JPH0617623A - Engine valve timing control device - Google Patents

Abstract

PURPOSE:To securely prevent the impact noise generated in an intake valve or an exhaust valve or the breakage of the suction valve or the exhaust valve when the intake valve or the exhaust valve is lifted by an oscillating cam. CONSTITUTION:A fundamental circular part where a valve is not lifted even when the fundamental circular part may directly or indirectly be brought into contact with the intake valve or the exhaust valve in a slidable manner, and a lift circular part to be formed adjacent to the fundamental circular part where the valve is lifted when the lift circular part may directly or indirectly be brought into contact with the valve are formed on a cam surface 12a of an oscillating cam 12. A buffer circular part to more gently lift the valve than the other part in the lift circular part when being brought into contact in a slidable manner is provided on the part of the lift circular part adjacent to the fundamental circular part.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve timing control device for an engine that changes the opening / closing timing of an intake valve or an exhaust valve according to the operating state of the engine.

[0002]

2. Description of the Related Art As a valve timing control device for an engine as described above, as disclosed in JP-A-55-137306, a drive cam that rotates in synchronization with the rotation of the engine and the drive cam. And a valve for intake / exhaust of the engine that swings in a state of sliding contact with the valve for intake / exhaust associated with the swing of the swing lever It is known to have a swinging cam for lifting.

The cam surface of the rocking cam in this engine valve timing control device is provided with a basic arc portion that does not lift the intake / exhaust valve even if it slides, and adjacent to the basic arc portion. A lift arc portion that lifts the intake / exhaust valve when it is slidably contacted is formed, and the lever ratio is changed by moving the swing center of the swing lever, thereby the intake / exhaust valve. The lift amount, and consequently the opening / closing time of the valve are changed. That is, when the swing center of the swing lever moves toward the swing cam, the lever ratio increases and the length of the portion of the drive cam that slides in contact with the swing lever expands to the vicinity of the nose portion. Therefore, the lift amount of the intake / exhaust valve increases and the opening time of the valve increases. On the other hand, when the swing center of the swing lever moves toward the drive cam, the lever ratio becomes smaller and the length of the portion of the drive cam that makes sliding contact with the swing lever is limited to the nose portion. Therefore, the lift amount of the valve is decreased and the opening time of the valve is shortened.

[0004]

However, in the above-described valve timing control device for an engine, the intake valve or the exhaust valve is lifted even if the cam surface of the swing cam is in sliding contact with the intake valve or the exhaust valve. A swing arc cam is formed that includes a basic arc portion that does not move and a lift arc portion that is provided adjacent to the basic arc portion and that lifts the intake valve or the exhaust valve when slidingly contacting the intake valve or the exhaust valve. The portion of the cam surface that is in sliding contact with the intake valve or the exhaust valve moves from the basic arc portion to the lift arc portion, and the intake valve or the exhaust valve lifts. In this case, since there is a slight clearance between the intake valve or exhaust valve and the swing cam, the part that is in sliding contact with the intake valve or exhaust valve moves from the basic arc part of the cam surface to the lift arc part. In the initial stage after the operation, the cam surface suddenly lifts the intake valve or the exhaust valve, so that an impact force is applied to the intake valve or the exhaust valve, and a shock noise is generated, or the intake valve or the exhaust valve is exhausted. There is a problem that the valve for use is damaged.

Therefore, it is also considered to provide a buffer portion for gently swinging the swing lever near the nose portion on the cam surface of the drive cam.

However, with the control of the valve timing, the swing center of the swing lever moves to the drive cam side or the swing cam side, and accordingly, there is an area where the cam surface of the drive cam slides on the swing lever. Therefore, even if a buffer portion is provided on the cam surface, the buffer portion may or may not be in sliding contact with the rocking lever. Therefore, the impact sound generated in the intake valve or the exhaust valve or the intake valve is generated. Alternatively, it is not possible to reliably prevent damage to the exhaust valve.

In view of the above, it is an object of the present invention to reliably prevent impact noise generated in an intake valve or an exhaust valve and damage to the intake valve or the exhaust valve. .

[0008]

In order to achieve the above-mentioned object, the invention according to claim 1 is such that another portion of the lift arc portion is adjacent to the basic arc portion of the lift arc portion of the cam surface of the swing cam. A buffer arc portion is provided for gently lifting the intake valve or the exhaust valve rather than the portion.

Specifically, the solution means taken by the invention of claim 1 is to oscillate in a state of directly or indirectly slidingly contacting an intake valve or an exhaust valve of an engine, and the intake valve or the exhaust is accompanied by the rocking. Rocking cam for lifting the valve for driving, rocking cam driving means for rocking the rocking cam, and the rocking cam and the rocking cam so that the opening / closing timing of the intake valve or the exhaust valve changes. A valve timing control device for an engine provided with a positional relationship changing means for changing a positional relationship with a driving means, and the cam surface of the swing cam is directly or indirectly connected to the intake valve or the exhaust valve. A basic arc portion that does not lift the intake valve or the exhaust valve even if it slides, and the intake valve or the exhaust valve is formed adjacent to the basic arc portion. A lift arc portion for lifting the intake valve or the exhaust valve by contact or indirect sliding contact is formed, and the intake valve or the exhaust valve is provided in a portion of the lift arc portion adjacent to the basic arc portion. A buffer circular arc portion is provided which gently lifts the intake valve or the exhaust valve when compared with other portions of the lift circular arc portion when directly or indirectly slidingly contacting the intake valve.

According to the second aspect of the present invention, the swing cam is swung by the drive cam which rotates following the camshaft, and the center of rotation of the drive cam is moved to move the intake valve or the exhaust valve. The opening / closing timing is changed. Specifically, in the structure of claim 1, the swing cam drive means includes a drive cam that abuts on the swing cam and swings the swing cam. The positional relationship varying means is a means for moving the rotation center of the driving cam, and is a camshaft having the structure.

According to the third aspect of the present invention, the swing cam is swung by the drive cam that rotates following the camshaft, and the basic arc portion of the swing cam is in sliding contact with the intake valve or the exhaust valve. The opening / closing timing of the intake valve or the exhaust valve is changed by changing the distance between the contact point that is in contact with the drive cam and the swing center of the swing cam when the valve is open. In the structure of claim 1, the rocking cam driving means is a cam shaft having a driving cam that abuts on the rocking cam to rock the rocking cam, and the positional relationship varying means is the rocking cam. A contact point where the rocking cam is in contact with the driving cam and a rocking center of the rocking cam when the basic arc portion of the moving cam is in direct or indirect sliding contact with the intake valve or the exhaust valve. Distance Is intended to add the configuration that a means for changing the.

According to a fourth aspect of the present invention, the swing cam is swung by the drive cam that rotates following the camshaft, and the reference line passing through the swing center of the swing cam and the basic arc of the swing cam. The intake valve or the exhaust valve is changed by changing the angle at which the straight line connecting the contact point of the drive cam and the swing center of the swing cam intersects when the portion is in sliding contact with the intake valve or the exhaust valve. The opening and closing timing of the valve for use is changed. Specifically,
In the structure of claim 1, the rocking cam driving means is a cam shaft having a driving cam that abuts on the rocking cam to rock the rocking cam, and the positional relationship varying means is the rocking cam. When the reference line passing through the swing center of the moving cam and the basic arc portion of the swing cam are in direct or indirect sliding contact with the intake valve or the exhaust valve, the swing cam acts as the drive cam. A structure is added which is a means for changing an angle at which a straight line connecting the contact point in contact with the swing center of the swing cam changes.

According to a fifth aspect of the present invention, the swing cam is swung by the drive cam that rotates following the camshaft, and the swing center of the swing cam is moved to thereby intake or exhaust the valve. For changing the opening and closing timing of, specifically, in the configuration of claim 1,
The rocking cam drive means is a cam shaft having a driving cam that abuts on the rocking cam to rock the rocking cam, and the positional relationship varying means sets the rocking center of the rocking cam. The configuration is added as a means for moving.

According to a sixth aspect of the present invention, the swing cam is swung by a crank mechanism including a crank that rotates following the camshaft and a crank arm that connects the crank and the swing cam. The intake valve or the exhaust valve timing of the engine is changed by changing the size of the radius of gyration of the connecting portion with the arm. Specifically, in the structure of claim 1, the swing cam is provided. The drive means is a cam shaft having a drive cam that abuts against the swing cam to swing the swing cam, and the positional relationship changing means is means for moving the swing center of the swing cam. This is to add the structure that there is.

According to a seventh aspect of the present invention, the rocking cam is rocked by a crank mechanism including a crank that rotates following the cam shaft and a crank arm that connects the crank and the rocking cam. The valve timing of the engine is changed by changing the distance between the connecting portion with the arm and the connecting portion with the crank arm and the swing cam. Specifically, in the configuration of claim 1, The oscillating cam driving means is a crank mechanism having a crank that is provided on the cam shaft and rotates together with the cam shaft, and a crank arm that connects the crank and the oscillating cam. A means for changing the distance between the connecting portion between the crank and the crank arm and the connecting portion between the crank arm and the swing cam. It is intended to add a cormorant configuration.

According to an eighth aspect of the present invention, the swing cam is swung by a crank mechanism including a crank that rotates following the cam shaft and a crank arm that connects the crank and the swing cam, and the crank rotates. A valve timing of the engine is changed by moving the center. Specifically, in the structure of claim 1, the swing cam drive means is provided on a cam shaft, and the crank rotates with the cam shaft. And a crank arm connecting the crank and the swing cam, and the positional relationship changing means is a means for moving the rotation center of the crank.

According to a ninth aspect of the present invention, the swing cam is swung by a crank mechanism including a crank that rotates following the camshaft and a crank arm that connects the crank and the swing cam. The valve timing of the engine is changed by changing the distance between the connecting portion with the rocking cam and the rocking center of the rocking cam. The dynamic cam driving means is a crank mechanism having a crank that is provided on the cam shaft and rotates together with the cam shaft, and a crank arm that connects the crank and the swing cam, and the positional relationship varying means is the crank mechanism. A structure is added to change the distance between the connecting portion of the arm and the swing cam and the swing center of the swing cam.

According to a tenth aspect of the present invention, the rocking cam is rocked by a crank mechanism including a crank that rotates following the cam shaft and a crank arm that connects the crank and the rocking cam. The valve timing of the engine is changed by changing the angle at which the reference line passing through the swing center of the and the straight line connecting the connecting part of the crank arm and the swing cam and the swing center of the swing cam intersect. Specifically, in the structure of claim 1, the swing cam driving means includes a crank that is provided on a cam shaft and rotates together with the cam shaft, and a crank arm that connects the crank and the swing cam. And a structure in which the positional relationship varying means is means for moving the swing center of the swing cam.

According to the eleventh aspect of the present invention, the swing cam is swung by the crank mechanism including the crank that rotates following the cam shaft and the crank arm that connects the crank and the swing cam, and the crank rotates. A valve timing of the engine is changed by moving the center. Specifically, in the structure of claim 1, the swing cam drive means is provided on a cam shaft, and the crank rotates with the cam shaft. And a crank arm that connects the crank and the swing cam, wherein the positional relationship varying means is means for moving the swing center of the swing cam. Is.

[0020]

According to the structure of claim 1, the intake valve or the exhaust valve is lifted more gently to the portion adjacent to the basic circular arc portion of the lift circular arc portion of the cam surface of the rocking cam than the other portions of the lift circular arc portion. Since the buffer arc portion is provided, the buffer arc portion is used for intake in the initial stage after the portion of the cam surface of the swing cam that is in sliding contact with the intake valve or the exhaust valve moves from the basic arc portion to the lift arc portion. Sliding contact with the valve or exhaust valve, the buffer arc part gently lifts the intake valve or exhaust valve.

According to the second aspect of the present invention, since the means for changing the valve timing by moving the rotation center of the drive cam is provided, when the rotation angle of the drive cam is a predetermined amount, the drive cam is changed. The angle of the oscillating cam changes with the movement of the rotation center, and the area of the cam surface of the oscillating cam slidingly contacting the intake valve or the exhaust valve changes accordingly, so the valve timing changes.

Further, since the rocking cam is directly driven by the driving cam, the rocking lever is not necessary and the sliding contact points are reduced.

According to the structure of claim 3, when the basic arc portion of the swing cam is in sliding contact with the intake valve or the exhaust valve, the contact point between the swing cam and the drive cam and the swing center of the swing cam. When the rotation angle of the drive cam is a predetermined amount due to the change in the distance between the contact point of the swing cam and the drive cam and the swing center of the swing cam, the rotation angle of the drive cam is a predetermined amount. The position of the contact point between the swing cam and the drive cam changes. Therefore, when the rotation angle of the drive cam is a predetermined amount, the angle of the rocking cam changes, and accordingly, the area of the cam surface of the rocking cam that slides on the intake valve or the exhaust valve changes. , Valve timing changes.

Further, as in the second aspect, since the rocking cam is directly driven by the driving cam, the rocking lever is not necessary and the sliding contact points are reduced.

According to the structure of claim 4, the rocking cam is driven when the reference line passing through the rocking center of the rocking cam and the basic arc portion of the rocking cam are in sliding contact with the intake valve or the exhaust valve. Since there is provided means for changing the angle at which the contact point contacting the working cam and the straight line connecting the swing center of the swing cam change, the contact point between the swing cam and the drive cam and swing of the swing cam As the angle of the straight line connecting to the center changes with respect to the reference line, the inclination of the swing cam with respect to the reference line changes when the rotation angle of the drive cam is a predetermined amount. Since the area of the cam surface that is in sliding contact with the intake valve or the exhaust valve changes, the valve timing changes. In this case, by selecting the angle of the straight line connecting the contact point of the swing cam with the drive cam and the swing center of the swing cam with respect to the reference line, only the basic arc portion on the cam surface of the swing cam is sucked. The lift arc portion can be set so as to be in sliding contact with the intake valve or the exhaust valve and not to be in sliding contact with the intake valve or the exhaust valve at all.

Further, as in the second aspect, since the rocking cam is directly driven by the driving cam, the rocking lever is not necessary and the sliding contact points are reduced.

According to the structure of claim 5, since the means for moving the swing center of the swing cam is provided, when the rotation angle of the drive cam is a predetermined amount, the swing center of the swing cam is moved. Along with this, the angle of the rocking cam changes, and the area of the cam surface of the rocking cam that is in sliding contact with the intake valve or the exhaust valve changes accordingly, so the valve timing changes.

Further, as in the second aspect, since the swing cam is directly driven by the drive cam, the swing lever is not necessary and the sliding contact points are reduced.

According to the sixth aspect of the present invention, there is provided means for changing the size of the radius of gyration of the connecting portion between the crank and the crank arm. Along with this, the eccentric amount between the rotation center of the crank and the connecting portion between the crank and the crank arm changes, so that the amplitude amount of the swing cam changes. As a result, the length of the region of the cam surface of the swing cam that is in sliding contact with the intake valve or the exhaust valve changes, and the valve timing changes accordingly.

Further, since the rocking cam is driven by the crank mechanism, the rocking lever is not necessary and the sliding contact points are reduced.

According to the structure of the seventh aspect, since the means for changing the distance between the connecting portion between the crank and the crank arm and the connecting portion between the crank arm and the swing cam is provided, the cam surface of the swing cam is provided. Since the area in sliding contact with the intake valve or exhaust valve changes, that is, the length of the area in which the basic arc portion of the cam surface slides in contact with the intake valve or exhaust valve, and the lift arc portion of the cam surface has the intake valve or Since the ratio of the length of the area in sliding contact with the exhaust valve changes, the valve timing changes accordingly.

Further, as in the sixth aspect, since the swing cam is driven by the crank mechanism, the swing lever is not necessary and the sliding contact points are reduced.

According to the structure of claim 8, since the means for moving the rotation center of the crank is provided, it is brought into sliding contact with the intake valve or the exhaust valve on the cam surface of the rocking cam in accordance with the movement of the rotation center of the crank. The region changes, and the valve timing changes accordingly.

Further, as in the sixth aspect, since the swing cam is driven by the crank mechanism, the swing lever is not necessary and the sliding contact points are reduced.

According to the structure of claim 9, the crank arm and the swing cam are provided with means for changing the distance between the connecting portion of the crank arm and the swing cam and the swing center of the swing cam. As the distance between the connecting portion and the swing center of the swing cam changes, the area of the cam surface of the swing cam that slides in contact with the intake valve or the exhaust valve changes, and the valve timing changes accordingly. .

Further, as in the sixth aspect, since the swing cam is driven by the crank mechanism, the swing lever is not necessary and the sliding contact points are reduced.

According to the structure of claim 10, the angle at which the reference line passing through the swing center of the swing cam and the straight line connecting the connecting portion between the crank arm and the swing cam and the swing center of the swing cam intersect with each other is defined as Since the means for changing is provided, the intake valve or the exhaust gas on the cam surface of the swing cam changes with the change of the angle at which the reference line and the straight line connecting the connecting portion and the swing center of the swing cam intersect. The area in sliding contact with the valve for use changes, and the valve timing changes accordingly.

Further, as in the sixth aspect, since the swing cam is driven by the crank mechanism, the swing lever is not necessary and the sliding contact points are reduced.

According to the eleventh aspect of the present invention, since the means for moving the swing center of the swing cam is provided, the intake valve or the intake valve on the cam surface of the swing cam is accompanied by the movement of the swing center of the swing cam. The area in sliding contact with the exhaust valve changes,
Along with this, the valve timing changes.

Further, as in the sixth aspect, since the rocking cam is driven by the crank mechanism, the rocking lever is not necessary and the sliding contact points are reduced.

[0041]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to the drawings, and the principle of the present invention will be described based on FIGS.

FIG. 1 shows a side surface shape of a swing cam 12 used in the present invention. The cam surface 12a of the swing cam 12 is directly or indirectly slidably contacted with an intake valve or an exhaust valve of an engine. A basic circular arc part that does not lift the valve and a lift arc part that is provided adjacent to the lift arc part and that lifts the intake valve or the exhaust valve when the valve directly or indirectly slides the valve. ,
A portion of the lift arc portion adjacent to the basic arc portion is a buffer arc that causes the valve to lift more gently than the other portions of the lift arc portion when directly or indirectly slidingly contacting the intake valve or the exhaust valve. Section is provided. Therefore, in the initial stage after the portion of the cam surface of the swing cam that is in sliding contact with the intake valve or the exhaust valve moves from the basic arc portion to the lift arc portion,
Since the buffer arc portion is in sliding contact with the intake valve or the exhaust valve, the valve lifts gently.

FIG. 2 shows a lift amount (indicated by a solid line), a lift speed (indicated by a broken line), and a lift acceleration when the cam surface of the swing cam is in sliding contact with the intake valve or the exhaust valve to lift the valve. (Indicated by a chain line). At the initial stage where the lift arc on the cam surface is in sliding contact with the intake valve or exhaust valve, the buffer arc is in sliding contact with the intake valve or exhaust valve, so the lift amount increases extremely slowly and the lift acceleration increases. Is a little positive and then becomes zero, so the lift speed is an extremely small value. Further, even at the final stage when the lift arc portion of the cam surface is in sliding contact with the intake valve or the exhaust valve, the buffer arc portion is in sliding contact with the intake valve or the exhaust valve, so the lift amount is extremely gently reduced,
Further, the lift acceleration is a value that slightly changes from zero to a positive value, so that the lift speed is an extremely small value.

In FIG. 3, as described in the section of the problem to be solved by the invention, in the case where a buffer portion for gently swinging the swing lever is provided near the nose portion on the cam surface of the drive cam. Shows the change in the lift amount in the drive cam, and the portion where the buffer portion of the drive cam is in sliding contact with the intake valve or the exhaust valve to gently lift the valve (the portion where the slope of the lift change curve is small) is the lift. When the amount of lift is large (indicated by a thick solid line), it appears, but when the amount of lift is small (indicated by a thin solid line), the buffer portion of the drive cam is absorbed by the basic arc portion of the swing cam. It doesn't appear because.

FIG. 4 shows a schematic configuration of a valve timing control device for an engine according to the first embodiment of the present invention.
In each of the following embodiments, the mechanism for varying the valve timing of the engine will be mainly described, and the description of the lift cushioning portion provided on the cam surface of the swing cam will be omitted. Cam surface 12 of the swing cam 12 at
The buffer arc portion described with reference to FIG. 1 is provided in a.

In FIG. 4, 10 is a valve for intake or exhaust of the engine, 11 is a lash adjuster for opening and closing the valve 10, and 12 is rocking in a state of sliding contact with the lash adjuster 11, and with rocking. A swing cam that lifts the valve 10 through the lash adjuster 11, 1
3 is a swing cam shaft that rotatably holds the swing cam 12, 14 is a drive cam that swings the swing cam 12 in accordance with the rotation, and 15 holds the drive cam 14, while rotating the engine body. A driving cam shaft 16 which is freely held, and a rocking cam 1 in a state where the driving cam shaft 16 is in contact with the driving cam 14.
A roller which is rotatably supported by 2 and rotates with the rotation of the drive cam 14 and swings the swing cam 12, and 17 biases the swing cam 12 toward the drive cam 14. This is a spring that keeps the roller 16 in contact with the driving cam 14 at all times.

On the cam surface 12a of the oscillating cam 12, there is a perfect circular basic arc portion 12b which does not lift the valve 10 even if it comes into sliding contact with the lash adjuster 11 and by extension the valve 10, that is, does not open the intake port or the exhaust port. A lift arc portion 12c is formed that lifts the valve 10 when slidingly contacting the valve 10, that is, opens the intake port or the exhaust port. As described above, although not shown, a buffer arc portion is provided in a portion of the lift arc portion 12b adjacent to the basic arc portion 12a.

FIGS. 4A and 4B show a state in which the center of rotation of the drive cam 14 moves between C1 and C2. As is clear from the figure, the rotation of the drive cam 14 The region in which the swing cam 12 swings when the drive cam 14 rotates by a predetermined amount changes as the center moves. In other words, when the rotation center of the drive cam 14 is at C2, the swing cam 1 is compared to when the rotation center is at C1.
When 2 oscillates by the same amount, the amount by which the basic arc portion 12b of the cam surface 12a of the oscillating cam 12 makes sliding contact with the upper surface of the lash adjuster 11 increases. With this,
The amount by which the lift arc portion 12c on the cam surface 12a slides on the upper surface of the lash adjuster 11 decreases, and the lift amount of the valve 10 decreases.

5 to 7 show a valve timing control system for an engine according to a second embodiment of the present invention.

In the second embodiment, a pair of left and right swing cams 12, 12 swings by one driving cam 14, and two intake or exhaust valves 10, 10 move up and down accordingly. It is a moving type.

In the second embodiment, the eccentric collar 18 between the drive cam shaft 15 and the drive cam 14 has its inner peripheral surface slidably contacting the outer peripheral surface of the drive cam shaft 15 and its outer peripheral surface. It is provided in a state of sliding contact with the inner peripheral surface of the driving cam 14. In addition, the drive camshaft 15
The external gear 15a is provided on the outer peripheral surface of the drive cam 14, and the internal gear 14a that meshes with the external gear 15a is provided on the inner peripheral surface of the drive cam 14. Further, a variable shaft 19 having a spur gear 19a on its outer peripheral surface is provided in parallel with the driving cam shaft 15, and a protrusion 18a is provided on the outer surface of the eccentric collar 18 and the protrusion 1 is provided.
8a has a spur gear 18 meshed with the spur gear 19a at the tip thereof.
b is provided.

The positional relationship changing means for moving the rotation center of the driving cam 14 by moving the rotation center of the driving cam 14 with respect to the driving cam shaft 15 by the eccentric collar 18 and the changing shaft 19 described above. When the variable shaft 19 is rotated, since the spur gear 19a of the variable shaft 19 and the spur gear 18a of the eccentric collar 18 mesh with each other, the eccentric collar 18 rotates. Since the drive cam 14 rotates relative to the drive cam shaft 15 while the external gear 15a of the drive cam shaft 15 and the internal gear 14a of the drive cam 14 mesh with each other, The center of rotation moves with respect to the drive camshaft 15. When the drive cam shaft 15 rotates, the drive cam 14 rotates in an eccentric state with respect to the drive cam shaft 15 and swings the swing cam 12, so that the opening / closing timing of the valve 10 changes.

FIG. 8 shows an engine valve timing control device according to a third embodiment of the present invention. The same members as those in the second embodiment are designated by the same reference numerals and their description is omitted.

In the third embodiment, the swing cam 12
In addition, a fork-shaped rocking engagement member 20 that projects toward the drive cam 14 and sandwiches the drive cam 14 is provided.
The rocking engaging member 20 and thus the rocking cam 12 rock together with the rotation of the driving cam 14. When the rocking engagement member 20 is provided as in the third embodiment, the basic arc portion 12b of the cam surface 12a of the rocking cam 12 is absorbed and invalidated without increasing the spring force of the spring 17 described above. The lift amount can be reduced.

FIG. 9 shows a valve timing control device for an engine according to a fourth embodiment of the present invention.

Also in the fourth embodiment, a pair of left and right swing cams 12, 12 swings by one driving cam 14, and two intake or exhaust valves 10, 10 move up and down accordingly. The movable arm 21 is a movable type and protrudes toward the drive cam 14 between the pair of rocking cams 12, 12.
Are integrally provided with the pair of swing cams 12, 12.
A roller 16 is rotatably provided on the swing arm 21, and the roller 16 is rotatably supported by the swing arm 21 while being in contact with the drive cam 14, and the roller 16 is rotated by the rotation of the drive cam 14. The roller 16 rotates and the swing arm 21 and thus the swing cam 12 swing.

The drive cam shaft 15 is formed in a square rod shape, and a drive arm 22 provided integrally with the drive cam 14 and having a rectangular through hole 22a is provided on the side surface of the drive cam 14. Between the driving cam shaft 15 and the driving arm 22, the inner surfaces of the two opposing sides are in sliding contact with the outer surface of the driving cam shaft 15 and the outer surfaces of the two sides orthogonal to the opposing two sides. Is provided with a pair of rectangular frame members 23, 23 that are in sliding contact with the inner surface of the through hole 22 a of the drive arm 22.

In the fourth embodiment, although not shown, moving means for moving the driving arm 22 and hence the driving cam 14 by a hydraulic type, an electric type or a gear mechanism is provided. Moving means and pair of frame members 2
3 and 23 constitute a positional relationship varying means for moving the rotation center of the drive cam 14 by moving the rotation center of the drive cam 14 with respect to the drive cam shaft 15, and actuating the moving means. When the drive cam shaft 15 is moved to rotate the drive cam shaft 15 in a state where the drive cam shaft 15 and the drive cam 14 are eccentric to each other, the opening / closing timing of the valve 10 changes. In this case, as shown in FIGS. 10A to 10E, the inner peripheral surfaces of the pair of frame members 23, 23 are in sliding contact with the outer peripheral surface of the driving cam shaft 15, and the outer peripheral surfaces thereof are the swinging arms. It is possible to rotate together with the drive cam shaft 15 in a state of sliding contact with the inner peripheral surface of the through hole 22a of 22 and transmit the rotational force to the drive cam 14.

11 and 12 show a valve timing control system for an engine according to a fifth embodiment of the present invention.

Also in the fifth embodiment, the pair of left and right swing cams 12 and 12 swing by the rotation of one drive cam 14,
Along with this, two intake or exhaust valves 10, 1
0 is a type that moves up and down, and a pair of swing cams 12,
A rocking arm 21 projecting toward the drive cam 14 is provided between the rocking cams 12 and 12 integrally with the rocking cams 12, 12. Both the drive camshaft 15 and the swing camshaft 13 are rotatably supported by a frame 24 rotatably held by the engine body 28, and the frame 24 is provided coaxially with the swing camshaft 13. An idle gear shaft 26 having an idle gear 25 formed of a spur gear is rotatably supported. Further, a spur gear 27 that meshes with the idle gear 25 is provided at one end of the drive camshaft 15, and the rotational force of the crankshaft (not shown) of the engine is applied to the idle gear shaft 26. After being transmitted, it is transmitted to the drive camshaft 15 via the idle gear 25 and the spur gear 27.

As shown in FIG. 12, the engine body 28 is provided with a piston member 29 slidably with respect to the engine body 28, and a bucket 30 is integrally formed at the lower end portion of the piston member 29. It is provided in. A coil spring 32 is compressed in a space 31 between the engine body 28 and the bucket 30, and oil is supplied to the space 31. When oil is supplied to the space 31, the piston member 29 is released. Descending frame 24
12 rotates clockwise in FIG. 12, and when the oil in the space 31 is returned, the piston member 29 rises and the frame 24 rotates counterclockwise.

By moving the drive camshaft 15 with respect to the engine body by the piston member 29, the bucket 30, the oil supplied to the space 31, and the coil spring 32, the rotation center of the drive cam 14 is moved. The positional relationship varying means for moving the spur gear 27 is configured to rotate and move the spur gear 27 along the idle gear 25.
Moves, and the opening / closing timing of the valve 10 changes.
In this case, since the spur gear 27 rotationally moves along the idle gear 25, the rotational force transmitted to the idle gear shaft 26 is transmitted via the spur gear 27 to the drive camshaft 15.
Be transmitted to.

13 and 14 show an engine valve timing control device according to a sixth embodiment of the present invention.

In the sixth embodiment, a pair of left and right swing cams 12, 12 swings by one driving cam 14, and two intake or exhaust valves move up and down accordingly. Is.

In the sixth embodiment, a pair of left and right swing arms 21 and 21 each having a long hole 21a are provided on the opposite side of the pair of left and right swing cams 12 and 12. A roller shaft 33 that rotatably supports the roller 16 passes through the long hole 21a, and the roller shaft 33 is slidable along the long hole 21a. The roller shaft 33 and the swing cam 12 have a first link member 34 whose upper end is rotatably connected to the roller shaft 33, and an upper end which is rotatably connected to a lower end of the first link member 34. The lower end is connected to the swing cam 12 via a link mechanism including a second link member 35 that is connected to the swing cam 12 so as to be relatively rotatable.

A hollow portion 36 extending in the axial direction of the swing cam shaft 13 is provided inside the lower ends of the pair of right and left swing cams 12, 12 and the second link member 35. Is provided with a spline shaft 37 extending in the axial direction of the swinging cam shaft 13 and having a linear projection 37a formed on the outer peripheral surface thereof. A helical recess 36 a extending in the axial direction of the swing camshaft 13 is formed on the inner peripheral surface of the second link member 35 in the hollow portion 36. Between the spline shaft 37 and the wall surface of the hollow portion 36, a helical convex strip 38a that meshes with the helical concave strip 36a of the hollow portion 36 is formed on the outer circumferential surface, and the convex projection of the spline shaft 37 is formed on the inner circumferential surface. A tubular member 38 having a linear recess 38b that meshes with the line 37a is provided.

The elongated hole 2 of the swing arm 21 described above
1a, the helical recess 36a of the hollow portion 36, the spline shaft 37, and the tubular member 38, the first link member 3
4 and the second link member 35 are changed to change the angle between the contact point of the roller 16 in contact with the driving cam 14 and the swing center of the swing cam 12 to change the positional relationship changing means. When the tubular member 38 moves in the axial direction of the swing camshaft 13, the second link member 35 rotates, so that the first link member 34 and the second link member
The angle at which the link member 35 intersects is changed, and accordingly, the roller shaft 33 moves along the elongated hole 21a, and the roller 16
Since the distance between the contact point with the driving cam 14 and the swing center of the swing cam 12 changes at, the opening / closing timing of the valve changes. In the above case, when the angle at which the first link member 34 and the second link member 35 intersect becomes large, the roller 16
The distance between the contact point with the drive cam 14 and the swing center of the swing cam 12 at the point of becomes larger, and the first link member 34 and the second link member
When the angle at which the link member 35 intersects becomes small, the roller 1
The distance between the contact point with the drive cam 14 and the swing center of the swing cam 12 in 6 is reduced.

FIG. 15 shows a valve timing control system for an engine according to a seventh embodiment of the present invention.

In the seventh embodiment, the rotation of one drive cam 14 causes one swing cam 12 to swing, and the swing arm 39 swings accordingly, so that one intake or exhaust air is used. This is a type in which the valve 10 is moved up and down.

In the seventh embodiment, the roller 16 is
A rack 40a is formed movably with respect to the swing cam 12, and a rack 40a is formed on a side surface thereof, and is rotatably held by an L-shaped holding member 40 extending in a direction orthogonal to the swing cam shaft 13. The rocking cam 12 and the rocking cam shaft 13 are connected to each other so as to be slidable in the axial direction and non-rotatable relative to each other.
A rack 13a extending in the axial direction of the swing camshaft 13 is formed on the side surface of the rack. Swing camshaft 1
In the vicinity of the intersection of 3 and the holding member 40, a first pinion 41a that meshes with the rack 13a of the swing camshaft 13 and a holding member that is coaxially and non-rotatably connected to the first pinion 41a. A pinion member 41 including a second pinion 41b that meshes with a rack 40a of 40.
Is provided.

By moving the holding member 40 holding the roller 16 with respect to the swing cam 12 by the rack 13a of the swing cam shaft 13, the rack 40a of the holding member 40, and the pinion member 41 described above. Positional relationship varying means for varying the distance between the contact point of the roller 16 in contact with the driving cam 14 and the swing center of the swing cam 12 is configured, and when the swing cam shaft 13 is moved in the axial direction thereof. Since the first pinion 41a and the second pinion 41b of the pinion member 41 rotate, the holding member 40 moves in the direction orthogonal to the axial direction of the swinging cam shaft 13, and contacts the roller 16 with the driving cam 14. And the swing center of the swing cam 12 changes, and the opening / closing timing of the valve changes.

FIG. 16 shows an engine valve timing control system according to the eighth embodiment of the present invention.

In the eighth embodiment, a pair of left and right swing cams 12, 12 swings by one driving cam 14, and two intake or exhaust valves move up and down accordingly. Is.

In the eighth embodiment, the roller 16 is a tip portion of the rectangular parallelepiped holding member 40 (upper end portion in FIG. 7).
On the other hand, the base end portion (lower end portion in FIG. 7) of the holding member 40 is rotatably held by the pair of left and right swing cams 1.
It is held so as to be able to move back and forth in a concave portion 42 formed between the two and twelve. A coil spring 43 is provided inside the recess 42, and the coil spring 43 urges the holding member 40 upward. An oil passage 13b is provided inside the swing camshaft 13, one end of the oil passage 13b communicates with the recess 42, and oil is supplied to the recess 42 through the oil passage 13b.

By the oil supplied to the coil spring 43 and the recess 42 described above, the holding member 40 holding the roller 16 is moved with respect to the swing cam 12 so that the roller 16 is in contact with the driving cam 15 of the roller 16. Positional relationship varying means for varying the distance between the contact point and the swing center of the swing cam 12 is configured, and by adjusting the pressure of the oil supplied to the concave portion 42, the holding member 40 and thus the roller 16 move, and Since the distance between the contact point with the driving cam 14 and the swing center of the swing cam 12 at 16 changes, the valve timing changes.

FIG. 17 shows an engine valve timing control system according to the ninth embodiment of the present invention.

The ninth embodiment is a type in which a pair of left and right swing cams 12, 12 swings by one driving cam 14, and two intake or exhaust valves move up and down accordingly. Is.

In the ninth embodiment, a horseshoe-shaped follower 46 is provided in place of the roller 16 of the eighth embodiment, and the follower 46 is provided at two places contacting the drive cam 14. Contact portions 46a and 46b are formed. The follower 46 is swingably held by a swing arm 21 that extends toward the drive cam 14 from between the pair of left and right swing cams 12, 12. Left and right rocking cams 12, 1
A cylinder portion 45 communicating with the oil passage 13b formed inside the swing camshaft 13 is provided between the two members, and a piston member 46 is slidably provided in the cylinder portion 45. Then, the piston member 46
Is urged toward the swing camshaft 13 side (lower side in FIG. 17) by the coil spring 43 housed inside the cylinder portion 45. In addition, the piston member 46
The follower 44 and the follower 44 are connected by two link members 47, 47 that are rotatably connected to each other, and the follower 44 swings as the piston member 46 moves up and down.

The oil supplied to the cylinder portion 45, the piston member 46, the two link members 47 and 47, the coil spring 43 and the cylinder portion 45 described above drives one of the two contact portions 44a and 44b of the follower 44. The positional relationship changing means is configured to change the distance between the contact point of the roller 16 in contact with the driving cam 15 and the center of swing of the swing cam 12 by changing the contact portion that contacts the use cam 14. If the pressure of the oil supplied to the cylinder portion 45 is adjusted, the piston member 46
Moves up and down, the follower 44 swings, and the contact portions 44a and 44b that come into contact with the drive cam 14 change accordingly. Therefore, the contact point between the follower 44 and the drive cam 14 and the swing cam 12 change. The distance from the swing center changes, and the opening / closing timing of the valve changes.

FIG. 18 shows a valve timing control system for an engine according to the tenth embodiment of the present invention.

In the tenth embodiment, one driving cam 14 is used.
The pair of left and right swing cams 12 and 12 swing, and two intake or exhaust valves move up and down accordingly.

In the tenth embodiment, a pair of left and right swing arms 21 and 21 extending toward the drive cam 14 is provided between the pair of left and right swing cams 12, 12, and one side (FIG. 9). An eccentric member 48, which is formed in a disk shape and has a gear 48a on its peripheral surface, is rotatably held by the swinging arm 21 on the front side of the eccentric member 48. The roller 16 is rotatably held. On the side where the eccentric member 48 is provided between the pair of left and right rocking cams 12, a cylinder portion 45 communicating with the oil passage 13b formed inside the rocking cam shaft 13 is provided. A piston member 46 is slidably provided on the cylinder portion 45. The piston member 46 includes a spur gear 48a of the eccentric member 48.
A rod member 49 having a spur gear 49a that meshes with is connected, and is urged toward the roller 16 (upper side in FIG. 18) by a coil spring 43 housed inside the cylinder portion 45.

The cylinder portion 45, the piston member 46, the gear 48a of the eccentric member 48, and the rod member 4 described above.
9, the oil supplied to the coil spring 43 and the cylinder portion 45 causes the eccentric member 48 to rotate with respect to the oscillating cam 12, so that the contact point of the roller 16 in contact with the driving cam 15 and the oscillating cam 12 swing. Positional relationship varying means for changing the distance from the center of motion is configured, and the rod member 49 moves up and down by adjusting the pressure of the oil supplied to the cylinder portion 45, and the eccentric member 48 rotates accordingly. Therefore, the rotation center of the roller 16 supported at a position eccentric to the rotation center of the eccentric member 48 moves, and the driving cam 14 on the roller 16 moves.
The distance between the contact point with and the swing center of the swing cam 12 changes,
The valve timing changes.

FIG. 19 shows a valve timing device for an engine according to the eleventh embodiment of the present invention.

In the eleventh embodiment, one driving cam 14 is used.
The pair of left and right swing cams 12 and 12 swing, and two intake or exhaust valves move up and down accordingly.

In the eleventh embodiment, a swing arm 21 extending toward the drive cam 14 is provided between the pair of left and right swing cams 12, 12 integrally with the pair of left and right swing cams 12. The roller 16 is rotatably held by the swing arm 21. The pair of right and left swing cams 12 and swing arms 18 are rotatably provided with respect to the swing cam shaft 13.

Inside the lower ends of the pair of right and left swing cams 12 and 12 and the swing arm 21, the swing cam shaft 1 is provided.
3 is provided with a hollow portion 36 extending in the axial direction, and the hollow portion 36 is provided with a spline shaft 37 extending in the axial direction of the swing cam shaft 13 and having a linear projection 37a formed on the outer peripheral surface thereof. It is arranged. A helical recess 36a extending in the axial direction of the swing camshaft 13 is formed on the inner peripheral surface of the hollow portion 36. Spline shaft 37
And the wall surface of the hollow portion 36, the helical convex strip 3 that meshes with the helical concave strip 36a of the hollow portion 36 on the outer peripheral surface.
8a is formed and the ridge 3 of the spline shaft 37 is formed on the inner peripheral surface.
A tubular member 38 having a linear recess 38b that meshes with the 7a is provided. An oil passage 13b for supplying oil to the inside of the hollow portion 36 is provided inside the swing camshaft 13.

The oil passage 13b and the hollow portion 3 described above
6, the helical recess 36a, the spline shaft 37, and the tubular member 38 cause the reference line passing through the swing center of the swing cam 12 and the basic arc portion 12b of the swing cam 12 in the swing cam 12 to move to the valve 10. When the sliding contact with the driving cam 14 and the straight line connecting the swing center of the swing cam are changed, the positional relationship changing means is configured to change the angle, and the hollow portion 36 is filled with the oil. When oil is supplied from the passage 13a to move the tubular member 38 in the axial direction of the swing cam shaft 13, the tubular member 38 rotates, and accordingly, the pair of left and right swing cams 12 and the swing arm 21.
Rotates with respect to the swing camshaft 13. Therefore, the reference line passing through the swing center of the swing cam 12 and the roller 1
The angle at which the straight line connecting the contact point with the driving cam 14 and the swing center of the swing cam 12 in 6 changes, and the valve timing changes.

FIG. 20 shows an engine valve timing device according to the twelfth embodiment of the present invention.

In the twelfth embodiment as well, one driving cam 14 is used.
The pair of left and right swing cams 12 and 12 swing, and two intake or exhaust valves move up and down accordingly.

Also in the twelfth embodiment, a swing arm 21 extending toward the drive cam 14 is provided between the pair of left and right swing cams 12, 12 integrally with the pair of swing cams 12, The roller 16 is rotatably held by the swing arm 21. The pair of swing cams 12 and swing arms 21 are provided so as to be rotatable relative to the swing cam shaft 13.

In the twelfth embodiment, a small diameter portion 13c having a smaller diameter than the other portions is provided at a portion of the swing cam shaft 13 that faces the pair of swing cams 12 and the swing arm 21. Between the pair of right and left swing cams 12, 12, the swing arm 21, and the small diameter portion 13c of the swing cam shaft 13, an eccentric collar 18 having a projecting portion 18a projecting toward the front side in FIG. 20 is provided. ,
The inner peripheral surface is provided so as to be in sliding contact with the outer peripheral surface of the small diameter portion 13c of the swing cam shaft 13, and the outer peripheral surface is in slidable contact with the inner peripheral surface of the swing cam 12. Further, the external gear 13 is provided on the outer peripheral surface of the small diameter portion 13c of the swing camshaft 13.
d is provided, and an internal gear 21a that meshes with the external gear 13d is provided on the inner peripheral surface of the swing arm 21.

Further, a cylinder member 50 for rotating the eccentric collar 18 with respect to the swing camshaft 13 is provided in the vicinity of the protruding portion 18a of the eccentric collar 18, and the cylinder member 50 and the cylinder portion 50a are provided. ,
A rod portion 50b slidably provided in the cylinder portion 50a, and a coil spring 5 for urging the rod portion 50b toward the cylinder portion bottom side (lower side in FIG. 20).
0c and the rod portion 50b on the cylinder head side (see FIG. 2).
0) and an oil reservoir 50d that urges it toward the upper side. The rod portion 50b of the cylinder member 50 is connected to the tip portion of the protruding portion 18a of the eccentric collar 18, and the eccentric collar 18 rotates as the rod portion 50b moves back and forth.

By the eccentric collar 18 and the cylinder member 50 described above, the reference line passing through the swing center of the swing cam 12 and the basic arc portion 12b of the swing cam 12 of the swing cam 12 are brought into sliding contact with the valve 10. The positional relationship changing means is configured to change the angle at which the contact point that is in contact with the drive cam 14 and the straight line that connects the swing center of the swing cam are intersected.

FIG. 21 shows a valve timing device for an engine according to the thirteenth embodiment of the present invention.

In the thirteenth embodiment, one driving cam 14 is used.
This is a type in which one rocking cam 12 rocks due to the rotation, and one intake or exhaust valve moves up and down accordingly.

In the thirteenth embodiment, the swing cam 12
Swinging arm 21 extending toward the driving cam 14 on the side surface of the
Is provided integrally with the swing cam 12, and the roller 16 is rotatably held by the swing arm 21. Also,
The swing cam 12 and the swing arm 21 are provided so as to be rotatable relative to the swing cam shaft 13.

In the second embodiment, a cylindrical shaft recess 13e is provided in a portion of the swing cam shaft 13 facing the swing cam 12, and the coil spring 13f is provided inside the shaft recess 13e. The pin member 13g biased radially outward by the is housed. A cylindrical first cam recess 12d and a second cam recess 12 having the same diameter as the shaft recess 13e are provided at positions on the swing cam 12 that can face the shaft recess 13e.
e is provided respectively, and the pin member 13g is provided with the first cam recess 12d or the second cam recess 12e by the relative rotation of the swing cam 12 and the swing cam shaft 13.
Can enter. In this case, the oil passage 13b formed inside the swinging camshaft 13 communicates with the first and second cam recesses 12d, 12e, and the first and second cam recesses 12d are formed through the oil passage 13b. , 12
By adjusting the pressure of the oil supplied to e, the pin member 13g retracts into the shaft recess 13e,
It is possible to advance to the cam concave portion 12d or the second cam concave portion 12e. Further, a protrusion 13h is provided on the side of the swing camshaft 13 opposite to the shaft recess 13e, and the protrusion 13h is engaged with a stopper recess 12f formed on the inner wall surface of the swing cam 12. As a result, the pin member 13g moves the first and second cam concave portions 1
It is easy to enter 2d and 12e. In this way, the swing cam 12 is supported by the swing cam shaft 13 so as to have a plurality of rotational angle positions with respect to the swing cam shaft 13.

The shaft recess 13e and the first portion described above
And second cam recesses 12d, 12e, pin member 13g,
The oil supplied to the coil spring 13f and the shaft recess 13e causes the swing cam 12 to select a predetermined rotation angle position from a plurality of rotation angle positions, so that a reference line passing through the swing center of the swing cam 12 is selected. And the basic arc portion 12b of the rocking cam 12 of the rocking cam 12 is in sliding contact with the valve 10, a straight line connecting the contact point in contact with the driving cam 14 and the rocking center of the rocking cam intersects. Positional relationship changing means for changing the angle is configured.

FIG. 22 shows an engine valve timing device according to the fourteenth embodiment of the present invention.

In the fourteenth embodiment, one driving cam 14 is used.
This is a type in which a pair of right and left swing cams 12 swings, and two intake or exhaust valves move up and down accordingly.

In the fourteenth embodiment, the pair of left and right rocking cams 12L and 12R includes one wide first cam member 12g provided at the center and the first cam member 12g.
Two narrow second cam members 12 arranged on both sides of the
h, 12h, the first cam member 12
The left side rocking cam 12L is constituted by the left side portion of g and the left side second cam member 12h.
A right side swing cam 12R is configured by the right side portion of g and the right side second cam member 12h. The first cam member 12g is fixed to the swing cam shaft 13, while the second cam member 12h is rotatably supported by the swing cam shaft 13. Also, the first and second
The above-described basic arc portion and lift arc portion are formed on the cam surfaces of the cam members 12g and 12h.

On both side surfaces of the first cam member 12g, a first pin recess similar to the shaft recess 13e is formed, and the first pin recess is similar to the pin member 13g. The pin member of is stored. Also, the second
When the first cam member 12g and the second cam member 12h have different rotational angle positions with respect to the swing cam shaft 13, the side surface of the cam member 12h on the first cam member 12g side is provided. A second pin recess is formed opposite to the first pin recess, and the tip end of the pin member housed in the first pin recess can advance and retreat to the second pin recess.

When the tip end of the pin member enters the second pin recess, the first cam member 12g and the second cam member 12h rotate in synchronization, and the pin member is used for the first pin. When housed in the recess, the second cam member 12h is rotatable with respect to the swing camshaft 13, and the second cam member 12h does not rotate in synchronization with the first cam member 12g. Therefore, the first cam member 12g
And the second cam member 12h rotate in synchronization with each other, the second cam member 12h comes into contact with the valve first to lift the valve, and the first cam member 12g and the second cam member 12h are lifted. 12h is not synchronized with the second cam member 12h even if the second cam member 12h contacts the valve.
Does not rotate and lift the valve, the valve lifts only when the first cam member 12g abuts.

With the pin member, the first pin concave portion provided in the first cam member 12g, and the second pin concave portion provided in the second cam member 12h described above, a plurality of cam members can be formed. Among them, a cam member having a predetermined rotation angle position with respect to the swing cam shaft 13 is brought into sliding contact with the valve, thereby forming a reference line passing through the swing center of the swing cam 12,
The basic arc portion 12b of the swing cam 12 in the swing cam 12
A positional relationship changing means is configured to change an angle at which a contact line contacting the driving cam 14 and a straight line connecting the swing center of the swing cam intersect with each other when the slide contact with the valve 10 is performed.

FIG. 23 shows a valve timing control system for an engine according to a fifteenth embodiment of the present invention.

In the fifteenth embodiment, one drive cam 14 is used.
The pair of left and right rocking cams 12, 12 rocks due to the rotation of the valve, and along with this, two intake or exhaust valves 1
It is a type in which 0 and 10 move up and down.

In the fifteenth embodiment, a swing arm 21 extending toward the drive cam 14 is provided between the pair of left and right swing cams 12, 12 integrally with the pair of left and right swing cams 12, 12. The roller 16 is rotatably held by the swing arm 21.

Both ends of the rocking cam shaft 13, which holds the pair of right and left rocking cams 12 and 12 and the rocking arm 21, are rotatably held by a frame 51 having a U-shape in plan view.

Although not shown in the figure, there is provided a drive means, which is composed of hydraulic pressure or a worm gear, for moving the frame 51 between the position shown by the solid line and the position shown by the chain double-dashed line. The frame 51 constitutes a positional relation varying means for moving the swing center of the swing cam 12, and the frame 5 is operated by operating the driving means.
1 is moved, the rocking cam shaft 13 and thus the rocking center of the rocking cam 12 moves, and along with this, the valve 1
The opening / closing timing of 0 changes.

FIG. 24 shows a valve timing control system for an engine according to the 16th embodiment of the present invention.

In the sixteenth embodiment, one driving cam 14 is used.
Is a type in which one swing cam 12 swings, and the swing arm 52 swings accordingly, so that the two intake valves 10 or exhaust valves 10 move up and down.

In the sixteenth embodiment, the swing arm 52 is swingably supported via the swing arm shaft 53, and its pressed surface 53a abuts on the cam surface 12a of the swing cam 12. Therefore, the rocking cam 12 rocks as the rocking cam 12 rocks, and the pressing portions 52b, 52b at the tips move the valves 10, 10 up and down.

On the upper surface of the swing cam 12, a swing arm 21 extending toward the drive cam 14 is provided integrally with the swing cam 12, and the roller 16 is rotatably held by the swing arm 21. .

Both ends of the swing cam shaft 13 that holds the swing cam 12 are rotatably supported by the upper ends of a pair of left and right support arms 54L and 54R extending in the vertical direction. The lower ends of the support arms 54L and 54R are connected by a support shaft 55, and the support shaft 55 is rotatably held by an engine body (not shown).

The spur gear 5 is attached to the lower end of the left support arm 54L.
6 is provided, and a worm gear 57 extending in a direction orthogonal to the left support arm 54L is provided below the left support arm 54L, and the worm gear 57 and the spur gear 56 mesh with each other.

The pair of left and right support arms 54 described above
The L, 54R, the support shaft 55, the spur gear 56, and the worm gear 57 constitute a positional relationship varying means for moving the swing center of the swing cam 12, and when the worm gear 57 is rotated, the spur gear 56 moves to the worm gear 57. It moves in the axial direction, and accordingly, the pair of left and right support arms 54L, 5
The upper end portion of 4R and thus the swing center of the swing cam 12 moves so that the cam surface 12a of the swing cam 12 moves along the pressed surface 52a of the swing arm 52.

25 and 26 show a valve timing control system for an engine according to a seventeenth embodiment of the present invention.

In the seventeenth embodiment, the swing camshaft 1 is used.
This is a type in which one swing cam 12 that is swingably provided via 3 swings by a crank mechanism to lift one intake or exhaust valve 10 via a lash adjuster 11.

In the seventeenth embodiment, the driving camshaft 15 is rotatably provided with the tubular member 58, and the driving camshaft 15 is provided with the crank member 59 so as to project therefrom. The crank member 59 rotates following the drive camshaft 15. Crank arm 60 for connecting the crank member 59 and the swing cam 12
The upper end of the crank member 59 is slidably fitted in a long hole 59a formed on one side surface of the crank member 59 and extending in the projecting direction of the crank member 59. It is rotatable with respect to the member 59. The lower end of the crank arm 60 is rotatably connected to the swing cam 12, and the swing cam 12 swings as the crank member 59 rotates.

The cylindrical member 58 is provided with a protruding portion 58a protruding along the crank member 59, and the protruding portion 58a is provided.
One side surface of the crank arm 60 is connected to one side surface of the upper end portion of the crank arm 60 via a link member 61, and a protrusion projecting on the other side surface of the protrusion 58a has a crank member 59.
It is slidably fitted in an arcuate hole 59b formed concentrically with the tubular member 58 on one side surface.

Due to the tubular member 58, the long hole 59a and the arcuate hole 59b of the crank member 59, and the link member 61 described above, the turning radius of the connecting portion between the crank member 59 and the crank arm 60 is increased. The positional relationship changing means for changing the height is configured, and when the cylindrical member 58 is rotated, the connecting portion between the projecting portion 58a and the link member 61 moves along the arcuate hole portion 59b, so that the crank arm 60 is provided. The upper end portion of moves along the long hole 59a. Therefore, the size of the radius of gyration of the connecting portion between the crank member 59 and the crank arm 60 changes, and the opening / closing timing of the valve 10 changes.

FIG. 27 shows a valve timing control system for an engine according to the 18th embodiment of the present invention.

In the eighteenth embodiment, the swing camshaft 1 is used.
This is a type in which one swing cam 12 swingably provided via 3 swings by a crank mechanism, and one intake or exhaust valve 10 is lifted via a lash adjuster 11.

In the eighteenth embodiment, the driving cam shaft 15 is rotatably provided with the tubular member 58, and the driving cam shaft 15 is provided with the crank member 59. It rotates following the drive camshaft 15.

The first spur gear 62 is fixed to the crank member 59 side of the tubular member 58, and the second spur gear 62 meshes with the first spur gear 62 on one side surface of the crank member 59.
The spur gear 63 of the second spur gear 63 is rotatably attached to the crank member 59, and the upper end portion of the crank arm 60 connecting the crank member 59 and the swing cam 12 has the second spur gear 63. The spur gear 63 is rotatably connected to a portion that is eccentric to the center of rotation. The lower end of the crank arm 60 is rotatably connected to the swing cam 12, and the swing cam 12 swings as the crank member 59 rotates.

By the tubular member 58, the first spur gear 62 and the second spur gear 63 described above, the crank member 59 is formed.
The positional relationship changing means for changing the size of the radius of gyration of the connecting portion between the crank arm 60 and the crank arm 60 is configured. When the tubular member 58 is rotated, the first spur gear 62 is rotated, and accordingly, the first spur gear 62 is rotated. Since the second spur gear 63 rotates, the connecting portion between the crank arm 60 and the second spur gear 63 rotates about the center of the second spur gear 63 as the center of rotation, and the crank arm 6
The upper end of 0 also rotates with the center of the second spur gear 63 as the center of rotation. Therefore, the size of the radius of gyration of the connecting portion between the crank member 59 and the crank arm 60 changes, and the opening / closing timing of the valve 10 changes.

FIG. 28 shows an engine valve timing control system according to the nineteenth embodiment of the present invention.

In the nineteenth embodiment, the swing camshaft 1 is used.
This is a type in which one swing cam 12 swingably provided via 3 swings by a crank mechanism, and one intake or exhaust valve 10 is lifted via a lash adjuster 11.

In the nineteenth embodiment, the driving camshaft 15 is provided with a pair of crank members 59, 59, and the pair of crank members 59 rotate following the driving camshaft 15.

The pair of crank members 59 and the swing cam 12 have a first crank arm member 60a whose one end is rotatably connected to the crank member 59 and one end which is connected to the other end of the first crank arm member 60a. A second rotatably connected second end rotatably connected to the swing cam 12.
Are connected by a crank arm 60 including a crank arm member 60b. Both ends of a connecting rod 60c for connecting the first crank arm member 60a and the second crank arm member 60b are rotatably held by a U-shaped frame 51, and the frame 51 is provided with hydraulic means (not shown). It is moved by a driving means such as a worm gear or a worm gear.

The first crank arm member 6 described above
0a, second crank arm member 60b, connecting rod 60c
The frame 51 constitutes a positional relationship varying means for changing the distance between the connecting portion between the crank member 59 and the crank arm 60 and the connecting portion between the crank arm 60 and the swing cam 12, and the drive means is When the frame 51 is actuated and moved, the crank arm 60 linearly bends or bends in a dogleg shape, so that the connecting portion between the crank member 59 and the crank arm 60, the crank arm 60 and the swing cam. Since the distance to the connecting portion with 12 changes, the opening / closing timing of the valve 10 changes.

FIG. 29 shows an engine valve timing control system according to the twentieth embodiment of the present invention.

The twentieth embodiment is a swing camshaft 1.
This is a type in which two swing cams 12 swingably provided via 3 swing by a crank mechanism to lift the two intake valves 10 and 10 for exhaust.

In the twentieth embodiment, the drive camshaft 15 is provided with a pair of crank members 59, 59, and the pair of crank members 59 rotate following the drive camshaft 15.

A swing arm 21 is integrally provided with the swing cam 12 between the pair of swing cams 12, 12, and the crank member 59 and the swing arm 21 are connected by a crank arm 60. There is.

Both the drive cam shaft 15 and the swing cam shaft 13 are rotatably supported by a frame 24 rotatably held in the engine body, and the frame 24 is coaxial with the swing cam shaft 13. An idle gear shaft 26 having an idle gear 25 formed of a spur gear is rotatably supported. A spur gear 27 that meshes with the idle gear 25 is provided at one end of the drive camshaft 15, and the rotational force of the crankshaft of the engine (not shown) is transmitted to the idle gear shaft 26 and then the idle gear 25 and It is transmitted to the drive camshaft 15 via the spur gear 27. Frame 24
Can be rotated about the rocking camshaft 13 by a driving means (not shown) including a hydraulic means and a worm gear.

The positional relationship varying means for moving the rotation center of the crank member 59 is constituted by the frame 24 and the driving means described above. When the driving means is operated to rotate the frame 24, the frame 24 and the crank member are rotated. The rotation center of 59 moves, and the opening / closing timing of the valve 10 changes. In this case, even if the frame 24 rotates, the spur gear 27 rotationally moves along the idle gear 25, so the rotational force transmitted to the idle gear shaft 26 is transmitted through the spur gear 27 to the drive camshaft 15.
Be transmitted to.

FIG. 30 shows a valve timing control system for an engine according to the 21st embodiment of the present invention.

In the twenty-first embodiment, the swing camshaft 1 is used.
This is a type in which one swing cam 12 swingably provided via 3 swings by a crank mechanism, and one intake or exhaust valve 10 is lifted via a lash adjuster 11.

In the twenty-first embodiment, the drive camshaft 15 is provided with a pair of crank members 59, 59, and the pair of crank members 59 rotate following the drive camshaft 15.

The rocking cam 12 is provided with a cam recess 12i having a rectangular cross section, and a moving member 64 having a bifurcated tip 64a having a rectangular cross section is slid in the cam recess 12i. It is provided freely. Although not shown in the drawings, a spring for urging the moving member 64 toward the inside of the cam recess 12i is provided inside the cam recess 12i, and the inside of the cam recess 12i swings the camshaft 1 for swinging.
3 is communicated with the oil passage 13b formed therein, and the moving member 64 can be moved back and forth with respect to the cam recess 12i by adjusting the pressure of the oil supplied through the oil passage 13b. A pair of crank member 59 and moving member 64
The front end portion 64a is connected by a crank arm 60.

By the pressure of the oil supplied to the cam concave portion 12i, the spring, and the cam concave portion 12i described above, the connecting portion between the crank arm 60 and the swing cam 12,
The positional relationship changing means for changing the distance from the swing center of the swing cam 12 is configured to move the moving member 64 to the swing cam 1.
2 by moving the crank arm 60
The distance between the connecting portion of the rocking cam 12 and the rocking center of the rocking cam 12 changes, and the opening / closing timing of the valve 10 changes.

FIG. 31 shows a valve timing control system for an engine according to the 22nd embodiment of the present invention.

The twenty-second embodiment is equivalent to the camshaft 1 for swinging.
Two rocking cams 12, which are swingably provided via
12 is a type that swings by a crank mechanism and lifts a valve for intake or exhaust through two lash adjusters 11, 11.

In the twenty-second embodiment, the driving camshaft 15 is provided with a pair of crank members 59, 59 so as to project, and the pair of crank members 59 follow the driving camshaft 15. Rotate.

A swing arm 21 is integrally provided with the swing cam 12 between the pair of swing cams 12, 12, and the crank member 59 and the swing arm 21 are connected by a crank arm 60. There is.

Inside the lower ends of the pair of right and left swing cams 12 and 12 and the swing arm 21, the swing cam shaft 1 is provided.
3 is provided with a hollow portion 36 that extends in the axial direction. It is set up. A helical recess 36a extending in the axial direction of the swing camshaft 13 is formed on the inner peripheral surface of the hollow portion 36. Between the spline shaft 37 and the wall surface of the hollow portion 36, a helical protrusion 38 that meshes with the helical recess 36a of the hollow portion 36 on the outer peripheral surface.
a is formed and the ridge 37 of the spline shaft 37 is formed on the inner peripheral surface.
A tubular member 38 having a linear recess 38b that meshes with a is provided.

An oil passage 13b for supplying oil into the hollow portion 36 is provided inside the swing cam shaft 13, and a tubular member 38 is provided in the oil passage 13b. A drive means for moving the shaft 13 in the axial direction is configured.

With the helical recess 36a of the hollow portion 36, the spline shaft 37, and the tubular member 38 described above, the reference line passing through the swing center of the swing cam 12, the crank arm 60, and the swing cam 12 are provided. The positional relationship changing means is configured to change the angle at which the straight line connecting the connecting portion of the rocking cam and the rocking center of the rocking cam 12 changes, and drives the driving means to move the tubular member 38 to the rocking camshaft 13. When moving in the axial direction of the rocking cam 12, the tubular member 38 rotates.
Since the swing arm 21 rotates with respect to the swing cam shaft 13, the reference line passing through the swing center of the swing cam 12, the connecting portion between the crank arm 60 and the swing cam 12, and the swing cam 12 are connected. The angle at which the straight line connecting the swing center intersects changes, and the opening / closing timing of the valve changes.

FIG. 32 shows a valve timing control system for an engine according to the 23rd embodiment of the present invention.

The twenty-third embodiment is equivalent to the swing camshaft 1.
One swing cam 12 that is swingably provided via 3 swings, and the swing arm 52 swings accordingly, and
This is a type in which the valves 10 and 10 for intake or exhaust of a book move up and down.

In the twenty-third embodiment, the driving camshaft 15 is provided with a pair of crank members 59, 59, and the pair of crank members 59 rotate following the driving camshaft 15.

A swing arm 21 is provided integrally with the swing cam 12 on the upper surface of the swing cam 12, and the pair of crank members 59 and the swing arm 21 are connected by a crank arm 60. .

The swing arm 52 is swingably supported via the swing arm shaft 52, and its pressed surface 52a is the cam surface 12a of the swing cam 12.
The rocking cam 12 rocks as the rocking cam 12 rocks, and the pressing portions 52b, 52b at the tips move the valves 10, 10 up and down.

Further, both ends of the swing cam shaft 13 that holds the swing cam 12 are rotatably supported by the upper ends of a pair of left and right support arms 54L and 54R extending in the vertical direction. The lower ends of the support arms 54L and 54R are connected by a support shaft 55, and the support shaft 54 is rotatably held by an engine body (not shown).

The spur gear 5 is attached to the lower end of the left support arm 54L.
6 is provided, and a worm gear 57 extending in a direction orthogonal to the left support arm 54L is provided below the left support arm 54L, and the worm gear 57 and the spur gear 56 mesh with each other.

The pair of left and right support arms 54 described above
The L, 54R, the support shaft 54, the spur gear 56, and the worm gear 57 constitute a positional relationship varying means for moving the swing center of the swing cam 12, and when the worm gear 57 is rotated, the spur gear 56 moves to the worm gear 57. It moves in the axial direction, and accordingly, the pair of left and right support arms 54L, 5
The upper end portion of 4R and thus the swing center of the swing cam 12 moves so that the cam surface 12a of the swing cam 12 moves along the pressed surface 52a of the swing arm 52, so the opening / closing timing of the valve 10 changes. To do.

[0159]

As described above, according to the valve timing control device for an engine of the first aspect of the present invention, the lift arc portion is adjacent to the basic arc portion of the lift arc portion of the cam surface of the swing cam. Since a buffer arc portion that gently lifts the intake valve or the exhaust valve is provided compared to the other portions in, the portion of the swing cam that makes sliding contact with the intake valve or exhaust valve is lifted from the basic arc portion. In the initial stage after moving to the engine part, the buffer arc part slides in contact with the intake valve or exhaust valve, and the buffer arc part gently lifts the intake valve or exhaust valve. No impact force is applied to the valve. For this reason,
According to the first aspect of the present invention, it is possible to reliably prevent the impact sound generated when the swing cam comes into sliding contact with the intake valve or the exhaust valve and the damage to the intake valve or the exhaust valve.

According to the engine valve timing control device of the second aspect of the present invention, the swing angle of the swing cam when the rotation angle of the drive cam is a predetermined amount as the rotation center of the drive cam moves. Is changed, and the region of the cam surface of the swing cam that is in sliding contact with the intake valve or the exhaust valve is changed accordingly, so that the valve timing of the engine can be controlled easily and reliably.

According to the valve timing control device for an engine of the third aspect of the invention, when the basic arc portion of the swing cam is in sliding contact with the intake valve or the exhaust valve, the swing cam and the drive cam of the swing cam are in contact with each other. When the distance between the contact and the swing center of the swing cam changes, the position of the contact point between the swing cam and the drive cam changes when the rotation angle of the drive cam is a predetermined amount. Since the area of the cam surface of the moving cam that is in sliding contact with the intake valve or the exhaust valve changes, the valve timing of the engine can be controlled easily and reliably.

According to the engine valve timing control device of the fourth aspect of the present invention, the reference line passing through the swing center of the swing cam and the basic arc portion of the swing cam are in sliding contact with the intake valve or the exhaust valve. When the rotation angle of the drive cam is a predetermined amount as the angle at which the contact point where the swing cam is in contact with the drive cam and the straight line connecting the swing center of the swing cam intersect with each other The inclination of the rocking cam with respect to the reference line changes, and the area of the cam surface of the rocking cam in sliding contact with the intake valve or the exhaust valve changes accordingly, so that the valve timing of the engine can be controlled easily and reliably. Can be done.

By selecting the angle of the straight line connecting the contact point of the swing cam with the drive cam and the swing center of the swing cam with respect to the reference line, only the basic arc portion on the cam surface of the swing cam is selected. Can be set to be in sliding contact with the intake valve or the exhaust valve, so that the stopped state of the intake valve or the exhaust valve can be easily obtained.

According to the valve timing control device for an engine of the fifth aspect of the invention, the swing cam swings when the rotation angle of the drive cam is a predetermined amount as the swing center of the swing cam moves. The angle of rotation changes, and the region of the cam surface of the swing cam that slides in contact with the intake valve or the exhaust valve changes accordingly, so that the valve timing of the engine can be controlled easily and reliably.

According to the valve timing control device for an engine of the present invention, the drive cam supported by the camshaft causes the swing cam to swing with the rotation of the camshaft. Since the number of contact points is reduced, the mechanical resistance is reduced, the clearance of the sliding contact points is easily managed, and the rigidity of the force transmission system is improved, so that the rotation limit of the engine is improved.

According to the valve timing control device for an engine of the sixth aspect of the present invention, the center of rotation of the crank and the crank and the crank arm are changed according to the change in the radius of rotation of the connecting portion between the crank and the crank arm. The amount of eccentricity with the connecting part changes, the amplitude of the rocking cam changes accordingly, and the length of the area of the cam surface of the rocking cam that makes sliding contact with the intake valve or exhaust valve changes easily. In addition, it is possible to reliably control the valve timing of the engine.

According to the valve timing control device for an engine of the seventh aspect of the present invention, the rocking cam is associated with a change in the distance between the connecting portion between the crank and the crank arm and the connecting portion between the crank arm and the rocking cam. Since the area of the cam surface that is in sliding contact with the intake valve or the exhaust valve changes, the valve timing of the engine can be controlled easily and reliably.

According to the valve timing control device for an engine of the eighth aspect of the present invention, the area of the cam surface of the swing cam that slides on the intake valve or the exhaust valve changes with the movement of the rotation center of the crank. The valve timing of the engine can be controlled easily and reliably.

According to the valve timing control device for an engine of the ninth aspect of the present invention, the swing cam of the swing cam changes as the distance between the connecting portion of the crank arm and the swing cam and the swing center of the swing cam changes. Since the area of the cam surface that is in sliding contact with the intake valve or the exhaust valve changes, the valve timing of the engine can be controlled easily and reliably.

According to the valve timing control device for an engine of the tenth aspect of the invention, the reference line passing through the swing center of the swing cam, the connecting portion between the crank arm and the swing cam, and the swing center of the swing cam are provided. The area of the cam surface of the rocking cam that is in sliding contact with the intake valve or the exhaust valve changes with the change in the angle at which the straight line connecting the it can.

According to the valve timing control device for an engine of the eleventh aspect of the present invention, the region of the cam surface of the rocking cam which is in sliding contact with the intake valve or the exhaust valve along with the movement of the rocking center of the rocking cam. Because of the change, the valve timing of the engine can be controlled easily and reliably.

According to the valve timing control device for an engine of the sixth to eleventh aspects of the present invention, the engine is provided with a crank mechanism including a crank and a crank arm, and the swing cam is pulled up by the crank arm to swing the swing cam. Since the rocking cam rocks in accordance with the rotation of the crank, it is possible to obtain a sufficient lift amount of the intake valve or the exhaust valve, and the rocking lever becomes unnecessary, so that the sliding contact is made. Since the number of points is reduced and the rigidity of the force transmission system is improved, the rotation limit of the engine is improved. Further, since the sliding contact points are reduced as described above, the mechanical resistance is reduced and the clearance of the sliding contact points is easily managed.

[Brief description of drawings]

FIG. 1 is a side view showing the shape of a swing cam used in the present invention.

FIG. 2 is an explanatory diagram illustrating an operation of the present invention.

FIG. 3 is an explanatory diagram illustrating an operation when a driving cam that is considered in the process of reaching the present invention is used.

FIG. 4 is a schematic diagram of a valve timing control device for an engine according to a first embodiment of the present invention.

FIG. 5 is a sectional view showing a valve timing control device for an engine according to a second embodiment of the present invention.

FIG. 6 is a sectional view showing a part of a valve timing control device for an engine according to the second embodiment.

FIG. 7 is a sectional view showing a valve timing control device for an engine according to the second embodiment.

FIG. 8 is a sectional view showing a valve timing control device for an engine according to a third embodiment of the present invention.

FIG. 9 is a cutaway perspective view showing an engine valve timing control device according to a fourth embodiment of the present invention.

FIG. 10 is a cross-sectional view showing the operation of the valve timing control device for the engine according to the fourth embodiment.

FIG. 11 is a partially cutaway perspective view showing a valve timing control device for an engine according to a fifth embodiment of the present invention.

FIG. 12 is a sectional view showing a valve timing control device for an engine according to the fifth embodiment.

FIG. 13 is a cutaway perspective view showing a valve timing control device for an engine according to a sixth embodiment of the present invention.

FIG. 14 is a partially cutaway perspective view showing a main part of a valve timing control device for an engine according to the sixth embodiment.

FIG. 15 is a cutaway perspective view showing a valve timing control device for an engine according to a seventh embodiment of the present invention.

FIG. 16 is a partially cutaway perspective view showing a valve timing control device for an engine according to an eighth embodiment of the present invention.

FIG. 17 is a partially cutaway perspective view showing a valve timing control device for an engine according to a ninth embodiment of the present invention.

FIG. 18 is a partially cutaway perspective view showing a valve timing control device for an engine according to a tenth embodiment of the present invention.

FIG. 19 is a partially cutaway perspective view showing a valve timing control device for an engine according to an eleventh embodiment of the present invention.

FIG. 20 is a partially cutaway perspective view showing a valve timing control device for an engine according to a twelfth embodiment of the present invention.

FIG. 21 is a partially cutaway perspective view showing a valve timing control device for an engine according to a thirteenth embodiment of the present invention.

FIG. 22 is a cutaway perspective view showing a valve timing control device for an engine according to a fourteenth embodiment of the present invention.

FIG. 23 is a cutaway perspective view showing a valve timing control device for an engine according to a fifteenth embodiment of the present invention.

FIG. 24 is a cutaway perspective view showing a valve timing control device for an engine according to a sixteenth embodiment of the present invention.

FIG. 25 is a partial cutaway perspective view showing a valve timing control device for an engine according to a seventeenth embodiment of the present invention.

FIG. 26 is a sectional view showing a valve timing control system for an engine according to the seventeenth embodiment.

FIG. 27 is a cutaway perspective view showing a valve timing control device for an engine according to an eighteenth embodiment of the present invention.

FIG. 28 is a partially cutaway perspective view showing a valve timing control device for an engine according to a nineteenth embodiment of the present invention.

FIG. 29 is a partially cutaway perspective view showing a valve timing control device for an engine according to a twentieth embodiment of the present invention.

FIG. 30 is a cutaway perspective view showing a valve timing control device for an engine according to a 21st embodiment of the present invention.

FIG. 31 is a partially cutaway perspective view showing a valve timing control device for an engine according to a 22nd embodiment of the present invention.

FIG. 32 is a cutaway perspective view showing a valve timing control device for an engine according to a 23rd embodiment of the present invention.

[Explanation of symbols]

 10 intake or exhaust valve 11 lash adjuster 12 swing cam 12a cam surface 12b basic arc portion 12c lift arc portion 13 swing camshaft 13a rack 13b oil passage 14 drive cam 15 drive camshaft 18 eccentric collar 19 variable Shaft 20 Swing engaging member 21 Swing arm 21a Long hole 23 Frame member 24 Frame 29 Piston member 30 Bucket 31 Space portion 34 First link member 35 Second link member 36 Hollow portion 36a Helical recess 37 Spline shaft 37a Linear convex strip 38 Cylindrical member 38a Helical convex strip 38b Linear concave strip 39 Swing arm 40 Holding member 41 Pinion member 42 Recess 43 Coil spring 44 Follower 45 Cylinder member 46 Piston member 47 Link Material 48 Eccentric member 49 Rod member 50 Cylinder member 51 Frame 52 Swing arm 54L 54R Support arm 55 Support shaft 56 Spur gear 57 Worm gear 58 Cylindrical member 59 Crank member 60 Crank arm 60a First crank arm member 60b Second crank arm Member 60c Connecting rod 61 Link member 62 First spur gear 63 Second spur gear 64 Moving member

Claims (11)

[Claims] 1. A swing cam that swings in a state of directly or indirectly slidingly contacting an intake valve or an exhaust valve of an engine and lifts the intake valve or the exhaust valve with the swing, and the swing. A rocking cam drive means for rocking the cam, and a positional relationship changing means for changing the positional relationship between the rocking cam and the rocking cam driving means so that the opening / closing timing of the intake valve or the exhaust valve changes. A valve timing control device for an engine, comprising: an intake valve or an exhaust valve on the cam surface of the rocking cam, even if the intake valve or the exhaust valve slides directly or indirectly. The basic arc portion that is not lifted and the intake valve that is formed adjacent to the basic arc portion and directly or indirectly slidably contacts the intake valve or the exhaust valve. Is formed with a lift arc portion for lifting the exhaust valve, and a portion of the lift arc portion adjacent to the basic arc portion when directly or indirectly slidably contacting the intake valve or the exhaust valve. A valve timing control device for an engine, further comprising: a buffer arc portion for gently lifting the intake valve or the exhaust valve as compared with other portions of the lift arc portion. 2. The swing cam drive means is a cam shaft having a drive cam that abuts on the swing cam to swing the swing cam, and the positional relationship changing means is the drive cam. The valve timing control device for an engine according to claim 1, wherein the valve timing control device is means for moving a rotation center of the engine. 3. The rocking cam driving means is a cam shaft having a driving cam that abuts on the rocking cam to rock the rocking cam, and the positional relationship varying means is the rocking cam. The distance between the contact point where the rocking cam is in contact with the drive cam and the rocking center of the rocking cam when the basic circular arc portion of the rocking cam is in direct or indirect sliding contact with the intake valve or the exhaust valve. 2. The valve timing control device for an engine according to claim 1, wherein the valve timing control device is a unit that changes the valve timing. 4. The swing cam drive means is a cam shaft having a drive cam that abuts on the swing cam to swing the swing cam, and the positional relationship changing means is the swing cam. When the reference line passing through the center of swing of the swing cam and the basic arc portion of the swing cam are in direct or indirect sliding contact with the intake valve or the exhaust valve, the swing cam is in contact with the drive cam. The engine valve timing control device according to claim 1, wherein the valve timing control device is means for changing an angle at which a straight line connecting the contact point and the swing center of the swing cam intersects. 5. The swing cam drive means is a cam shaft having a drive cam that abuts on the swing cam to swing the swing cam, and the positional relationship changing means is the swing cam. 2. The valve timing control means for an engine according to claim 1, wherein the valve timing control means is means for moving the swing center of the. 6. The swing cam driving means comprises a crank provided on a cam shaft and rotating with the cam shaft,
It is a crank mechanism having a crank arm connecting the crank and the swing cam, and the positional relationship changing means is means for changing a size of a radius of gyration of a connecting portion between the crank and the crank arm. The valve timing control means for an engine according to claim 1, wherein: 7. The swing cam driving means comprises a crank provided on a cam shaft and rotating together with the cam shaft,
A crank mechanism having a crank arm connecting the crank and the swing cam, wherein the positional relationship changing means includes a connecting portion between the crank and the crank arm,
2. The valve timing control means for an engine according to claim 1, wherein the valve timing control means is means for changing a distance between a connecting portion of the crank arm and the swing cam. 8. The swing cam driving means comprises a crank provided on a cam shaft and rotating together with the cam shaft,
The crank mechanism having a crank arm that connects the crank and the swing cam, and the positional relationship changing means is means for moving a rotation center of the crank. Engine valve timing controller. 9. The swing cam driving means comprises a crank provided on a cam shaft and rotating with the cam shaft,
A crank mechanism having a crank arm connecting the crank and the swing cam, wherein the positional relationship changing means includes a connecting portion between the crank arm and the swing cam, and a swing center of the swing cam. 2. The valve timing control device for an engine according to claim 1, wherein the valve timing control device is a unit that changes the distance. 10. The swing cam drive means is a crank mechanism having a crank that is provided on a cam shaft and rotates together with the cam shaft, and a crank arm that connects the crank and the swing cam. The relationship changing means changes the angle at which the reference line passing through the swing center of the swing cam and the straight line connecting the connecting portion between the crank arm and the swing cam and the swing center of the swing cam intersect. The valve timing control device for the engine according to claim 1, wherein the valve timing control device is a means for causing the valve timing control device. 11. The oscillating cam driving means is a crank mechanism having a crank provided on a cam shaft and rotating together with the cam shaft, and a crank arm connecting the crank and the oscillating cam. 2. The valve timing control means for an engine according to claim 1, wherein the relationship varying means is means for moving the swing center of the swing cam.