JPH0734825A - Intake/exhaust valve drive control device of internal combustion engine - Google Patents

Abstract

PURPOSE:To increase the control range of the valve timing by efficiently transferring the movement of a moving means to a disk housing, secure the required output according to the operational condition of the engine, and improve the fuel consumption. CONSTITUTION:The changes in the angular velocity of a disk housing 34 which is interposed between a driving shaft 21 and a cam shaft 22, and swayed by the rotation of an eccentric cam 41 and the cam shaft 22 where the center (Y) is made eccentric from the axial center (X) of the driving shaft 21 accompanied by the swaying of the disk housing 34 are obtained. The rotational direction of the eccentric cam 41 is set to be approximately parallel to the moving direction (the arrow direction) of the disk housing 34.

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 devices of this type have been provided, and one of them is described, for example, in Japanese Patent Application No. 4-157909 filed by the present applicant.

The outline will be described with reference to FIG. 10. A drive shaft 1 is rotatably driven from a crankshaft of an engine through a sprocket, and is provided on the outer periphery of the drive shaft 1 so as to be rotatable relative to each other and divided into cylinders. Formed camshafts 2
And a plurality of annular disc housings 3 arranged between the camshafts 2 and swingable in a substantially radial direction with respect to the axis X of the drive shaft 1, and the disc housings 3
Is rotatably supported in the inner peripheral support hole 4 of the drive shaft 1, and while the drive shaft 1 and the cam shaft 2 are connected via a pair of pins 10 and 11, the center Y of the drive shaft 1 is the center of the drive shaft 1 as the disc housing 3 swings. It has an axis X and an eccentric disk 5.

The camshaft 2 is integrally provided with a pair of cams 2a for opening and operating two intake valves per cylinder on the outer circumference against the spring force of a valve spring.

The disk housing 3 is swingably supported in the direction of the arrow in the figure by a support shaft 7 engaged in a U-shaped groove 6 formed at one end of the boss portion 3a at the upper end.
The eccentric cam 9 held in a cam hole 8 formed at the other end of the boss portion 3a swings by rotation. A control shaft 12 to which a rotational force is applied from a hydraulic actuator (not shown) is connected and fixed to the eccentric cam 9.

Then, when the control shaft 12 is rotated by a predetermined angle by the hydraulic actuator in accordance with a change in engine operating state, the eccentric cam 9 rotates in one direction within a predetermined angle range θ. Therefore, the disc housing 3
Of the U-shaped groove 6 swings in the direction of the arrow in the drawing with the inner peripheral surface of the U-shaped groove 6 slidingly contacting the outer peripheral surface of the support shaft 7 with the support shaft 7 as the fulcrum. Along with this, the disk 5 also swings, and the center Y thereof is eccentric from the axis X of the drive shaft 1 as shown in the figure.

Therefore, the rotation phase of the disk 5 changes with respect to the drive shaft 1 at each rotation of the drive shaft 1, and at the same time, the rotation phase of the cam 2a of the camshaft 2 also changes with respect to the disk 5. Therefore, the cam 2a rotates with a phase difference twice the phase difference with respect to the drive shaft 1 of the disk 5 with respect to the drive shaft, and the angular velocity changes. As a result, the valve timing can be made variable according to the change in the angular velocity of the cam 2a.

[0008]

However, in the device according to the prior application, the rotation direction of the eccentric cam 8 is perpendicular to the swing direction of the disc housing 3. That is, the disk housing 3 swings in the direction of the arrow in the figure as described above, that is, it swings on a line substantially parallel to the connection Z1 connecting the axis Q1 of the support shaft 7 and the axis Q2 of the control shaft 12. However, the eccentric cam 8 is adapted to rotate in a direction orthogonal to the connection Z1.

Therefore, the eccentric movement amount ε1 of the center O due to the rotation of the eccentric cam 8 is not efficiently transmitted to the disk housing 3, and the disk housing 3 swings with respect to the axis X of the drive shaft 1 of the center Y. The movement amount (eccentricity amount) ε2 becomes sufficiently smaller than the eccentric movement amount ε1 of the eccentric cam 8. As a result, the change in the angular velocity between the drive shaft 1 and the camshaft 2 cannot be increased, and the change in the operating angle of the valve also becomes small. Therefore, the valve timing control width also becomes small, and there is a possibility that the required output or the reduction in fuel consumption depending on the engine operating state cannot be obtained.

[0010]

SUMMARY OF THE INVENTION The present invention has been devised in view of the actual situation of the device according to the above-mentioned prior application, and is relatively rotatable coaxially with the drive shaft that is rotationally driven by the engine. And a cam shaft having a cam for opening and closing the intake and exhaust valves on the outer circumference, and a drive shaft disposed between the drive shaft and the cam shaft and having a support shaft engaged at one end as a fulcrum. A disk housing movably provided in the radial direction, a moving means for moving the disk housing via a drive mechanism according to an engine operating state, and a rotatably supported inside a support hole of the disk housing, The drive shaft and the cam shaft are connected to each other, and a disc is provided, the center of which is eccentric with the axial center of the drive shaft as the disc housing swings, and the change in the angular velocity of the cam shaft is caused by the eccentric movement of the disc. In the intake and exhaust valves drive control device for variably controlling the operating angle of the intake and exhaust valves Te, the actuation direction of the moving means, is characterized in that set substantially parallel to the moving direction of the disc housing.

[0011]

According to the present invention having the above-described structure, the operating direction of the shaft center of the eccentric cam or the like, which is the moving means, is not a direction orthogonal to the moving direction of the disk housing but a direction substantially along a parallel line. The axial center movement amount of the eccentric cam becomes the movement amount of the disc housing as it is, and efficient swing transmission can be obtained.

[0012]

1 to 7 show an embodiment in which the intake / exhaust valve drive control device according to the invention of claims 1 and 2 is applied to a multi-cylinder engine, and 21 in FIG. 3 is a crankshaft of the engine not shown. Drive shaft which is rotationally driven from the drive shaft through a sprocket, and 22 is the drive shaft 2
1 is arranged with a constant gap on the outer periphery of 1 and the drive shaft 2
1. The cam shaft is provided coaxially with the center X of the drive shaft 1. The drive shaft 21 extends in the longitudinal direction of the engine, and is formed into an internal hollow shape in order to reduce the weight.

The cam shaft 22 is formed in a hollow shape, is rotatably supported by a cam bearing (described later) provided at the upper end of the cylinder head 43, and as shown in FIG. A plurality of cams 26 that open the valve via the valve lifter 25 against the spring force of the valve spring 24 are integrally provided. Further, the camshaft 22 is divided and formed for each cylinder from a direction perpendicular to the axis at a predetermined position in the longitudinal direction, and a flange portion 27 is provided at a divided end portion on one side.

A sleeve 28 and an annular disk 29 are arranged between the divided ends. The flange portion 2
As shown in FIG. 5, the elongated groove 7 has an elongated rectangular engaging groove 30 extending in the radial direction from the hollow portion, and slidably contacts one side surface of the annular disk 29 in the circumferential direction of the outer peripheral surface thereof. The protruding surface 27a is integrally provided.

The sleeve 28 has a small diameter one end portion 28b.
Is rotatably inserted into the other end of the camshaft 22 on the other side, and is fixedly connected to the drive shaft 21 via a connecting shaft 31 penetrating diametrically at a substantially central position. Further, as shown in FIG. 6, the flange portion 32 provided at the other end of the sleeve 28 has an elongated rectangular engaging groove 33 formed in the radial direction on the side opposite to the engaging groove 30. At the same time, the outer peripheral surface is integrally provided with a protruding surface 28a that is in sliding contact with the other side surface of the annular disk 29.

The annular disc 29 has a substantially toroidal plate shape, an inner diameter of which is substantially the same as the inner diameter of the cam shaft 22, and an annular gap S is formed between the annular disc 29 and the outer peripheral surface of the drive shaft 21. In addition, the outer peripheral portion 29a having a small width is rotatably supported by the inner peripheral surface 34a of the annular disc housing 34. In addition, a pair of pins 36 and 37 that engage with the engagement grooves 30 and 33 are provided in the pin holes 29b and 29c that are formed at the opposite positions on the diameter line. The pins 36 and 37 project in opposite directions to each other in the axial direction of the camshaft, the base portions are rotatably supported in the pin holes 29b and 29c, and the pins 36 and 37 are provided on both side edges of the tip portion as shown in FIGS. As shown in FIG.
Flat portions 36a, 36b, 37a, 37b having a width across flats are formed so as to come into contact with 0a, 30b, 33a, 33b.

As shown in FIGS. 1 and 2, the disk housing 34 has a substantially annular shape, and a boss portion 35 provided at the upper end of the outer periphery has a substantially U-shaped support groove 38 formed at the outer edge of one end portion. And the cam hole 3 is provided at the other end of the boss portion 35.
9 is formed through. Then, one end of the disk housing 34 is rotatably and slidably supported by the support shaft 40 inserted into the support groove 38, and the eccentric cam 41 inserted into the cam hole 39 is rotated. The disc housing 34 swings in the direction of the arrow. That is, this disc housing 34
Is such that the center Y moves on a line Z2 that is substantially parallel to a straight line Z1 that connects the axis Q1 of the support shaft 40 and the axis Q2 of the control shaft 42 of the drive mechanism 52, which will be described later, connected to the eccentric cam 41. Has become.

As shown in FIGS. 1 and 4, the support shaft 40 is extended along the longitudinal direction of the engine, and a predetermined portion of the support shaft 40 is provided in the frame body 4.
5 is rotatably supported in a shaft hole 45c formed in the lateral beam portion 45b of the horizontal beam portion 45b, and has flat contact surfaces 40a, 4a formed at both end edges of a portion corresponding to the disk housing 34.
0b is in contact with the facing surfaces 38a and 38b of the support groove 38 in a surface contact state.

The eccentric cam 41 has a ring shape, the outer diameter is set to be slightly smaller than the inner diameter of the cam hole 39, and the wall thickness in the circumferential direction is gradually increased from the thin portion 41a to the thick portion 41.
b, and the through hole 4 is formed through the axial direction.
It is connected and fixed to the hollow control shaft 42 via 1c. The eccentric cam 41 has a rotation angle θ set to about 110 ° as shown in FIG. 2, and its rotation direction is an arc locus substantially along a straight line Z1 connecting the two axial centers Q1 and Q2. Is set in the direction of drawing, and the arcuate locus is substantially symmetric with respect to a line Z3 orthogonal to the straight line Z1.

As shown in FIG. 7, the drive mechanism 51 includes the control shaft 42, a hydraulic actuator 52 provided at one end of the control shaft 42, and a hydraulic circuit 53 for supplying and discharging hydraulic pressure to and from the hydraulic actuator 52. Is equipped with.

As shown in FIGS. 3 and 4, the control shaft 42 extends along the longitudinal direction of the engine, and has a frame 45 fixed to the upper end of the cylinder head 43 with bolts 44. Bearing groove 46 and bearing cap 47
Is bearing between and. The bearing cap 47
Are fixed on the frame body 45 by bolts 48.
As shown in FIGS. 1, 3, and 4, the frame body 45 is disposed inside the rocker cover 49 and is provided with support portions 45a, 45a on both sides extending along the longitudinal direction of the engine and the support portion 4
5a, 45a are connected at right angles to each other, and the upper surface is formed with the bearing groove 46 and the lower surface is formed with the cam bearing groove 50 of the camshaft 22, that is, a plurality of horizontal beam portions 45b which also serve as cam bearing brackets. ing.

In the hydraulic actuator 52, the first oil chambers 56, 56 and the second oil chambers 57, 57 in which the two-blade rotary vanes 55 are located on the diagonal line in the cylindrical housing 54.
The rotary vane 55 is connected to the control shaft 42 while being rotatably provided.

The hydraulic circuit 53 includes the first and second oil chambers 5.
A pair of first and second oil passages 58 for supplying and discharging hydraulic pressure to and from
a, 58b, a 4-port 2-position electromagnetic switching valve 59 provided at the ends of the oil passages 58a, 58b, and an oil pump 6 provided at the upstream end of the oil main gallery 60.
1, a drain passage 63 that appropriately communicates with the oil passages 58a and 58b to return the working oil into the oil pan 62, and a relief valve 64 that controls the pump discharge pressure to a constant pressure.

Further, the electromagnetic switching valve 59 is switched by an ON-OFF signal from the controller 65 which detects the current engine operating state based on signals such as the engine speed and the intake air amount, and the OFF signal causes the oil to change. The pump 61 and the first oil passage 58a are communicated with each other, the second oil passage 58b and the drain passage 63 are communicated with each other, and an ON signal is communicated in the opposite direction.

The operation of this embodiment will be described below.
First, when the engine speed is low and the load is low, an ON signal is output from the controller 65 to the electromagnetic switching valve 59, and the oil pump 61
The hydraulic oil discharged from the first oil chambers 56, 56 flows into the first oil chambers 56, 56, while the hydraulic oil in the second oil chambers 57, 57 is discharged from the drain passage 63.
Is discharged into the oil pan 62. For this reason, the rotary vane 55 rotates counterclockwise in the drawing to rotate the control shaft 42.
Is rotated counterclockwise in FIG. Therefore, as shown in FIG. 2, the eccentric cam 41 rotates counterclockwise from the position of the broken line to the maximum angle position of θ, and the maximum thick portion 41b moves to the upper side. That is, the maximum thick portion 41
b is eccentrically rotated by a predetermined amount ε1 substantially along the connection Z1. Accordingly, the disk housing 34 swings while sliding along the arrow direction with the support shaft 40 as a fulcrum through the support groove 38. Therefore, the annular disc 29 also swings in the same direction, and its center Y is eccentric with the center X of the drive shaft 21 (cam shaft 22). In other words, when the cam hole 39 side of the boss portion 35 is pulled up in the upper left direction as the eccentric cam 41 rotates, the facing surfaces 38a and 38b of the support groove 38 slide on the contact surfaces 40a and 40b of the support shaft 40. The whole swings in the counterclockwise direction and is eccentric by an eccentric rotation amount ε1 of the eccentric cam 41 and a movement amount ε3 which is substantially equal to the moving amount ε3. Therefore, the engagement groove 33 on the sleeve 28 side, the pin 37, and the camshaft 2
The sliding position between the locking groove 30 and the pin 36 on the first side is the drive shaft 21.
, And the angular velocity of the annular disk 29 changes, resulting in unequal angular velocity rotation.

That is, when the sliding position of the locking groove 30 and the pin 36 approaches the center X of the drive shaft 21, the sliding position of the locking groove 33 and the pin 37 moves away from the center X. In this case, the annular disc 29 has a large angular velocity with respect to the drive shaft 21, and the angular velocity of the camshaft 22 also becomes large with respect to the annular disc 29. Therefore, the camshaft 22 is partially doubled in speed with respect to the drive shaft 21.

On the other hand, when the engine shifts to the high speed and high load range, an OFF signal is output from the controller 65 to the electromagnetic switching valve 59, and the working oil in the first oil chambers 56, 56 is discharged from the drain passage 63. At the same time, the oil pressure is sent from the oil pump 61 into the second oil chambers 57, 57, and the rotating vanes 5
5 reversely rotates in the clockwise direction. Therefore, the eccentric cam 4
1 rotates clockwise and returns to the original position shown in FIG. 1, whereby the disc housing 34 also swings to the original position, and the center Y of the annular disc 29 coincides with the center X of the drive shaft 21. . Therefore, in this case the annular disc 2
No rotational phase is generated between the drive shaft 21 and the drive shaft 21, and since the center of the camshaft 22 and the center Y of the annular disk 29 are aligned with each other, the rotational phase difference between the two 22 and 29 does not occur. Therefore, as the drive shaft 21 rotates, the sleeve 28 rotates synchronously via the connecting shaft 31, and the locking groove 33 on the sleeve side, the pin 37, the annular disk 29, and the pin 3 are rotated.
6. The camshaft 22 also rotates synchronously via the locking groove 30 on the camshaft 22 side.

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. 8A, and the valve timing changes as shown in FIG. The valve lift changes according to the phase difference of the cam shaft 22 with the valve 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 speeds 21 and 22 become uniform, and eventually when the angular velocity of the camshaft 22 relatively decreases. Phase is both 2
Delay until 1 and 22 become constant speed. Then, as shown in FIG. 8A, the same phase point (point P) exists in the middle of the maximum and minimum points of the rotational phase difference, and in the change of the rotational phase shown by the broken line in the figure, the intake valve before point P is changed. The valve opening timing of 23 is delayed, the valve closing timing after point P is advanced, and the operating angle of the valve is reduced as shown by the broken line in FIG. 8B. Therefore, as described above, in the engine low speed and low load region, the valve timing of the intake valve 23 becomes small as shown by the broken line in FIG. 8B, the opening timing is slightly delayed, and the closing timing is advanced. As a result, the valve overlap of the intake and exhaust valves is reduced, the residual gas in the combustion chamber is reduced, and stable combustion improves fuel efficiency. Further, the early closing timing improves the intake charging efficiency and can increase the low speed torque.

On the other hand, in the high-speed and high-load range, the operating angle becomes large as shown by the solid line in FIG. 8B, the same timing is advanced and the closing timing is delayed, so the intake charging efficiency utilizing the intake inertial force is improved. However, high output can be achieved.

As described above, in this embodiment, the valve timing can be variably controlled with high accuracy in accordance with the change in engine operation, and in particular, the disc housing 34 is swung by using the eccentric cam 41. As a result, it is possible to reliably prevent the occurrence of hammering noise, abrasion, etc. due to the alternating load of the disk housing 34 due to the fluctuation of the rotational torque of the camshaft 22.

Moreover, as described above, since the eccentric cam 41 is rotated along the connection line Z1 which is substantially parallel to the moving direction of the disc housing 34, the eccentric rotation amount ε1 of the eccentric cam 41 is efficiently applied to the disc housing 34. Good transmission is possible, and the disc housing 34 also obtains a movement amount ε3 that is substantially equal to the eccentric rotation amount ε1. As a result, the rotational phase difference between the drive shaft 21 and the cam shaft 22 can be increased as much as possible, and the operating angle change amount of the intake valve 23 is also increased. Therefore, the valve timing control width can be expanded.

FIG. 9 shows an embodiment according to the inventions of claims 1 and 3, wherein the disk housing 34 is raindrop-shaped, and has a substantially annular housing main body 34b and the housing main body 3
4b is provided with an extending portion 34c which is provided on the outer circumference of the upper end portion in the radial direction, and the housing main body 34a rotatably supports the disk 29 in a support hole 34a provided at the center. On the other hand, the extending portion 34c is engaged with a support shaft 40 that swings and supports the disc housing 34 in the left direction (arrow direction) in the drawing in a substantially U-shaped support groove 38 that is cut out at the tip. , Between the support groove 38 and the support hole 34a, that is, the axis Q2 of the support groove 38 and the center of the support hole 34a (the disk 2
An eccentric cam 41 is rotatably held in a cam hole 39 formed on a connection line connecting the centers Y of 9).

In the eccentric cam 41, the thick portion 41b is located on the upper side, and the control shaft 42 which is rotated by the hydraulic actuator is fixed to the through hole 41c provided at the eccentric position on the lower side as in the above embodiment. Has been done. In addition, the eccentric cam 41 has an axial center Q of the control shaft 42.
The rotation is about 90 ° in an angle range of about 90 °, and the rotation direction is set substantially parallel to the swinging direction of the disc housing 34. That is, a straight line Z1 parallel to the swinging direction Z2 of the disk housing 34
The arc locus has a substantially left-right symmetrical shape about a line Z3 orthogonal to the straight line Z1.

Therefore, when the control shaft 42 is rotated clockwise by the hydraulic actuator when the engine load is low, the eccentric cam 41 also rotates in the same direction as indicated by the broken line,
The axis Q1 is eccentrically moved by a predetermined amount ε1. For this reason,
The disc housing 34 swings counterclockwise around the support shaft 40, but the center Y of the disc housing 34
Since the distance from the shaft center Q2 of the support shaft 40 is larger than that of the eccentric cam 41, its swing amount ε4 is larger than the eccentric rotation amount ε1 of the eccentric cam 41.

Therefore, in this embodiment, not only the same effects as the above-described embodiments can be obtained, but the swing amount ε4 of the disc housing 34 becomes larger than the eccentric rotation amount ε1 of the eccentric cam 41. The amount of change in the operating angle of the intake valve is increased, and the control range of valve timing can be further increased.

The present invention is not limited to the configuration of the above embodiment, and a link can be used as the moving means of the disc housing 34 instead of the eccentric cam 41. That is, one end of the link is rotatably connected to one end of the disk housing 34, and the other end is connected to the control shaft 42. With the rotation of the link, the disk housing 34 uses the support shaft 40 as a fulcrum. It is also possible to make it rock. At this time, it goes without saying that the rotation direction of the link is set substantially parallel to the swing direction of the disk housing 34.

Further, the rotation angle of the eccentric cam 41 is set to the connection Z1.
Can be set to 180 ° as a reference, and by doing so, the swing amount of the disc housing 34 can be further increased, and the valve operating angle is further increased as shown by the one-dot chain line in FIG. 8B. be able to.

[0039]

As is apparent from the above description, according to the present invention, in particular, the operating direction of the moving means is set substantially parallel to the moving direction of the disc housing, so that the operating amount of the moving means remains unchanged. It can be efficiently transmitted to the housing. That is, even if the movement amount of the moving means is the same as that of the prior application, the movement amount of the disk housing is sufficiently expanded as compared with the prior application. As a result, the rotational phase difference between the drive shaft and the cam shaft due to the movement of the disc housing can be increased as much as possible, and the operating angle change amount of the intake and exhaust valves can also be increased. Therefore, the valve timing control range is increased, and the required output and fuel consumption can be improved according to the engine operating state.

[Brief description of drawings]

FIG. 1 is a sectional view taken along line AA of FIG. 3 showing an embodiment of the present invention.

FIG. 2 is a sectional view taken along the line AA of FIG. 3 showing the operation of this embodiment.

FIG. 3 is a sectional view of a main part of this embodiment.

FIG. 4 is a plan view of a main portion of this embodiment.

5 is a cross-sectional view taken along the line BB of FIG.

FIG. 6 is a sectional view taken along line CC of FIG.

FIG. 7 is a schematic view showing a drive mechanism used in this embodiment.

FIG. 8 is a valve timing characteristic diagram of the rotational phase difference between the drive shaft and the cam shaft of the present embodiment.

FIG. 9 is a cross-sectional view of an essential part showing an embodiment according to the invention of claim 3;

FIG. 10 is a cross-sectional view of a main part of the device according to the prior application.

[Explanation of symbols]

 21 ... Drive shaft 22 ... Cam shaft 29 ... Annular disk 34 ... Disk housing 34b ... Housing body 34c ... Extension part 41 ... Eccentric cam (moving means) 42 ... Control shaft 51 ... Drive mechanism

Claims (3)

[Claims] 1. A drive shaft which is rotationally driven by an engine, a cam shaft which is provided coaxially with the drive shaft and is rotatable relative to the drive shaft, and a cam having a cam for opening and closing an intake / exhaust valve on the outer periphery, the drive shaft and the cam shaft. And a disk housing that is provided so as to be movable in a substantially radial direction of the drive shaft with a support shaft that is engaged with one end as a fulcrum, and a drive mechanism that drives the disk housing according to an engine operating state. Through a moving means for moving the disk housing through a support hole rotatably in the support hole of the disk housing, and while linking the drive shaft and the camshaft, the center of the drive shaft is offset from the axis of the drive shaft as the disk housing swings. An intake / exhaust valve drive control device, comprising: a disc that moves in a moving manner, and variably controlling an operating angle of the intake / exhaust valve by obtaining a change in an angular velocity of the camshaft in accordance with an eccentric movement of the disc. The operating direction of the means, intake and exhaust valves drive control apparatus for an internal combustion engine, characterized in that set substantially parallel to the moving direction of the disc housing. 2. The intake / exhaust valve for an internal combustion engine according to claim 1, wherein the moving means is an eccentric cam rotatably held in a cam hole formed at an end of the disk housing. Drive controller. 3. The disk housing comprises a substantially annular housing body that rotatably supports the disk in a central support hole, and an extending portion that is radially provided on an outer peripheral surface of the housing body. The eccentric cam is rotatably held in a cam hole formed at the base end portion of the extending portion on the side of the support hole, while the support shaft is engaged with the distal end portion of the extending portion. The intake / exhaust valve drive control device for an internal combustion engine according to claim 1 or claim 2, characterized in that.