on the rocker arm so as to come into contact with the engine valve, and a rocker arm. and a valve-opening elastic member interposed between the sliding plungers, and the locking mechanism includes a locking part provided on the sliding plunger, a position where the locking part is engaged, and a position where the locking mechanism releases the engaged state. The valve control device for an internal combustion engine according to item (5), further comprising a locking member that is movably disposed on the rocker arm and a locking member that is movable in the rocker arm. (8) The valve driving means includes a rocker arm as a first driving member that slides in contact with the valve driving cam, a sliding plunger as a second driving member that is slidably supported on the rocker arm so as to come into contact with the engine valve, and a rocker arm. and a valve-opening elastic member interposed between the sliding plungers. a lock member supported by the rocker arm; an actuating piston disposed on the rocker arm so as to be movable back and forth so as to press the lock member in a direction to engage the sliding plunger; and an actuating piston for applying hydraulic pressure to the actuating piston. The valve control device for an internal combustion engine according to item (5), further comprising: a hydraulic chamber provided in the rocker arm facing the rear surface of the valve control device for an internal combustion engine. (9) The valve control device for an internal combustion engine according to item (1), wherein the holding means comprises an electromagnetic actuator.