JPH029902A - Valve system controller for internal combustion engine - Google Patents

Abstract

PURPOSE:To make it possible to set an optimum valve opening timing at all times by providing a retaining means for retaining an engine valve at a valve close position while storing valve opening force by a valve system can in a resilient member, between the engine valve and the valve system cam, and controlling retaining state release timing of the retaining means. CONSTITUTION:When a valve system cam shaft 14 is rotated by the operation of an engine, an intake valve 5 is opened and closed with a specified timing by the cooperation of an intake cam 15 and valve springs 11, 12. In this case, under a specified operation state of the engine, an intake valve 5 energizes an electromagnet 13 in a retaining means before the valve turns into a lift state, thereby to attract a spring retainer 9. Under a state that the valve 5 is lifted, a rocker arm 18 is turned while a twist spring 20 is twisted, and the valve 5 is retained at a valve close position. Valve opening force stored in the spring 20 is released by shutting energization to the magnet 13 off when the rotational angle of the cam shaft 14 reaches to the point which is located just before the amount of valve lift becomes the maximum to rapidly open the valve 5.

Description

Detailed Description of the Invention A1 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 In the past, the opening and closing of the intake valve or exhaust valve as an engine valve was controlled by the joint operation of a valve drive cam and a valve spring, but it was also possible to control the opening and closing of the intake valve or exhaust valve as an engine valve by operating 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 By the way, in the engine valve opening/closing control device, the suction force of the electric Ck actuator is utilized to the maximum to improve the performance of the engine. was proposed (Japanese Patent Application No. 123647/1982), but in this method, the engine valve is opened by the excitation of the electric 1tlf actuator, and the valve is closed all at once by the spring force by demagnetization, so the valve opening timing is However, there was a problem in that variable control of valve opening timing, which would allow effective use of inertial supercharging, was not possible.

Therefore, the applicant has proposed that regardless of the rotational position of the valve drive cam,
The engine valve is kept in the closed state t'+ I- against the elastic force of the valve-opening elastic member, and when the holding state is released, the engine opens due to the elastic force Q2 of the valve-opening elastic member. Have you already created a system that controls jUl when the engine button t opens by opening the valve? , this proposal (Special 19! I Showa 622377
06'r3-)L. However, after this proposal, the retention means -! If the holding state is released, the engine valve may suddenly open due to the elastic force of the valve opening elasticity: ', II)4, which may cause injury to the engine valve or other members.

The present invention has been made in view of the above circumstances, and it is possible to make effective use of inertia supercharging by controlling the opening timing of the engine valve, and also to make it possible to smoothly operate the engine valve when the valve is opened. An object of the present invention is to provide a valve control device for an internal combustion engine.

B1 Structure of the Invention (1) Means for Solving the Problems The present invention provides a valve driving means including a valve opening elastic member that exerts an elastic force in the valve opening direction of the engine valve, and the engine valve and the valve driving cam. 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 is interposed between the It 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 accordingly, and the valve driving means includes a valve driving means and a drawing stage that open the valve using the elastic force of an elastic member for opening the valve. It is characterized by being equipped with a buffer mechanism for reducing the load.

Further, in 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 valve-opening force generated by the valve-driving cam is provided between the engine valve and the valve-driving cam. A holding means capable of holding the engine valve in the closed position while accumulating pressure in the valve opening elastic part H is provided, and the holding means is configured to control the opening timing of the engine valve according to the operating state of the engine. Between an engine valve or an interlocking member integrally connected to the engine valve, which is configured to be switchable between a holding state and a holding release state, and a fixed guide member that guides the operation of the engine valve or interlocking member. Another feature is that a buffer mechanism is provided to relieve the valve opening operation of the engine valve due to the elastic force of the valve opening elastic member.

(2) Effect According to the above feature, the engine valve can be held in the closed position by the 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. In the valve-closed state, a valve-opening force can be accumulated in the valve-opening elastic member. Moreover, when the holding state by the holding means is released, the engine valve tries to open suddenly, but the sudden valve opening operation is alleviated by the action of the buffer mechanism attached to the valve driving means.

According to the other features mentioned above, the holding means can hold the engine valve in the closed position regardless of the operating state of the engine and the opening/closing operation of the engine valve by the valve drive cam and valve spring. Valve opening force can be accumulated in the valve opening elastic member in the valve closed state.

Furthermore, when the holding state by the holding means is released, the engine valve tries to open suddenly, but the sudden valve opening operation is alleviated by the action of the buffer mechanism between the engine valve or the interlocking member and the guide member.

(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 cylinder head 1 of an engine body E is formed with a combustion chamber 2 and an intake port 3 communicating with the combustion chamber 2. , and is connected to an intake system including a fuel supply device 4.

In addition, the cylinder head 1 has a combustion chamber 2 of the intake port 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 port 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 contour 8.
is installed. Valve springs 11 and 12 made of compression coil springs are compressed between the spring retainer 9 and a spring seat 10 formed on the cylinder head 1 facing the spring retainer 9. The 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 camshaft 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 second rocker arm 19 as a second driving member supported on the rocker shaft 17 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 shirt 1-17 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. Torsion springs 20 are provided at both axial ends of the collar 22.
. 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 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 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 26.27, 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 tram portions 22a, 22a of the collar 22, respectively. tension 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. As a result, the first and second rocker arms 18.19 are connected to the tenth rocker arm 1.
18 toward the intake cam 15 side, and the second rocker arm 19 toward the intake valve 5 side. Moreover, the elastic force of both helical springs 20 and 20 is equal to that of the valve spring 11. It is set stronger than that of L2. Therefore, the valve train camshaft 1
When the intake valve 4 rotates, its 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 body 13 that faces the upper surface of the spring retainer 9 and surrounds the valve shaft portion 5a of the intake valve 5 is fixed to the Norinda hemlock 1. An electromagnetic actuator A is configured together with a magnetic body 9 that also serves as a spring retainer. Also, the electromagnet body 13
2, a small diameter hole 2 that slides into contact with the valve stem 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 to the electromagnetic actuator and the spring force of the valve spring 11°I2 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.

A buffer mechanism D1 is provided between the intake valve 5 and an electromagnetic body 13 serving as a guide member for guiding the operation of the intake valve 5. This buffer mechanism includes a hydraulic chamber 3 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.
4 is provided. That is, the large diameter hole 2 of the through hole 30 is inserted into the upper end of the valve shaft portion 5a that is inserted into the through hole 30.
A camp-shaped valve piece 32 that is slidably fitted into the valve piece 32 is fitted, and a stepped portion 32a formed by this valve piece 32 and a stepped portion 3 between the small diameter hole 28 and the large diameter hole 29 are fitted.
A hydraulic chamber 34 is defined between 0a and 0a. Also, the through hole 30
An annular recess 31 is provided in the middle inner surface of the large diameter hole 29 in the electromagnetic body 13, and an oil supply hole 33 passing through the annular recess 31 is bored in the electromagnetic body 13, and the oil supply hole 33 is connected to an oil supply source (not shown). . Moreover, the outer surface of the valve stem portion 5a and the small diameter hole 2
A gap is formed between the inner surfaces of the hydraulic pressure chambers 9 to the extent that the hydraulic pressure in the hydraulic chamber 34 can leak when the hydraulic pressure in the hydraulic chamber 34 increases. Furthermore, the valve piece 32 is configured such that when the intake valve 5 is in the closed position, the upper part of the valve piece 32 is connected to the through hole 30.
The tappet screw 24 is fitted onto the valve shaft portion 5a so as to protrude upward from the upper end of the valve piece 3.
2.

In FIG. 4, a buffer mechanism D
2 is provided. . This buffer mechanism D2 includes a piston 51 that is slidably fitted into the second rocker arm 19, and is formed facing the back surface of the piston 51 to exert hydraulic pressure that brings the piston 51 into contact with the first rocker arm 18. A hydraulic chamber 52 is provided.

The first rocker arm 18 is provided with a protruding contact arm 53 that approaches the second rocker arm 19 when both the rocker arms 18 and 19 rotate due to the elastic force of the torsion spring 20.
A sliding hole 54 is formed in the second rocker arm 19 and opens opposite the corresponding reading 53 . A bottomed cylindrical sliding member 55 is slidably fitted into the sliding hole 54, and the piston 51 is fitted into the sliding member 55 so as to be relatively slidable therein. The hydraulic chamber 52 is defined between the piston 51 and the sliding member 55, and this hydraulic chamber 52 communicates with the inside of the sliding hole 54 through a throttle hole 56 provided at the closed end of the sliding member 55. It goes through. Further, a valve hole 57 is bored in the closed end of the sliding member 55 in parallel with the throttle hole 56, and a spherical valve body 58 that can open and close the valve hole 57 is provided in the hydraulic chamber 52. A spring 59 that urges the valve body 58 toward the closing side is housed therein.

A passage 60 communicating with the sliding hole 54 is bored in the second rocker arm 19, and this passage 60 connects the collar 22 and the sliding metal 21 to a hydraulic pressure supply passage 61 provided in the rocker shaft 1f. The hydraulic pressure supply path 6 is in constant communication through the
1 is connected to a hydraulic power source (not shown). Further, an accumulator 62 facing halfway into the passage 60 is disposed on the second rocker arm 19.

According to this buffer mechanism D2, when the contact arm 53 approaches the second rocker arm 19, the piston 51 is moved into the hydraulic chamber 52.
is driven in the direction of contracting the volume of the hydraulic chamber 52, and the hydraulic pressure inside the hydraulic chamber 52 increases.
It is discharged from 2.

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. Further, the control circuit C is manually supplied with detection signals such as engine speed, temperature, throttle opening, and intake air amount 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 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 intake cam 15 is in sliding contact with the first rocker arm 18, as shown in FIG. Before the spring retainer 9 becomes energized, the electromagnet 13 is energized under the control of the control circuit C.
A (Adsorb to petrification 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 in the clockwise direction in FIG. 1 also acts on the second rocker arm 19. However, as mentioned above, the spring force of the electromagnetic actuator A and the valve springs 11 and 12 is equal to the torsion springs 20 and 20.
6, the second rocker arm 19 is prevented from rotating, and as shown in FIG.
The first rocker arm 18 only rotates while twisting by 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, the vicinity of point P in FIG. When the power supply to the spring retainer 13 is cut off, the force that attracts the spring retainer 9 is released. Due to the dirt, the valve opening force accumulated in the torsion springs 20, 20 is suddenly released, and the intake valve 5 is suddenly opened due to the elastic force of the torsion springs 20, 20, as shown in FIG. , the valve opening riff l-1 is the fifth
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 when the piston is lower, 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 electromagnetic actuator A, in the buffer mechanism D1, the valve piece 32 is moved into the large diameter hole 2.
9, the hydraulic pressure is trapped in the hydraulic chamber 34 between the stepped portions 32a and 30a, so the downward movement speed of the valve piece 32, that is, the opening speed of the intake valve 5, is relaxed, and the trapped pressure is reduced. Hydraulic pressure is applied to the valve stem portion 5a and the small diameter hole 28
The intake valve 5 slowly opens in response to the gradual leakage from between the intake valves. In addition, in the buffer mechanism D2, the second rocker arm 19 rotates in the valve opening direction as the hydraulic pressure in the hydraulic chamber 52 is gradually discharged from the throttle hole 56, thereby moving the second rocker arm 19 toward the valve opening side. operation is relaxed. Therefore, by the action of both buffer mechanisms D+ and Dz, a drastic damping of the valve opening speed is achieved.

Moreover, the reason why the hydraulic shock absorbing effect is exerted in the J-:J machine mechanism is because the distance l (see FIG. 3) between the lower end of the annular four part 31 and the stepped part 32a in the large diameter hole 29 is This is the state in which the release energy of the torsion springs 20 and 20 is large near the maximum lift amount of the intake valve 5, whereas the buffer mechanism D2 is activated when the intake valve 5 is opened. It exerts a buffering effect while the valve is operating,
Both t''Jj-:ji a 4M DD2 compensate for each other's buffering effects, and the impact tZ 1M of the intake valve 5 can be effectively achieved.

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

Moreover, in the valve driving means 16, the torsion spring 20.20
It is possible to reduce the inertial weight by arranging around the Ronkan Yaft 17. Also, valve train cam #1
14 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 valve closing holding action by the electromagnetic actuator A can be performed at any timing, as shown by the thin 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 electromagnetic actuator A is constantly de-energized, the opening/closing timing can be obtained in accordance with the cam profile.
If the relative rotation of 8.19 is prevented, opening/closing timing that reliably follows the cam profile can be obtained.

Furthermore, if the electromagnetic actuator A is continued to be energized during the cam lift, the state on the valve body can be obtained.

FIG. 8 shows a third embodiment of the present invention, in which a buffer mechanism D3 is provided at the abutting portions of the first and second rocker arms 18,19.

The buffer mechanism D3 includes a piston 64 that is slidably fitted into the second rocker arm 19, and is formed facing the back surface of the piston 64 to exert hydraulic pressure that brings the piston 64 into contact with the first rocker arm 18. A hydraulic chamber 65 is provided.

A sliding hole 54 is formed in the second rocker arm 19 and opens to face the contact arm 53 of the first rocker arm 18 . A cylindrical piston 64 with a bottom is slidably fitted into the sliding hole 54, and a cylindrical sliding member 66 is fitted into the piston 64 so as to be relatively slidable therein. The hydraulic chamber 65 is defined between the piston 64 and the sliding member 66, and communicates with the inside of the sliding hole 54 through a gap between the piston 64 and the sliding member 66. Further, a valve hole 67 is bored in the sliding member 66.
A spherical valve body 68 that can open and close the valve hole 67 and a spring 69 that biases the valve body 68 toward the closing side are housed in the hydraulic chamber 65 . Further, the sliding member 66 is arranged so that the second rocker arm 1
9 is biased in the direction of fitting into the piston 64 by a spring 70 interposed between the piston 64 and the piston 64.

Further, the sliding hole 54 is connected to the rocker shirt 1 through the passage 60.
As in the first embodiment, an accumulator 62 is disposed in the middle of the passage 60 and is always in communication with the hydraulic pressure supply passage 61 in one fan.

According to this buffer mechanism D3, when the contact arm 53 approaches the second rocker arm 19, the piston 64 is moved into the hydraulic chamber 65.
is driven in the direction of contracting the volume of the hydraulic chamber 65, and the hydraulic pressure in the hydraulic chamber 65 increases, but this hydraulic pressure is discharged from the gap between the piston 64 and the sliding member 66 to the sliding hole 54, and the buffer of the first embodiment is It can achieve the same buffering effect as mechanism D2.

FIGS. 9 and 10 show a third embodiment of the present invention, in which a buffer mechanism D4 is provided at the abutting portions of the first and second rocker arms 18,19.

The buffer mechanism D4 includes a sphere 72 that is slidably fitted into the second rocker arm 19, and a hydraulic chamber 73 formed facing the back surface of the sphere 72. It is biased in the direction of abutting against the abutment arm 53 of the first rocker arm 18 .

A sliding hole 74 is bored in the second rocker arm 19, and the sphere 72 is fitted into this sliding hole 74. Moreover, at the opening end of the sliding hole 74, a regulating flange 75 for preventing the sphere 72 from falling out of the sliding hole 74 is provided over the entire circumference, and on the inner side of the regulating flange 75, the sphere is 72 is provided with a recess forming an annular gap 76 therebetween. Further, a passage 60 and a hydraulic chamber 73 provided in the second rocker arm 19
A valve hole 77 is provided in the second rocker arm 19 , and a spherical valve body 78 that can open and close the valve hole 77 and a spring 79 that biases the valve body 78 toward the closing side are connected to the hydraulic chamber 73 . stored inside.

In this buffer mechanism D4, when the sphere 72 is pushed in by the contact arm 53, the hydraulic pressure in the hydraulic chamber 72 leaks from the gap 76, and the moving speed of the sphere 72 is determined according to the amount of leakage, so when the valve is opened, The rotation speed of the second rocker arm 19 is reduced.

Figures 11, 12, 13, 14 and 15
The figure shows a fourth embodiment of the present invention, and parts 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 Ronca 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; The torsion springs 38, 38 are interposed between the dynamic plunger 37 and serve as elastic members for opening the valve.

The rocker arm 36 is supported by the four-pronged 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 locking nut 41 for fixing the position of the stopper 40 is screwed therein. 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 is provided between the rocker arm 36 and the stopper 40 fixed to the sliding plunger 37. A chamber 44 is provided, and the hydraulic chamber 44 communicates with a hydraulic pressure supply passage 61 in the rocker shaft 17 via a passage 49 bored in the rocker arm 36 .

This buffer mechanism performs a buffering effect when the sliding plunger 37 slides downward by leaking hydraulic pressure from the gap between the stopper 40 and the rocker arm 36.

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
By press-fitting the pusher 45 into the wedge hole 47 provided at the center of the arm member 46, the arm member 46 moves into the sliding plunger 37.
Fixed.

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

This torsion spring 3838 generates 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.

The other configurations are the same as in the first embodiment, and the adsorption force to the electromagnetic actuator and the spring force of the valve springs 11, 12 are set larger than the elastic forces of the torsion springs 3B and 38. In addition, the electromagnet body 13 and the valve shaft portion 5 of the intake valve 5
A buffer mechanism is provided between the three.

According to this fourth embodiment, by energizing the electromagnetic body I3 to the electromagnetic actuator, the sliding plunger 37 can be operated even when the mouth and arm 36 are 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 valve opening force accumulated in the torsion springs 3B, 3B is released by the electromagnetic actuator A. Accordingly, as shown in FIG. 15, the intake valve 5 can be suddenly opened by suddenly acting on the intake valve 5, and at this time, the valve opening operation speed is controlled by the buffer mechanism D5. It can be relaxed.

Further, in this fourth embodiment, in order to ensure the blood pressure relative to 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.

FIGS. 16, 17, and 18 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 1, 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 camp 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 that is shaped like a hollow cylinder with a bottom and is fitted into eight hollow cylinder parts so as to be vertically slidable, and a lifter lower part 91 as a first driving member that is connected to the lifter lower part 91 from the open upper part. A cap-shaped lifter upper part 92 as a second driving member that is slidably fitted, and a valve-opening elastic that is compressed between the lifter lower part 91 and the lifter lower part 92 and urges them to extend each other. Two lifter springs 93,94 as members and the lifter lower part 9
The set nut 95 is screwed onto the open upper part of the lifter 1 and engages with the upper limit position of the lower part 92 of the lifter.

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, in the downward direction.

The electromagnet body 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 D6 is provided between the lifter lower part 91 as an interlocking member that is interlocked and connected to the intake valve 5 and the support cylinder 86 as a guide member that guides the movement of the lifter lower part 91. A buffer mechanism D7 is provided between the lifter upper part 92 and the lifter upper part 92.

The buffer mechanism D6 connects the outer circumferential surface of the lifter lower part 91 and the support tube 36.
An annular hydraulic chamber 97 is provided between the inner circumferential wall of the
1 in the hydraulic chamber 97 and an oil supply [1] drilled in the support tube 86.
9B and the oil drain port 99 are in communication with each other, and the hydraulic chamber 97
A hydraulic circuit, such as an engine lubricating oil circuit, is communicated within the chamber 97, and pressure oil is circulated within the chamber 97.

The pressure oil that has flowed into the hydraulic chamber 97 is then transferred to the lifter lower part 41.
When the valve lifter 90 lifts by acting on the downward pressure receiving surface 1 (10) formed on the outer circumferential surface of the valve lifter 90, it provides a buffering effect and a lubricating effect to the valve lifter 90.

The buffer mechanism D7 includes a set number I integrated with the lifter lower part 91.
A hydraulic chamber 101 is provided between the □ 95 and the lifter upper part 92, and the hydraulic chamber 101 can communicate with the oil supply port 98 via a communication passage 102 bored in the lifter lower part 91.

In addition, the communication passage 102 communicates with the fuel filler port 98 when the lifter part 1) 2 is pushed down to the maximum extent while the intake valve 5 is held in the closed state, and the lower part 92 of the lifter is pushed down to the maximum extent. It is drilled into the lifter lower part 91 in such a way that communication with the fuel filler port 98 is cut off when the lifter lower part 91 is pushed down in a certain state.

According to this 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. At this time, the hydraulic chambers 97, 10
1 is filled with hydraulic pressure.

Next, when the state in which the valve is held in the closed position by the electromagnetic actuator A is released, the intake valve 5 is opened as shown in FIG. 17 due to the accumulated pressure and the spring force of the lock springs 93 and 94. Moreover, in response to the opening operation of the intake valve 5, hydraulic pressure is trapped in the hydraulic chamber 101 of the tension mechanism, and the hydraulic pressure is transmitted between the set nut 95 and the lifter upper part 92, and between the lifter lower part 91 and the lifter upper part 92. As the lifter lower part 91 is pushed down in response to leakage from the gap,
The opening operation of the intake valve 5 is relaxed. The damping action of this damping mechanism is effective over the entire lift range of the intake valve 5.

Further, when the lift amount of the intake valve 5 reaches a maximum value as shown in FIG. do. Therefore, the lifter springs 93,9
In a region where the energy released by the intake valve 4 increases, the opening operation of the intake valve 5 is relaxed by the buffering action of the buffering mechanism D7 and the buffering action of the buffering mechanism D6.

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

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. By rapidly opening the valve, pressurized exhaust gas flows into the exhaust system all at once, increasing exhaust inertia and improving exhaust efficiency, thereby increasing output.

According to one feature of the present invention as described in "C1 Effects of the Invention" and "2," the engine E driving means includes a valve opening elastic member (r:W) 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 by the valve-driving cam in the valve-opening elastic member. 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 valve driving means includes a valve driving means using an elastic force of an elastic member for opening the valve. Since a buffer mechanism is attached to alleviate the valve opening operation of the engine, by controlling the timing for releasing the holding state of the holding means, the optimum valve opening timing can be set according to the operating condition of the engine.
It is possible to increase the intake efficiency or exhaust efficiency by increasing the intake and exhaust inertia effects, and the function of the buffer mechanism alleviates the opening operation of the engine valve due to the elastic force of the valve opening elastic member, preventing damage to the engine valve. can be prevented.

According to another feature of the present invention, the valve driving means includes a valve-opening elastic member that exerts a resilient 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 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 engine valve or an interlocking member interlocked and connected to the engine valve, and the engine valve or A buffer mechanism is provided between the fixed guide member that guides the operation of the interlocking member and the buffer mechanism that relieves the valve opening operation of the engine valve due to the elastic force of the valve opening elastic member, so that it is difficult to release the holding state of the holding means. By controlling the valve opening timing, it is possible to set the optimum 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. The opening operation of the engine valve due to the elastic force of the elastic member can be alleviated, and damage to the engine valve can be prevented.

[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. A detailed enlarged view of the figure, FIG. 4 is a vertical sectional view of the main part showing the buffer mechanism attached to the valve driving means,
Fig. 5 is a line showing the relationship between the valve opening lift amount and the rotation angle of the valve drive cam, Fig. 6 is a vertical cross-sectional side view corresponding to Fig. 1 showing the valve closed position held by the holding means, and Fig. 7. 8 is a vertical sectional view corresponding to FIG. 1 showing a state in which holding is released by the holding means, FIG. 8 is a vertical sectional view of main parts corresponding to FIG. 4 of the second embodiment of the present invention, FIG. 9 and FIG. 9 shows a third embodiment of the present invention, FIG. 9 is a vertical cross-sectional view of the main part corresponding to FIG. 4, FIG. 10 is an enlarged view of the X section in FIG. 9, and FIGS. 11 is a longitudinal sectional side view, FIG. 12 is a view taken along the xn-xi line in FIG. 11, and FIG. 13 is a sectional view taken along the xm-xm line in FIG. 12. , FIG. 14 is a longitudinal sectional side view corresponding to FIG. 11 showing a state in which the valve is held in the closed position by the holding means, FIG. 15 is a longitudinal sectional side view corresponding to FIG. 11 showing a state in which the holding is released by the holding means, and FIG. 16 , 1st
7 and 18 show a fifth embodiment of the present invention, FIG. 16 is a longitudinal side view showing the state in which the valve closed position is held by the holding means, and FIG. 17 is a longitudinal side view showing the state in which the valve closed position is held by the holding means. No. 16 when the engine valve is released and the engine valve is in the process of opening.
FIG. 18 is a longitudinal side view corresponding to FIG. 16 when the engine valve is in a fully open state. 5... Intake valve as engine valve, 11.12... Valve spring, 15... Intake cam as valve operating cam, I6, 35
...Valve drive means, 18...First rocker arm, 19
...Second rocker arm, 20.38...Torsion spring as a valve opening elastic member, 34, 44.52, 65°7
3.97, 101... Hydraulic chamber, 36... Rocker arm as first driving member, 37... Sliding plunger as second driving member, 51.64... Piston, 72
. . . Sphere, 74 . . . Sliding hole, 86 . . . Support tube as a guide member, 90 .
...Lifter upper part as second driving member, 93.94
... Lifter spring as an elastic member for opening the valve, A ... Electromagnetic actuator as a holding means, D to D
7...Buffer mechanism, E...Engine body period Authorized by Kendo Ochiai, Honda Motor Co., Ltd. 1) Takashi Naka Figure 4 Figure 5 Valve camshaft rotation angle Figure 7 Figure 6 Figure 9 Figure 12 Figure 13 Figure 15 Figure 14

Claims (10)

[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 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 valve driving means includes a valve driving means that uses the elastic force of an elastic member for opening the valve. A valve control device for an internal combustion engine, characterized in that it is equipped with a buffer mechanism that alleviates valve opening operation. (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 buffer mechanism includes a contact portion between the driving members. The valve control device for an internal combustion engine according to item (1), characterized in that the device is provided in a valve control device for an internal combustion engine. (3) A buffer mechanism is provided 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 shock absorbing mechanism includes a piston slidably fitted to one of the first and second rocker arms, and a rear surface of the piston for exerting hydraulic pressure to bring the piston into contact with the other of the first and second rocker arms. 2. The valve control device for an internal combustion engine according to item (2), further comprising a hydraulic chamber formed facing the valve. (4) A buffer mechanism is provided 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 buffer mechanism includes a sliding hole formed in one of the first and second rocker arms, a spherical body that is slidably fitted into the sliding hole, and a spherical body that is inserted into the first and second rocker arms. A hydraulic chamber is formed facing the back of the sphere so as to be in contact with the other, and the hydraulic pressure in the hydraulic chamber is leaked between the outer surface of the sphere and the inner surface of the sliding hole when the sphere moves toward the inside of the sliding hole. The first (
The valve control device for an internal combustion engine according to item 2). (5) The amount of leakage between the rocker arm on the valve-driving cam side as the first driving member and the sliding plunger as the second driving member that is slidably supported on the rocker arm so as to come into contact with the engine valve. The valve control device for an internal combustion engine according to item (2), further comprising a buffer mechanism having a hydraulic chamber capable of restricting the pressure. (6) a lower part of the lifter on the engine valve side as a first driving member;
A buffer mechanism having a hydraulic chamber capable of limiting the amount of leakage is provided between the upper part of the lifter on the side of the valve operating cam serving as a second driving member that is slidably fitted to the lower part of the lifter. The valve control device for an internal combustion engine according to item (2). (7) 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 of the valve-driving cam in the valve-opening direction 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 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 mechanism, and the engine valve or an interlocking member interlocked and connected to the engine valve, and the engine valve or The operation of an internal combustion engine, characterized in that a buffer mechanism is provided between a fixed guide member that guides the operation of the interlocking member and that relieves the valve opening operation of the engine valve due to the elastic force of the valve opening elastic member. Valve control device. (8) The buffer mechanism is characterized in that a hydraulic chamber capable of limiting the amount of leakage is provided between a stepped portion formed at the upper end of the engine valve and a guide member that guides the operation of the engine valve. The valve control device for an internal combustion engine according to item (7). (9) The valve driving means includes a lower part of the lifter on the engine valve side, an upper part of the lifter that is slidably fitted to the lower part of the lifter, and an elastic member for opening the valve that is interposed between the lifter part and the upper part of the lifter. In the buffer mechanism, a hydraulic chamber capable of limiting the amount of leakage is provided between a lower part of the lifter as an interlocking member and a support cylinder as a guide member fixed to the cylinder head to guide movement of the lower part of the lifter. The valve control device for an internal combustion engine according to item (7), characterized in that: (10) The valve control device for an internal combustion engine as set forth in item (1) or item (7), wherein the holding means comprises an electromagnetic actuator.