JPH10325310A - Drive control device of intake and exhaust valves of internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress a dispersion of an eccentricity of an annular disk caused by a deflection deformation of a control shaft and secure characteristics of a valve lift uniformly. SOLUTION: This device is equipped with a cylindrical cam shaft 11 divided per every cylinder at the periphery of a driving shaft 1 rotating synchronously with an engine, and the cam shaft 11 rotates at an unequal speed corresponding to an eccentric position of the annular disk 17 linking both motions. The annular disk 17 is fitted into a control housing 18 and kept with a free rotation. The control housing 18 is supported to be able to sway by the support shaft of an adjacent support housing 26 and moves eccentrically by an eccentric cam 36 of a control shaft 33. A bearing part 37 of a control shaft supporting the control shaft 33 is formed integratedly with a cam bracket, being off-set to an axial direction, and is located between the one cam 11a and the control housing 18.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an opening / closing timing of an intake valve and an exhaust valve in accordance with an operation state of an internal combustion engine by rotating a cylindrical camshaft arranged around an outer periphery of a drive shaft at an unequal speed relative to the drive shaft. In particular, the present invention relates to an internal combustion engine in which the center of an annular disk provided for each cylinder is eccentric in a direction perpendicular to the axis by a control shaft having an eccentric cam. The present invention relates to an intake / exhaust valve drive control device.

[0002]

2. Description of the Related Art Various types of devices for variably controlling the opening / closing timing and operating angle of intake and exhaust valves have been conventionally provided. One of such devices is disclosed in, for example, JP-A-7-1194.
As described in Japanese Patent Publication No. 25, there is known an apparatus applying the principle of a non-uniform velocity joint. This is because a cylindrical camshaft divided for each cylinder is provided on the outer periphery of a drive shaft that rotates in synchronization with the rotation of the engine, and a flange portion at the end of the camshaft and a flange portion on the drive shaft side are provided. And a pair of pins that are engaged with the respective engagement grooves are provided in an annular disk interposed between the two flange portions, and the annular disk is provided in a control housing. In this way, the rotary disk is rotatably held, and the annular disk can be eccentric with respect to the camshaft through the control housing. By controlling the amount of eccentricity, the valve lift characteristics can be changed. ing.

Further, Japanese Patent Application Laid-Open No. 7-119425 discloses a configuration using an eccentric cam to move a control housing in a direction perpendicular to the axis. That is, the control housing is swingably supported by the support shaft, and a circular cam fitting hole is formed in the control housing. The eccentric cam formed in the control shaft is fitted in the cam fitting hole. It is fitted rotatably. Then, by controlling the rotational position of the control shaft by an actuator, the control housing is moved in a direction perpendicular to the axis to control the amount of eccentricity.

Here, the control shaft is disposed immediately above the drive shaft and the camshaft. The control shaft is rotatably supported on an upper portion of a cam bracket that supports the camshaft with the cylinder head. I have. Specifically, a bearing bracket for the control shaft is disposed on the cam bracket, and is fastened together with the cylinder head by a pair of bolts penetrating both.

[0005]

In the intake / exhaust valve drive control device of the type described above, the valve lift characteristic depends on the eccentric amount of the annular disk, that is, the distance between the center of rotation of the annular disk and the center of rotation of the drive shaft. Therefore, it is important to control the amount of eccentricity with high accuracy.
In particular, in a multi-cylinder internal combustion engine, the amount of eccentricity of the annular disk must be ensured uniformly in each cylinder.

However, in the above-described conventional configuration, the position for supporting the control shaft is located away from the control housing when viewed in the axial direction. Therefore, when the eccentric cam receives a load from the control housing due to the reaction force of the valve spring. In addition, the control shaft is likely to bend and deform, and as a result, the position accuracy of the control housing is low. Therefore, there is a disadvantage that the valve lift characteristics of each cylinder greatly vary, and the configuration in which the control shaft is disposed immediately above the camshaft as in the above-mentioned publication increases the overall height of the internal combustion engine.

[0007]

An intake / exhaust valve drive control device for an internal combustion engine according to the present invention is provided with a drive shaft that rotates in synchronization with the rotation of the engine and an outer periphery of the drive shaft so as to be relatively rotatable. A cylindrical camshaft which is divided for each cylinder and has a cam for driving an intake / exhaust valve on an outer periphery thereof; a first flange provided at one end of the camshaft; A second flange portion provided on the drive shaft side so as to oppose each other, and is disposed between the two flange portions, and the two flange portions are eccentrically linked to each other to transmit rotational motion therebetween. While holding the annular disk and the annular disk rotatably,
A control housing supported to be swingable in a direction perpendicular to the axis,
A control shaft having an eccentric cam rotatably fitted to the control housing, the control shaft moving the control housing in a direction perpendicular to the axis by the rotation of the eccentric cam. The center of the shaft and the center of the camshaft are offset from each other on the plane of the cylinder head, and the control shaft bearing supporting the control shaft is provided between the cam of the camshaft and the control housing. And connected to a cam bracket that supports the camshaft on the cylinder head.

[0008] In a further specific aspect, the cam bracket supports a cam journal portion between a pair of cams in a camshaft, and the cam bracket and the control shaft bearing portion are connected in the axial direction. Are connected in an offset state.

That is, in this type of intake / exhaust valve drive control device, valve lift characteristics are determined by the amount of eccentricity of the annular disk, that is, the distance between the center of rotation of the annular disk and the center of rotation of the drive shaft. Here, since the annular disk is rotatably held by the control housing, the eccentric amount is determined by the relative positional relationship between the control housing and the center of rotation of the drive shaft. In the present invention,
The bearing portion of the control shaft that determines the swing position of the control housing is located between the cam of the camshaft and the control housing when viewed in the axial direction, and is close to the control housing. Therefore, even if a load due to the reaction force of the valve spring acts on the control shaft from the control housing, the flexural deformation of the control shaft is reduced, and a decrease in the positional accuracy of the control housing is suppressed.

[0010] Further, since the control shaft is not at a position directly above the camshaft but at a position offset to the side, the overall height of the internal combustion engine can be suppressed low.

According to the third aspect of the present invention, the control shaft bearing portion is directly fixed to the cylinder head # with at least one bolt separately from a bolt passing through the cam bracket.

Therefore, the cylinder head is directly supported by the cylinder head, and the support rigidity is high.

Further, in the invention according to claim 4, the side surface of the control shaft bearing portion regulates the movement of the control housing in one axial direction. In other words, the control housing directly or indirectly abuts the side surface of the control shaft bearing,
The position in the axial direction is regulated.

Further, in the invention according to claim 5, a stopper member for restricting the movement of the control housing in the other axial direction is attached to the control shaft bearing. The control housing directly or indirectly abuts the stopper member to regulate the axial position thereof. That is,
The control shaft bearing portion and the stopper member sandwich the control housing from both sides, and the axial movement of the control housing is restricted in both directions.

According to the invention of claim 6, the stopper member engages with the groove on the outer periphery of the control shaft to regulate the axial movement of the control shaft.

According to the present invention, an oil passage extending from the cam bracket to the control shaft bearing portion is formed, and a tip end of the oil passage is formed on the control shaft bearing surface in the axial direction of the bearing surface. Is opened at a position offset from the center of the control housing toward the control housing.

A part of the lubricating oil supplied to the cam bracket to lubricate between the cylinder head side and the camshaft is supplied to the control shaft bearing via the oil passage, and the lubricating oil is supplied to the control shaft. Lubricate. Further, the lubricating oil lubricated between the control shaft and the control shaft flows in the axial direction on the contact surface with the control shaft and flows out to the outside. Here, since the front end of the oil passage is offset toward the control housing, most of the lubricating oil is directed toward the control housing and is used for lubricating various parts on the control housing, for example, eccentric cams.

Further, according to the present invention, an arc-shaped oil reservoir surrounding the lower part of the control shaft is formed on a side surface of the control shaft bearing on the control housing side, and a leading edge of the oil reservoir is formed. Thus, the axial movement of the control housing is restricted.

In this configuration, the lubricating oil which has flowed out to the control housing side after lubricating the control shaft bearing surface,
The oil is collected in the oil reservoir below the control shaft, and is more reliably supplied to the control housing side in contact with the leading edge.

According to the ninth aspect of the present invention, an oil ejection hole for supplying lubricating oil toward the cam is connected to the oil passage. Therefore, the contact portion between the cam and the intake / exhaust valve is simultaneously lubricated by the lubricating oil ejected from the oil ejection hole.

According to a tenth aspect of the present invention, a support housing held rotatably relative to the camshaft is disposed between the control housing and the control shaft bearing, and is provided on the support housing. The control housing is swingably supported by a support shaft, and the rotational position of the support housing is regulated by the control shaft.

That is, in the tenth aspect of the present invention, the control housing is supported by the support housing so as to be swingable, and the support housing is rotatably held by the camshaft. The above-described eccentricity can be accurately obtained by the swinging amount when the housing is swung relatively to the housing. Therefore, a desired amount of eccentricity can be accurately obtained by moving the control housing about the support shaft by the control shaft having the eccentric cam.

[0023]

According to the intake / exhaust valve drive control apparatus for an internal combustion engine according to the present invention, the control shaft for defining the amount of eccentricity of the annular disk is supported at a position close to the control housing in the axial direction. The bending deformation of the control shaft due to the reaction force is suppressed, and the positional accuracy of the control housing is improved. In particular, in a multi-cylinder internal combustion engine, variations in valve lift characteristics of each cylinder can be suppressed. Moreover, by offsetting the control shaft from immediately above the camshaft, the overall height of the internal combustion engine can be reduced.

According to the third aspect of the present invention, the support rigidity of the control shaft bearing is improved, and the variation in the position of the control housing caused by the valve spring reaction force is further reduced.

According to the fourth and fifth aspects of the invention,
The control housing can be positioned in the axial direction using the control shaft bearing portion, and the overall configuration is simplified.

Similarly, according to the configuration of the sixth aspect, the control shaft can be positioned in the axial direction by using the control shaft bearing portion, and the overall configuration is simplified.

According to the seventh, eighth or ninth aspect of the present invention, the lubricating oil lubricating the bearing surface of the control shaft is used for lubricating other lubricating parts. No external lubricating oil passage is required, and the lubricating mechanism can be simplified.

Further, according to the tenth aspect of the present invention, since the support housing for supporting the control housing is held by the camshaft, the amount of eccentricity between the center of rotation of the annular disk and the center of rotation of the drive shaft can be reduced. High accuracy can be maintained without being affected by the processing accuracy or the like.

[0029]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of an intake / exhaust valve drive control device according to the present invention will be described below with reference to the drawings.

FIGS. 1 to 4 show the essential parts of an embodiment of an intake / exhaust valve drive control apparatus according to the present invention.

As shown in FIGS. 3 and 4, a drive shaft 1 which is continuous over all cylinders is disposed above the cylinder head. The drive shaft 1 has a hollow shape in which a lubricating oil passage 2 is formed. A sprocket (not shown) is attached to one end of the drive shaft 1, and is linked to a crankshaft via a timing chain. A cylindrical camshaft 1 divided for each cylinder is provided on the outer circumference of the drive shaft 1.
1 are rotatably fitted, and each camshaft 11
Is provided with a first flange portion 12 having a perfect circular shape. Each of the camshafts 11 has a pair of cams 11a for driving an intake valve or an exhaust valve (not shown), and a journal portion 11b between the pair of cams 11a has a partition wall-like cam bracket mounting side. It is rotatably supported between a semicircular bearing surface recessed in the portion 8 and a cam bracket 13 described later. The cam bracket mounting portion 8 has a lubricating oil supply passage 4 communicating with an oil gallery inside the cylinder head. The lubricating oil supply passage 4 has an oil hole 5 formed in the journal portion 11 b of the camshaft 11 and an oil hole formed in the drive shaft 1. Lubricating oil is introduced from the lubricating oil supply passage 4 to the lubricating oil passage 2 inside the drive shaft 1 through the hole 6.

A short sleeve 15 is fixed to the drive shaft 1, and a second flange 16 is formed at an end of each sleeve 15 so as to face the first flange 12. I have. An annular disk 17 having an annular shape is interposed between the flange portions 12 and 16. The annular disk 17 is rotatably held in a circular opening 18 a of the control housing 18. Specifically, a roller bearing 25 in which a number of needles are arranged is provided on the inner periphery of the opening 18 a of the control housing 18, and the annular disc 17 is held via the roller bearing 25.

The first flange portion 12 and the second flange portion 16 have engaging grooves 19,
20 are formed. The two engagement grooves 19 and 20 are arranged at positions different from each other by 180 °. The annular disk 17 has holding holes formed at positions 180 ° different from each other, and a first pin 23 and a second pin 24 are rotatably fitted to the holding holes, respectively.
The pins 23 and 24 project in opposite directions to each other, and the distal end of the first pin 23 is slidably engaged with the engagement groove 19 of the first flange portion 12 and the second pin 2
4 is slidably engaged with the engagement groove 20 of the second flange portion 16. The side surfaces of the tips of the pins 23 and 24 that are in sliding contact with the engagement grooves 19 and 20 are machined into a pair of parallel planes.

The engagement grooves 19, 20 and the pins 23, 2
In order to lubricate a sliding portion with the drive shaft 4, a pair of oil holes 9 is formed in a position covered by the camshaft 11 of the drive shaft 1 along a diametric direction for each cylinder so as to penetrate the drive shaft 1. The lubricating oil is guided from the lubricating oil passage 2 inside 1 to the inner circumference of the annular disk 17 through a fitting gap with the inner circumference of the camshaft 11.

The above-described eccentric type variable valve mechanism itself has a known structure in, for example, the above-mentioned Japanese Patent Application Laid-Open No. 7-119425, and a detailed description thereof will be omitted. When the camshaft 11 is at a concentric position with respect to the center of the shaft 1, each camshaft 11 rotates at a constant speed with respect to the drive shaft 1, and a valve lift characteristic along the profile of the cam 11a is obtained. When the annular disk 17 is eccentric with respect to the center of the drive shaft 1, it becomes a kind of non-uniform velocity joint, and each camshaft 11 rotates at irregular speed with respect to the drive shaft 1. Thus, the valve lift characteristics and the valve operating angle change according to the amount of the eccentricity.

As shown in FIG. 1, the control housing 18 for rotatably holding the annular disk 17 includes a drive shaft 1.
It has a substantially triangular plate shape along a plane orthogonal to. A support housing 26 having a plate shape having the same outer shape as the control housing 18 is provided adjacent to the control housing 18.
Is provided. As shown in FIG. 2, the support housing 26 has a circular opening 26a in the center, and the first flange portion is formed on the inner periphery of the opening 26a via a roller bearing 27 composed of a large number of needles. 12 are rotatably fitted. That is, the support housing 26
Is held by the first flange portion 12 at the end of the camshaft 11 so as to be relatively rotatable.

The control housing 18 and the support housing 26 each having a plate shape are in close contact with each other in the axial direction of the drive shaft 1. That is, the respective one end faces are in contact with each other. Support shaft fitting holes 27 and 28 are formed through the lower portions of the housings 18 and 26, respectively, and the support shaft 29 is relatively densely and rotatably inserted therein. That is, both housings 18, 2
6 are connected to each other so as to be swingable about the support shaft 29. The support shaft 29 is, as shown in FIG.
Both ends having concave grooves protrude from the end surfaces of the housings 18 and 26, respectively.
It is prevented by 0, 30. The support shaft 29 is connected to the support housing 26 and the control housing 1.
8 may be provided in a fixed form.

Slider engagement grooves 31 and 32, which are open in the radial direction of the openings 18a and 26a, respectively, are formed at the upper portions of the control housing 18 and the support housing 26, that is, at the ends opposite to the support shaft 29. It is notched in a substantially rectangular shape. And these slider engagement grooves 3
A control shaft 33 is provided in parallel with the drive shaft 1 so as to pass through the drive shafts 1 and 32.

More specifically, a rectangular first slider 34 is formed in the slider engagement groove 32 of the support housing 26 with an opening 26a.
2, and the shaft of the control shaft 33 is rotatably inserted into a circular opening at the center of the first slider 34 as shown in FIG. Mated. Similarly, a rectangular second slider 35 is formed in the slider engagement groove 31 of the control housing 18 with the opening 18a.
A circular eccentric cam 36 formed on the control shaft 33 is slidably engaged in the radial direction of the second slider 35, and is formed in a true circular opening at the center of the second slider 35 in FIG.
As shown in FIG. In this embodiment, for ease of assembly, the second slider 35 is divided into two parts as shown in FIG.
The eccentric cam 36 is incorporated in the engagement groove 31 so as to sandwich the eccentric cam 36 from both sides.

The control shaft 33 is continuous over all the cylinders, like the drive shaft 1, and has one end connected to a hydraulic actuator (not shown) and the other end connected to the control shaft. A position sensor (not shown) for detecting the rotational position of the motor 33 is provided.

The control shaft 33 is rotatably supported by a control shaft bearing 37 integrated with the cam bracket 13 as shown in FIG.

FIGS. 5 to 9 show the above-mentioned cam bracket 13.
3 shows a specific configuration of a bearing member 41 provided with a control shaft bearing portion 37.

As shown in these figures, the bearing member 41
Is a substantially rectangular block-shaped cam bracket 13 in which a semicircular bearing surface 13a is cut out, and an arm portion 42 extending from one side of the cam bracket 13 in the axial direction of the drive shaft 1.
And a control shaft bearing portion 37 connected diagonally upward from the tip of the arm portion 42 toward the drive shaft 1. The control shaft bearing 3
Reference numeral 7 denotes a bearing body 43 integrally formed with the cam bracket 13 and the arm 42, and a cap 44 fixed to the bearing body 43 by a pair of bolts 45, each having a semicircular bearing surface. 43a and 44a are formed. As is apparent from FIG. 5, both divided surfaces are inclined with respect to the lower surface of the cam bracket 13, that is, the mounting surface to the cylinder head. The lower surface side of the bearing body 43 is formed in an arc shape centering on the drive shaft 1.

The cam bracket 13 has a bearing surface 13a.
Are fixed to the cylinder head by a pair of bolts 46 arranged symmetrically on both sides of the cylinder head. Further, a flange portion 47 is further formed integrally with the outside of the arm portion 42, and the flange portion 47 is fixed to the cylinder head with one bolt 48.

As is apparent from FIG. 5, the control shaft 33 is held by the bearing member 41 at a position offset laterally, not directly above the camshaft 11. Specifically, as shown in FIG. 6, the center S1 of the camshaft 11 and the center S2 of the control shaft 33 are offset by Δ1 in the plan view. 6, the control shaft bearing 37 is offset from the cam bracket 13 in the axial direction of the camshaft 11, etc., and the cam bracket 13 is located between the pair of cams 11a. On the other hand, the control shaft bearing 37 is located between the cam 11a and the control housing 18 as shown in FIG. More specifically, the control shaft bearing 37 is in close contact with the support housing 26 and regulates the axial movement between the support housing 26 and the control housing 18 in one direction.

In order to restrict the movement of the support housing 26 and the control housing 18 to the opposite side in the axial direction,
In this embodiment, a stopper member 49 made of a metal plate is provided. As shown in FIG. 10, the stopper member 49 is formed by bending a metal plate into an L-shape, and has a base end portion 49a fastened to the cap portion 44 by a bolt 45 together with a distal end portion. 49b is the control housing 1
8 are arranged along the end face. That is, by the stopper member 49 and the control shaft bearing 37,
The control housing 18 and the support housing 26 are sandwiched from both sides. Further, in this embodiment, the tip portion 49b of the stopper member 49 having the arc-shaped notch is engaged with one of the circumferential grooves 50 provided along both ends of the eccentric cam 36 of the control shaft 33, This restricts the movement of the control shaft 33 in the axial direction.

The above-mentioned bearing member 41 is used for the cam bracket 1.
3 is provided with an oil passage extending from the bearing surface 13a to the control shaft bearing portion 37. This oil passage, as shown in FIG.
An oil groove 51 extending from the bearing surface 13a of the cam bracket 13 along the lower surface of the arm portion 42, an oil hole 52 extending upward from one end of the oil groove 51, as shown in FIG.
And an oil groove 53 formed in the cap portion 44 such that the tip is open to the bearing surface 44a. Here, as shown in FIG. 6, the opening position of the leading end of the oil groove 53 on the bearing surface 44a is offset from the axial center M of the bearing surface 44a toward the support housing 26 by Δ2.

In the above arrangement, the support housing 26 is rotatably held by the camshaft 11 rotatably supported by the cylinder head, and the support housing 2 is held by the control shaft 33.
6 is restricted. Since the slidable first slider 34 is interposed between the control shaft 33 and the support housing 26, the control shaft 33 restricts only the rotation of the support housing 26, for example, along the vertical direction in FIG. The thermal expansion difference and the like are absorbed by the sliding of the first slider 34. When the control shaft 33 provided with the eccentric cam 36 rotates, the control housing 18 moves in the left-right direction in FIG. 1 according to the position of the eccentric cam 36. That is, the control housing 18 swings relatively to the support housing 26 about the support shaft 29, and the control housing 18
The center of rotation of the annular disk 17 held at this position is eccentric from the center of rotation of the drive shaft 1 and the camshaft 11.

The control housing 18 and the support housing 26 are connected at one end by a common support shaft 29 and positioned at the other end by a common control shaft 33. Without being affected, the amount of eccentricity of the housings 18 and 26 and the amount of eccentricity from the center of rotation of the drive shaft 1 to the center of rotation of the annular disk 17 can be extremely accurately adjusted in accordance with the amount of eccentricity of the eccentric cam 36. can get.

According to the configuration of the above embodiment, the control shaft 33 is not disposed immediately above the camshaft 11 but is offset laterally, so that the overall height of the entire internal combustion engine can be suppressed low. As is apparent from FIG. 6, since the bolts 46 and the bolts 48 are arranged on both sides of the control shaft 33, a sufficiently high support rigidity can be obtained for the cylinder head even if the bolts are offset as described above. Further, since the control shaft bearing 37 is offset toward the control housing 18 when viewed in the axial direction of the drive shaft 1, the valve spring reaction force is reduced by the annular disk 17.
, The deflection of the control shaft 33 due to the load can be reduced, and the variation in the valve lift characteristics caused by the deflection can be suppressed.

Further, a part of the lubricating oil supplied to the cam bracket 13 from the cylinder head side is guided to the control shaft bearing 37, and the space between the control shaft 33 and the control shaft 33 is lubricated.
Then, the lubricating oil flows out further in the axial direction and is supplied to the support housing 26 side, and the first and second sliders 34,
35 etc. are lubricated. Here, as described above, since the opening position of the leading end of the oil groove 53 in the bearing surface 44a is offset toward the support housing 26, most of the lubricating oil is guided to the support housing 26 side, and the lubrication of each part is more efficiently performed. Is performed.

Next, FIGS. 11 to 14 show different embodiments of the present invention. In this embodiment, an arc-shaped oil reservoir 61 surrounding the lower part of the control shaft 33 is formed on the side face of the control shaft bearing part 37 of the bearing member 41. The oil reservoir 61 projects slightly outside the bearing surface on the side of the control shaft bearing 37 on the side of the support housing 26. In this embodiment, the lower half of the control shaft 33 is provided. , And is formed over the bearing body 43 and the cap 44. The configuration of the oil passage in the bearing member 41 is the same as that of the above-described embodiment.

In the structure of this embodiment, the end surface of the support housing 26 abuts on the end surface of the semicircular oil reservoir 61, and the support housing 26 and the control housing 18 are positioned in the axial direction. Therefore, the lubricating oil that has overflowed from between the bearing surfaces 43a and 44a of the control shaft bearing portion 37 and the control shaft 33 temporarily accumulates on the oil reservoir 61 between the lubricating oil and the support housing 26. Each part of the support housing 26 and the control housing 18 can be more reliably lubricated.

Next, FIGS. 15 to 17 show still another embodiment of the present invention. In this embodiment, a pair of cams 11a are simultaneously lubricated, and an extension 62 extends from one side of the cam bracket 13 of the bearing member 41 to the side opposite to the arm 42. An oil ejection hole 63 is formed in the portion 62 toward the one cam 11a. The oil ejection hole 63 is continuous with the oil groove 51 via an oil groove 64 on the lower surface. Further, a similar oil ejection hole 65 is formed from the middle of the oil groove 51 extending to the lower surface of the arm portion 42 toward the other cam 11a. These oil jet holes 6
The lubricating oil squirted from 3, 65 collides with the cams 11a, thereby lubricating the cams 11a. According to this configuration, the lubrication mechanism of the entire valve train is simplified, and lubricating oil can be supplied to the cam 11a from a short distance, so that there is an advantage that oil mist is reduced.

[Brief description of the drawings]

FIG. 1 is a front view of a main part showing one embodiment of the present invention.

FIG. 2 is a rear view of a main part as viewed from a side opposite to FIG. 1;

FIG. 3 is a sectional view taken along the line AA of FIG. 1;

FIG. 4 is a sectional view taken along the line BB of FIG. 1;

FIG. 5 is a front view showing a bearing member.

FIG. 6 is a top view of the same.

FIG. 7 is a bottom view of the same.

FIG. 8 is a side view of the same.

FIG. 9 is a sectional view taken along the line CC of FIG. 6;

FIG. 10 is a perspective view of a stopper member.

FIG. 11 is a front view showing a different embodiment of the bearing member.

FIG. 12 is a top view of the same.

FIG. 13 is a bottom view of the same.

FIG. 14 is a side view of the same.

FIG. 15 is a top view showing still another embodiment of the bearing member.

FIG. 16 is a sectional view taken along the line DD in FIG. 15;

FIG. 17 is a bottom view of the bearing member.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Drive shaft 2 ... Lubricating oil passage 11 ... Camshaft 12 ... 1st flange part 13 ... Cam bracket 16 ... 2nd flange part 17 ... Annular disk 18 ... Control housing 26 ... Support housing 29 ... Support shaft 33 ... Control shaft 37 … Control shaft bearing part 41… bearing member 61… oil reservoir 63, 65… oil ejection hole

Continued on the front page (72) Inventor Keisuke Takeda 1370 Onna, Atsugi-shi, Kanagawa Pref.

Claims (10)

[Claims] 1. A drive shaft that rotates in synchronization with the rotation of an engine, and a cam that is provided on the outer periphery of the drive shaft so as to be relatively rotatable, is divided for each cylinder, and drives an intake / exhaust valve. A cylindrical camshaft having an outer periphery, a first flange portion provided at one end of the camshaft, and a second flange portion provided on the drive shaft side so as to face the first flange portion, respectively. An annular disk disposed between the two flange portions, and eccentrically interlocking with each flange portion to transmit rotational motion between the two; and an annular disk rotatably held and in a direction perpendicular to the axis. A control housing rotatably supported, a control shaft having an eccentric cam rotatably fitted to the control housing, and moving the control housing in a direction perpendicular to the axis by the rotation thereof; An intake / exhaust valve drive control device for an internal combustion engine, comprising: a control unit that centers the control shaft and the center of the camshaft on a plane of a cylinder head, and that supports the control shaft. A drive control for intake and exhaust valves of an internal combustion engine, wherein a shaft bearing portion is located between a cam of the camshaft and the control housing, and is connected to a cam bracket supporting the camshaft on a cylinder head. apparatus. 2. The cam bracket supports a cam journal between a pair of cams on a camshaft, and the cam bracket and the control shaft bearing are connected in an axially offset state. The intake / exhaust valve drive control device for an internal combustion engine according to claim 1, wherein: 3. The suction system for an internal combustion engine according to claim 2, wherein the control shaft bearing portion is directly fixed to the cylinder head with at least one bolt separately from a bolt passing through the cam bracket. Exhaust valve drive control device. 4. The internal combustion engine according to claim 1, wherein a side surface of the control shaft bearing portion restricts movement of the control housing in one axial direction. Exhaust valve drive control device. 5. The intake / exhaust valve of an internal combustion engine according to claim 4, wherein a stopper member for restricting the control housing from moving in the other axial direction is attached to the control shaft bearing. Drive control device. 6. An intake / exhaust valve for an internal combustion engine according to claim 5, wherein said stopper member engages with a groove on the outer periphery of said control shaft to restrict axial movement of said control shaft. Drive control device. 7. An oil passage from the cam bracket to the control shaft bearing portion is formed, and a tip of the oil passage is formed on the control shaft bearing surface from the axial center of the bearing surface to the control housing. 5. An opening at a position offset closer to the opening.
7. An intake / exhaust valve drive control device for an internal combustion engine according to any one of claims 6 to 6. 8. An arc-shaped oil reservoir that surrounds a lower portion of the control shaft is formed on a side surface of the control shaft bearing on the control housing side, and a shaft of the control housing is formed by a leading edge of the oil reservoir. 8. The intake / exhaust valve drive control device for an internal combustion engine according to claim 7, wherein the movement in the direction is regulated. 9. An intake / exhaust valve drive control device for an internal combustion engine according to claim 7, wherein an oil ejection hole for supplying lubricating oil toward said cam is connected to said oil passage. 10. A control housing, which is rotatably held on the camshaft, is disposed between the control housing and the control shaft bearing. The control housing is mounted on a support shaft provided on the support housing. The drive control of the intake and exhaust valves of the internal combustion engine according to any one of claims 1 to 9, wherein the support shaft is swingably supported and the rotational position of the support housing is regulated by the control shaft. apparatus.