JP2586631Y2 - Intake and exhaust valve drive control device for internal combustion engine - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an intake / exhaust valve drive control device for variably controlling the opening / closing timing of intake / exhaust valves according to the operating state of an internal combustion engine.

[0002]

2. Description of the Related Art Various conventional apparatuses of this kind are provided, one of which is, for example, Japanese Utility Model Laid-Open No. 57-198.
No. 306 is known.

[0003] Referring to FIGS. 11 and 12 , an outline 2 is provided on the outer periphery of a camshaft 1 so that an intake valve 16 is opened against a spring force of a valve spring 17. A cam to be operated.
Is a key 4 on the cam bearing bracket 3 and the cam shaft 1.
Axial positioning is performed by the flange portion 5 fixed via the through hole. A flange 7 having a U-shaped groove 6 is formed on one side of the cam 2, and a U-shaped groove 8 is also formed on the flange 5, so that both flanges 5 are formed.
An annular disk 9 is interposed between 7. The disc 9 is provided with pins 10 and 11 for engaging the U-shaped grooves 6 and 8 at opposing positions on both sides, and the outer periphery thereof is rotatably supported by a control ring 12. This control ring 12
Is swingably supported by a support hole 13 on the cylinder head side via a projection 12a on the outer periphery.
a of the rocker shaft 14
It meshes with the outer gear ring 14a.

The control ring 12 is configured to swing in one or the other direction in the radial direction by a drive mechanism (not shown) via a gear ring 14a and a gear portion 12b in accordance with the operating state of the engine. That is, when the center C of the disk 9 is at the position shown in FIG. 11 , the rotation centers of the camshaft 1 and the disk 9 coincide with each other.
The cam 2 rotates synchronously with the camshaft 1 through the pin 10 and the U-shaped groove 6 while rotating synchronously with the camshaft 1 through the U-shaped groove 8.

A rocker shaft 1 that supports a rocker arm 15 by a driving mechanism in accordance with a change in the engine operating state.
When the knob 4 is rotated, the control ring 12 swings around the protrusion 12a, whereby the center C of the disk 9 is eccentric with respect to the center of the camshaft 1 in the rotation direction. For this reason, the pins 10 and 11 move along the U-shaped grooves 6 and 8, respectively, and the flange portions 5 and 7
Is turned around. Therefore, every time the camshaft 1 rotates, the rotation phase of the disk 9 changes with respect to the camshaft 1, and at the same time, the rotation phase of the cam 2 also changes with respect to the disk 9. Therefore, the cam 2 rotates with respect to the camshaft 1 with a phase difference of twice the phase difference of the disc 9 with respect to the camshaft 1. As a result, the valve timing can be made variable according to the phase difference of the cam 2.

[0006]

However, in the above-described conventional apparatus, the valve operating mechanism swings one rocker arm 15 by one cam 2 to open a single intake valve 16. Since it is a rocker arm type, one disk 9 or the like is required for one cam 2. For this reason, when the present invention is applied to a multi-valve type in which, for example, two intake valves and exhaust valves are provided for each cylinder, the disks 9 and the like must be arranged between the intake and exhaust valves, so that the disks 9 and the like are arranged. Therefore, a large space must be provided between each intake valve and each exhaust valve. As a result, the span between adjacent intake valves and exhaust valves must be increased,
It cannot be applied to multiple valve type.

In addition, the camshaft 1 is connected to each cam 2
Therefore, in the multi-valve system, the camshaft 1 must be divided into a large number according to the number of intake and exhaust valves, the number of cam bearings provided on the cylinder head increases, and the installation space must be increased. . Therefore, the size and weight of the entire engine must be increased, and as a result, it cannot be applied to a multi-valve system.

Each of the pins 10 and 11 has a U-shaped groove 6, 8
When the disk 9 is eccentrically oscillated, the outer edges slide on the opposing inner surfaces 6a, 6b, 8a, 8b of the U-shaped grooves 6, 8. Therefore, each of the pins 10, 1
A large sliding frictional resistance is generated between 1 and the inner surfaces 6a, 6b, 8a, 8b of the U-shaped grooves 6, 8 so that they are easily worn, and a large gap is generated between the two 6, 8, 10 and 11. There is a fear. As a result, there is a problem that a tapping sound is generated due to the positive and negative rotation torque fluctuations of the camshaft 1 and a deviation in valve timing is generated, thereby lowering control accuracy. Further, since the outer peripheral surface of the disk 9 repeatedly slides on the inner peripheral surface of the control ring 12 during the eccentric swing,
A large sliding frictional resistance is generated between them, which may not only hinder smooth sliding but also cause wear.

[0009]

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned conventional problems, and the invention of claim 1 has a drive shaft that rotates in synchronization with the rotation of an engine, and a drive shaft that rotates the drive shaft. A camshaft having a shaft which is rotatably inserted through an insertion hole formed in the inner axial direction, and which has a cam for directly driving an intake / exhaust valve on the outer periphery, and a camshaft opposed to a flange portion provided at an end of the camshaft. A flange connected to and fixed to the drive shaft, a control ring disposed between the two flanges and capable of eccentrically swinging in the radial direction with respect to the axis of the drive shaft;
An annular disk which is rotatably held inside the perimeter of, so as to project in opposite directions on both sides of the annular disc, one to each engaged into said flanges each engaging a groove formed in the portion
An intake / exhaust valve drive control device comprising a pair of pins and a drive mechanism for swinging the annular disk in accordance with an engine operation state, wherein an oil supply passage is formed in an axial direction inside the drive shaft.
And one end is open to the oil supply passage and the other end is
A pair of first and second injection holes directed in the direction of each pin are driven by a drive shaft.
Along the radial direction at approximately 180 ° in the circumferential direction on the peripheral wall of
And one end is open to the oil supply passage, and the other end is the ring.
The third injection hole directed in the inner circumferential direction of the disk
Along the direction and inside the annular disc
Then, the lubricating oil injected from the second injection hole is
Oil passage hole leading between the outer peripheral surface of the control ring and the inner peripheral surface of the control ring
Are formed to penetrate along the diameter direction .

[0010]

According to the present invention, not a rocker arm type but a direct-acting type in which the intake and exhaust valves are directly driven by cams provided integrally on the outer periphery of the camshaft, at least two cams are provided on one camshaft. The two or more cams can be controlled in angular velocity by one annular disk.

Further, according to the present invention , the lubricating oil flowing into the oil supply passage is simultaneously injected from the first and second injection holes between the pins and the respective engagement grooves, and the respective pins and the respective engagement grooves are formed. Forced between
, The lubrication between them can be efficiently performed. Thus, the outer peripheral surface of each of the pin and engagement grooves of
The sliding frictional resistance between the opposing inner peripheral surface is greatly reduced.

Furthermore, the lubricating oil in the oil supply passage
Is injected from the third injection hole to the inner peripheral side of the annular disk,
From here, it is further led to the oil passage hole in the annular disc
Supply between the outer peripheral surface of the annular disk and the inner peripheral surface of the control ring
Therefore, it is possible to efficiently lubricate the inner and outer peripheral surfaces.
Wear. In particular, oil passage holes are formed in the diameter direction of the annular disc
Lubricating oil
Forcibly and in large quantities can supply lubrication performance
Can be further improved.

[0013]

1 to 6 show an embodiment according to the first aspect of the present invention, which is applied to a four-cylinder engine having two intake valves per cylinder. 1 is a drive shaft to which a rotational force is transmitted from a crankshaft of an unillustrated engine via a timing sprocket 71 , and 22 is disposed around the drive shaft 21 with a certain clearance. Is a camshaft provided on the same axis as the center X of the camshaft.

The drive shaft 21 extends in the front-rear direction of the engine. The drive shaft 21 is formed in a hollow shape in order to reduce the weight and the like, and has an oil communicating with a main oil gallery (not shown) inside the hollow shape. A supply passage 60 is formed. This oil
The supply passage 60 has a cylinder head at one end as shown in FIG.
Of the drive shaft 21 which is supported through a bearing 68 at the upper end of the drive shaft.
No. 1 journal 69 and oil passage 7 bored in bearing 68
It communicates with the main oil gallery (not shown) through 0
You.

Each of the camshafts 22 is formed separately from a direction perpendicular to the axis for each cylinder, and the drive shaft
1 is formed, and a pair of cam bearings 61,
62 rotatably supported. As shown in FIG. 2, each camshaft 22 is provided with a pair of cams 26, 26 integrally on the outer peripheral surface thereof.
Reference numeral 6 designates opening operation of two intake valves 23, 23 per cylinder via direct-acting valve lifters 25, 25 against the spring force of valve springs 24, 24. Further, each camshaft 22 is provided with a flange portion 27 at one divided end, and a bearing 63 for bearing the drive shaft 21 on the inner peripheral surface of the insertion hole 22a at the other divided end. Is provided. A sleeve 28 and an annular disc 29 are provided between the flange 27 and the other end of the adjacent camshaft 22.

The bearing 63 has an annular shape and is provided integrally with the inner peripheral surface of the insertion hole 22a. The inner peripheral surface 63a is in sliding contact with the outer peripheral surface of the drive shaft 21 .

As shown in FIG. 4, the flange portion 27 has an elongated rectangular engaging groove 3 extending radially from the hollow portion.
0 is formed, and a protruding surface 27a is provided integrally with one side surface of the annular disk 29 in the circumferential direction of the outer peripheral surface thereof.

The sleeve 28 has a small-diameter end rotatably inserted into the other divided end of the camshaft 22 and is driven through a connecting shaft 31 which is diametrically penetrated at a substantially central position. It is connected and fixed to the shaft 21. The other end of the sleeve 28 has the annular disc 29
A flange portion 32 facing the flange portion 27 is provided integrally. As shown in FIG. 5, the flange portion 32 has an elongated rectangular engaging groove 33 extending in the radial direction on the opposite side to the locking groove 30 and has an outer peripheral surface other than the annular disk 29. Projection surface 28 that slides on the side surface
a is provided integrally.

The annular disk 29 has a substantially donut shape, an inner diameter substantially equal to the inner diameter of the camshaft 22, and an annular gap S between the outer peripheral surface of the drive shaft 21. In addition, the small-width outer peripheral portion 29 a is rotatably supported on the inner peripheral surface of the control ring 35 via the roller bearing 34. Each of the holding grooves 29b and 29c formed in the axial direction at the opposing position on the diameter line has a respective engaging groove 3.
A pair of pins 36 and 37 that engage with the pins 0 and 33 are provided. The pins 36 and 37 project in opposite directions in the camshaft axial direction, and the bases of the pins 36 and 37 have the holding holes 29 b and 2.
9c, and is rotatably supported in the engaging grooves 30, 33 as shown in FIGS.
Are formed to have two flat width portions 36a, 36b, 37a, 37b that are in contact with the opposed inner surfaces 30a, 30b, 33a, 33b.

The control ring 35 has a substantially annular shape as shown in FIGS. 1 to 3, and has a boss 35a at one end of the outer periphery.
And a pivot pin 38 that penetrates the boss 35a is provided as a fulcrum so as to be swingable up and down.
A lever portion 35b is provided on the outer peripheral surface on the opposite side to the portion a. The control ring 35 is configured to swing by a drive mechanism 39 via a lever 35b.

As shown in FIGS. 2 and 6, the drive mechanism 39 includes first and second cylinders 40 and 41 formed opposite to predetermined portions of the cylinder head.
A hydraulic piston 42 and a retainer 43 which are provided so as to be able to protrude and retract from the inside of the cylinder 41 and hold the arc-shaped tip of the lever portion 35a from above and below at each end edge, and supply and discharge hydraulic pressure to a pressure receiving chamber 40a in the first cylinder 40. And a hydraulic circuit 44 for moving the hydraulic piston 42 forward and backward.

The retainer 43 provided in the second cylinder 41 has a substantially cylindrical shape with a bottom.
1 is urged in the advance direction (toward the lever portion) by the spring force of a coil spring 45 elastically mounted in the inside.

The hydraulic circuit 44 includes an oil passage 47 having one end in the oil pan 46 and the other end communicating with the pressure receiving chamber 40a, and an oil pump 48 provided on the oil pan 46 side of the oil passage 47. And a three-port two-position electromagnetic switching valve 49 provided downstream of the oil pump 48. The electromagnetic switching valve 49 switches the flow path in response to an ON-OFF signal from a controller 50 that detects the current engine operating state based on signals such as the engine speed and the amount of intake air. While communicating the whole, the oil passage 4
7 and the drain passage 51 are communicated with each other.

The annular disk 29 of the drive shaft 21
One end of the peripheral wall is open to the oil supply passage 60,
Are the plane portions 36a, 36b, 37 of the pins 36, 37, respectively.
a, 37b, and opposing inner surfaces 30a,
30b, 33a, 33b, the first and second jets directed
Holes 65 and 66 are radially located at 180 ° in the circumferential direction.
Has been drilled. Also, a substantially intermediate position between the two injection holes 65 and 66.
The oil supply passage 60 is directly connected to the inside of the annular disc 29.
Third injection hole 6 directed to oil passage hole 71 formed in the radial direction
7 are formed through the diametrical direction.

The operation of this embodiment will be described below.

First, the controller 50 sends the electromagnetic switching valve 4
When the ON signal is output to 9, the hydraulic oil pumped from the oil pump 48 to the oil passage 47 is directly supplied to the pressure receiving chamber 40a. Accordingly, as the internal pressure of the pressure receiving chamber 40a rises, the hydraulic piston 42 moves against the lever portion 35b against the spring force of the coil spring 45 as shown by the solid line in FIGS.
Of the control ring 35, that is, the annular disc 29
And the center X of the drive shaft 21 coincide with each other. In this case, there is no rotational phase between the annular disk 29 and the drive shaft 21, and the center Y of the camshaft 22 and the center Y of the annular disk 29 coincide with each other. Does not occur. Accordingly, the sleeve 28 rotates synchronously via the connecting shaft 31 with the rotation of the drive shaft 21, and the sleeve-side engaging groove 33 and the pin 37, the annular disc 29, the pin 36, and the camshaft 22 side engaging groove 30.
, The camshaft 22 also rotates synchronously.

Next, an OFF signal is output to the electromagnetic switching valve 49 in accordance with a change in the engine operation state, thereby shutting off the upstream side of the oil passage 47 and the downstream side of the oil passage 47 and the drain passage 5.
Connect 1 Therefore, the hydraulic oil in the pressure receiving chamber 40a
The oil pan 47 flows back through the oil passage 47 and the oil pan 4
6, the hydraulic piston 42 moves backward through the retainer 43 by the spring force of the valve spring 24 and the coil spring 45 as the internal pressure of the pressure receiving chamber 40a decreases. As a result, the control ring 35 is pushed up by the retainer 43 as shown by a dashed line in FIGS. 2 and 6 and swings upward with the pivot pin 38 as a fulcrum. Eccentric with center X. Accordingly, the sliding position between the engaging groove 33 and the pin 37 of the sleeve 28 and the engaging groove 30 and the pin 36 of the camshaft 22 moves with each rotation of the drive shaft 21, and the angular velocity of the annular disk 29 changes. The rotation becomes uneven angular velocity.

That is, for example, when the sliding position between the engagement groove 33 and the pin 37 approaches the center X of the drive shaft 21, the engagement groove 3
0 and the sliding position of the pin 36 are separated from the center X. In this case, the annular disk 29 has a lower angular velocity with respect to the drive shaft 21 and the angular velocity of the camshaft 22 with respect to the annular disk 29 also decreases. Therefore, the camshaft 22 is in a state of being decelerated twice with respect to the drive shaft 21.

On the other hand, the operating state of the engine further changes, and the lever 35b is pushed down by the hydraulic piston 42, contrary to the above, so that the annular disk 29 is shifted from the center coincidence position as shown by the two-dot chain line in FIGS. Further swinging downward, when the sliding position of the engaging groove 33 and the pin 37 moves away from the center X of the drive shaft 21 and the operating position of the engaging groove 30 and the pin 36 approaches the center X, The camshaft 22 is in a state where the speed is doubled with respect to the drive shaft 21.

As a result, the rotational phase difference between the camshaft 22 and the cam 26 and the drive shaft 21 changes as shown in FIG. 7B based on the change in the respective angular velocities, and the valve timing changes as shown in FIG. It changes according to the phase difference of the camshaft 22 with the lift kept constant.

That is, when the angular velocity of the camshaft 22 is relatively high, the rotational phase with respect to the drive shaft 21 advances until the two 21 and 22 become equal in speed. Phase 2
It is delayed until 1 and 22 become uniform speed. Then, as shown in FIG. 7B, an in-phase point (point P) exists midway between the maximum and minimum points of the rotational phase difference, and in the change of the rotational phase indicated by the broken line in FIG. The valve opening timing of the valve 23 is delayed, the valve closing timing after the point P is advanced, and the operating angle of the valve is reduced as shown by the broken line in FIG. 7A. On the other hand, in the change of the rotation phase indicated by the one-dot chain line in FIG. 7B, the valve opening timing is advanced before the point P, the valve closing timing after the P point is delayed, and as shown by the one-dot chain line in FIG. The corner becomes larger. The solid line in FIG. 7A indicates a case where the centers X and Y match.

In this embodiment, two cams 26, 26 arranged close to the outer periphery of each of the divided camshafts 22 are provided.
This is a so-called direct drive type in which both intake valves 23, 23 are directly driven, so that the span of both intake valves 23, 23 can be made as small as possible, and the annular disk 2
9 and the like can be arranged between the cylinders instead of between the intake valves 23 and 23 as in the related art. Therefore, the size of the entire apparatus can be reduced. In particular, since the drive shaft 21 is supported not by an external bearing but by the bearing 63 inside the camshaft 22, no space is required for installing the bearing 63, and this also promotes downsizing of the entire apparatus.

The bearing portion 63 is connected to the camshaft 22.
, The drive shaft 21 and the camshaft 22
The work of centering the shaft center with the inner peripheral surface 63 of the bearing portion 63 is simply performed.
This can be performed by adjusting the processing of a. Therefore,
Such centering work becomes extremely easy.

As described above, the pins 36, 37 have both side edges formed on the flat portions 36a, 36b, 37a, 37b, so that the opposing inner surfaces 30a,
30b, 33a, and 33b are brought into surface contact with each other. Therefore, when the rotation is transmitted from the drive shaft 21 to the camshaft 22 and when the annular disc 29 is eccentric,
a, 36b, 37a, 37b and opposing inner surfaces 30a, 30
When sliding with b, 33a, 33b, generation of concentrated load between them is prevented, and the surface pressure is reduced. As a result, the engagement groove 3
0, 33 and the pins 36, 37 are prevented from being worn over time, and the sound of the flanges 27, 32 and the pins 36, 37 caused by the fluctuation of the rotation torque of the camshaft 22 is generated, and the valve is mounted. It is possible to prevent the control accuracy from being lowered due to the timing deviation.

Further, each pin 36 and 37, because it is rotatably supported holding hole 29b of the annular disc 29, the 29c, each pin 36 even when the rocking of the disk 29,
37 is rotated appropriately, and the plane portions 36a, 36b, 37a, 3
7b and the opposing inner surfaces 30a, 30b, 3 of the engagement grooves 30, 33.
3a and 33b are always in surface contact. Therefore,
The occurrence of wear between the two 30, 36, 33, 37 is more reliably prevented.

[0036] Moreover, according to this embodiment, a portion from the oil pump, not shown, at the time of engine driving the lubricating oil pumped into the main oil gallery is introduced from the oil passage 70 to the oil supply passage 60, and each nozzle hole Each pin 36,3 from 65-67
It is supplied between the 7 and the locking groove 30 and 33, annular disc 29 from the oil passage hole 72 and the roller bearing 34
Is actively supplied into the gap. Accordingly, the lubricating properties of each sliding portion are improved, smooth sliding and eccentric swing operation are always obtained, and the occurrence of wear can be more reliably prevented. In particular, oil
A passage hole 72 is formed in the diameter direction of the annular disc 29,
In addition, since the rotational centrifugal force of the annular disk 29 acts, lubricating oil
Between the annular disc 29 and the roller bearing 34
The lubrication performance can be
It can be further improved.

Further , since the oil supply passage 60 is formed inside the drive shaft 21, the manufacturing operation is easier and the cost can be reduced as compared with the case where the oil supply passage 60 is formed separately. Also,
Even when the engine speed is low and the discharge amount of the oil pump is small, the lubricating action can be performed by the rotational centrifugal force of the drive shaft 21.

9 and 10 show another example of the second embodiment.
An oil supply pipe 72 having an oil supply passage 60 therein is provided in parallel above the camshaft 22, and a pair of jets directed to the upper portions of the pins 36 and 37 on the peripheral wall of the oil supply pipe 73. Holes 65 and 66 are formed in the radial direction. One end of the oil supply passage 60 communicates with a main oil gallery (not shown).

Therefore, in this embodiment, each injection hole 65,
Together between the pins 36, 37 and Kakukakaritomemizo 30 and 33 are positively lubricated by sprayed lubricating oil from 66, annular disc 29 and the roller bearing 34 and controlled by the return vanes of the injected lubricant The space between the ring 35 is also lubricated.

[0040]

[Effect of the invention] As is clear from the above description, the present invention
According to this, the lubricating oil in the oil supply passage is
Because it is always positively supplied between the pin and each engagement groove,
The lubrication performance between each pin and each engagement groove is improved,
The occurrence of wear is suppressed, and the occurrence of a gap is prevented. This
As a result, tapping noise and valve tie
A decrease in control accuracy due to misalignment of the head is prevented.

The lubricating oil injected from the oil supply passage through the third injection hole is positively supplied between the outer peripheral surface of the annular disk and the inner peripheral surface of the control ring through the oil passage hole. For,
The smooth rotation and eccentric operation of the annular disk can be obtained at all times, and the occurrence of wear between the inner and outer peripheral surfaces is prevented. In particular, oil passage holes are formed in the diameter direction of the annular disc
Lubrication due to the rotating centrifugal force of the annular disk
Forcibly and in large quantities of oil between the annular disc and the control ring
Lubrication performance can be further improved because it can be supplied
be able to.

[Brief description of the drawings]

FIG. 1 is a partially cutaway view showing a main part of an embodiment according to the invention of claim 1;

FIG. 2 is a view taken in the direction of arrow A in FIG. 1;

FIG. 3 is a plan view showing a main part of the embodiment.

FIG. 4 is a sectional view taken along line BB of FIG. 3;

FIG. 5 is a sectional view taken along line CC of FIG. 3;

FIG. 6 is a schematic diagram showing a driving unit of the embodiment.

FIG. 7 is a characteristic diagram of a rotational phase difference between a drive shaft and a camshaft and a valve lift amount according to the present embodiment.

[8] a partially cutaway view showing an essential part of this embodiment.

FIG. 9 FIG. 4 is a partially cutaway view showing a main part of another example according to the present invention.

FIG. 10 FIG. 10 is a sectional view taken along line DD of FIG. 9.

FIG. 11 Sectional drawing of the conventional intake-and-exhaust-valve drive control apparatus.

FIG. FIG. 12 is a sectional view taken along line EE of FIG. 11.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 21 ... Drive shaft 22 ... Cam shaft 22a ... Insertion hole 27 ... Flange part 29 ... Annular disk 32 ... Flange part 30, 33 ... Engagement groove 35 ... Control ring 36, 37 ... Pin 39 ... Driving mechanism 60 ... Oil supply passage 63 ... bearing parts 65, 66, 67 ... injection holes 72 ... oil passage holes

──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F01L 13/00 301 F01L 1/04 F01M 1/06 F01M 1/08

Claims (1)

(57) [Scope of request for utility model registration] 1. A drive shaft that rotates in synchronization with the rotation of an engine, a drive shaft that is rotatably inserted through an insertion hole formed in an internal axial direction, and directly drives an intake / exhaust valve on an outer periphery. A cam shaft having a cam, a flange portion opposed to a flange portion at an end portion of the cam shaft, and a flange portion connected and fixed to the drive shaft, and disposed between the two flange portions; Can be eccentrically oscillated in the radial direction with respect to the axis
A control ring, an annular disk rotatably held on the inner periphery of the control ring, and protruding in opposite directions on both sides of the annular disk, in respective engagement grooves formed in the two flange portions. a pair of pins respectively engaged into the a intake and exhaust valves drive control apparatus and a drive mechanism for swinging in accordance with circular disks to engine operating conditions, the oil supply passage to the interior axis of the drive shaft When formed
Each end is open to the oil supply passage and the other end is connected to each of the pins.
A pair of first and second injection holes directed in the direction of
Formed along the radial direction at approximately 180 ° in the circumferential direction
And one end is open to the oil supply passage, and the other end is the annular
The third injection hole oriented in the inner circumferential direction of the disk
And along the inside of the annular disc,
The lubricating oil injected from the second injection hole is
The oil passage hole leading between the outer peripheral surface and the inner peripheral surface of the control ring is straightened.
An internal combustion engine characterized by being formed so as to penetrate in the radial direction.
Intake and exhaust valve drive control device.