JP5503469B2 - Variable valve timing valve operating system for in-vehicle internal combustion engine - Google Patents

Description

  The present invention relates to a valve gear that makes a valve timing variable in a vehicle-mounted internal combustion engine.

  In this type of valve operating device, a variable cam member is provided on the valve operating camshaft in addition to the normal intake cam and exhaust cam, and the action of the variable cam member on the valve can be switched between valid and invalid, Various variable valve timing valve operating apparatuses that perform valve operation at valve timings other than normal intake / exhaust valve timings when set to be effective have been proposed (see, for example, Patent Document 1).

International Publication No. 2009/069425

  Patent Document 1 discloses an internal combustion engine equipped with an EGR (exhaust gas recirculation) device. In the variable valve timing valve operating device, an EGR cam can be rotated relative to a camshaft in addition to a normal intake / exhaust cam. When the EGR valve is operated by the rotation of the EGR cam by the engagement of a displacement member that engages and disengages with the EGR cam, the EGR port of the combustion chamber opens and closes at a predetermined timing and is stored in the gas storage chamber Exhaust gas is introduced into the combustion chamber for combustion.

  A mechanism for displacing a displacement member that engages and disengages with the EGR cam is such that a displacement cam, a press cam, and a displacement shaft connected to the displacement member are slidably inserted into the central shaft hole of the cam shaft, while the cam shaft is defined in the head cover. A solenoid is mounted so as to protrude in the opposite direction, and an arm is provided between the solenoid and the displacement cam so as to swing up and down around the swing shaft, and the upper end (power point) of the arm advances and retreats. A displacement cam connected to the rod and urged by a spring is in contact with the lower end (operation point) of the arm.

If the solenoid retracts the rod, the lower end of the arm pushes the displacement cam, and the displacement member is detached from the EGR cam via the pressing cam and displacement shaft, the EGR cam does not act on the EGR valve.
When the solenoid advances the rod, the displacement cam, the pressing cam, and the displacement shaft are moved by the spring, and the displacement member connected to the displacement shaft engages with the EGR cam and rotates together. The EGR cam becomes the EGR valve. The exhaust gas is used for combustion at a predetermined timing.

  In the arm in Patent Document 1, the upper and lower centers are fulcrums supported by a swing shaft, the upper end is a force point at which the driving force of the solenoid acts, and the lower end is an action point that acts on the displacement cam. Since the length is short, the solenoid is disposed close to the cam shaft and protrudes to the side of the head cover so as not to interfere with the valve mechanism.

  Since the solenoid protrudes to the side of the head cover, when the internal combustion engine is mounted on the vehicle, the arrangement of the internal combustion engine may be restricted so that the solenoid does not get in the way, and the protruding solenoid is protected from external force. In order to cut off the operation sound of the solenoid, it is necessary to cover the solenoid with a dedicated shielding member.

  The present invention has been made in view of the above points, and a purpose of the present invention is to protect an actuator from an external force without using a dedicated shielding member and to prevent an operating sound of the actuator from being interrupted. The variable valve timing valve is provided.

  In order to achieve the above object, the invention according to claim 1 is a valve camshaft rotatably supported by a cylinder head (15) of an internal combustion engine mounted on a saddle riding type vehicle and covered by a head cover (20). (41), a variable cam member (50) that is fitted on the outer periphery of the valve camshaft (41) so as not to be relatively rotatable and is slidably displaced in the axial direction to vary the valve timing, and the variable cam member ( A slider mechanism (52) that slides and displaces 50) in the axial direction, and a variable valve timing drive mechanism (60) that transmits the drive of the actuator (61) to the slider mechanism (52) to change the valve timing. A variable valve timing valve operating apparatus for an on-vehicle internal combustion engine provided with the fuel, wherein the internal combustion engine is suspended from a body frame of the straddle-type vehicle with a cylinder slightly tilted forward and is supported so as to straddle the body frame from above. A tank (6) covers the internal combustion engine from above. The head cover (20) faces the bottom plate of the fuel tank (6), the actuator (61) is supported on the head cover (20), and the upper part is covered by the fuel tank (6). A variable valve timing valve operating apparatus for an on-vehicle internal combustion engine, wherein the valve timing cam valve is disposed at a position overlapping with the valve operating camshaft (41) when viewed in a cylinder axis direction.

  According to a second aspect of the present invention, in the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to the first aspect, the variable valve timing driving mechanism (60) is a pivotally supported pivotally supported by a fulcrum (P). The moving arm (65) is a mechanism that receives the operation of the actuator (61) at a force point (Q) and transmits it to the slider mechanism (52) at an action point (R), and the head cover that supports the actuator (61) (20) is characterized in that it is positioned with respect to the cylinder head (15) by at least two knock members (72), and is attached to a mating surface perpendicular to the cylinder axis via a seal member (18). To do.

  According to a third aspect of the present invention, in the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to the second aspect, the swing arm (65) is a swing shaft (P) serving as a fulcrum (P) on the head cover (20). 64), and the head cover (20) is characterized in that the seal member (18) interposed between the cylinder head (15) and the mating surface is an elastic seal member and is elastically supported. To do.

  According to a fourth aspect of the present invention, in the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to any one of the first to third aspects, a part of the ceiling wall (20u) of the head cover (20) is upward. And the actuator (61) is cantilevered by the protrusion (21, 22).

  According to a fifth aspect of the present invention, in the variable valve timing valve operating apparatus for the on-vehicle internal combustion engine according to the fourth aspect, the head cover (20) is formed with a reinforcing rib (23r) extending in parallel to the cylinder axis on the inner surface. It is characterized by that.

  According to a sixth aspect of the present invention, in the variable valve timing valve operating apparatus for the on-vehicle internal combustion engine according to the fourth or fifth aspect, the ceiling wall (20u) of the head cover (20) is a concave portion (20uh) The actuator (61) is cantilevered by the protrusions (21, 22) by inserting the lower part into the recess (20uh).

  According to a seventh aspect of the present invention, in the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to the sixth aspect, the ceiling wall (20u) of the head cover (20) has the recess (20uh) as viewed in the cylinder axial direction. Convex portions (20up) that are formed to extend in the direction in which the valve camshaft (41) is directed at a position that overlaps with the valve camshaft (41) and project upward on both sides of the concave portion (20uh) Is formed to extend in the direction in which the valve camshaft (41) is directed.

  According to an eighth aspect of the present invention, in the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to any one of the first to seventh aspects, the actuator (61) supported by the head cover (20) includes: It is arranged at a position overlapping the center line in the vehicle body width direction of the saddle riding type vehicle in a top view.

  A ninth aspect of the present invention is the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to any one of the first to eighth aspects, wherein the actuator (61) supported by the head cover (20) includes: The main body case has a cylindrical shape parallel to the valve camshaft (41), and is an electromagnetic solenoid in which the drive shaft advances and retreats in the direction in which the valve camshaft (41) is directed.

  According to the variable valve timing valve operating apparatus for an in-vehicle internal combustion engine according to claim 1, the head cover (20) serving as the uppermost end of the internal combustion engine suspended by leaning the cylinder slightly forward on the body frame of the saddle riding type vehicle. The actuator (61) for changing the valve timing is supported at a position overlapping the valve camshaft (41) when viewed in the cylinder axis direction, and is supported so as to straddle the body frame from above the actuator (61). Since the fuel tank (6) covers, the actuator (61) is sandwiched between the head cover (20) and the fuel tank (6), and the operating sound of the actuator (61) is cut off by the fuel tank (6) in particular. In addition, the actuator (61) is protected by the fuel tank (6), and a shielding member dedicated to the actuator is not required.

  According to the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to claim 2, the head cover (20) supporting the actuator (61) is constituted by at least two knock members (72) with respect to the cylinder head (15). By positioning and attaching to the mating surface perpendicular to the cylinder axis via the seal member (18), the displacement along the mating surface of the head cover (20) with respect to the cylinder head (15) is regulated, and the relative positional relationship The oscillating arm (65) receives the operation of the actuator (61) at the force point (Q) and transmits the operation of the variable valve timing drive mechanism (60) to the slider mechanism (52) at the action point (R). Is performed accurately, and the valve timing can be changed smoothly and accurately.

  According to the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to claim 3, the seal member (18) interposed on the mating surface with respect to the cylinder head (15) is an elastic seal member and is elastically supported. Since the swing arm (65) is pivotally supported by the swing shaft (64) on the head cover (20), the engine vibration on the cylinder head (15) side is absorbed and transmitted to the head cover (20). 20) The swinging arm (65) on the side can reduce the influence of engine vibration on the operation of the variable valve timing drive mechanism (60), guaranteeing accurate operation and changing the valve timing accurately. .

  According to the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to claim 4, a part of the ceiling wall (20u) of the head cover (20) protrudes upward to form a protrusion (21, 22), and the actuator Since (61) is cantilevered by the protrusions (21, 22), the weight of the head cover (20) including the actuator (61) can be reduced.

According to the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to claim 5, since the reinforcing rib (23r) is formed on the inner surface of the head cover (20) in parallel with the cylinder axis, the reinforcing rib (23r ), The head cover (20) is reinforced to secure reinforcement and rigidity of the protrusions (21, 22) that cantilever-support the actuator (61), so that the protrusion (22) is fixed. The drive of the actuator (61) is accurately transmitted to the slider mechanism (52), and the valve timing can be changed with high accuracy.
At the same time, the reinforcing rib (23r) extending parallel to the cylinder axis, i.e. substantially downward, collects the splashed oil from the drive of the valve mechanism (40), cam chain (37), etc. 13p) To improve the return to etc.

  According to the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to claim 6, the ceiling wall (20u) of the head cover (20) is formed with a recess (20uh) recessed downward, and the actuator (61) Since the lower part is inserted into the recess (20uh) and is cantilevered by the protrusions (21, 22), the head cover (20) has higher rigidity due to the recess (20uh) of the ceiling wall (20u), and the actuator ( 61) is supported by inserting the lower portion into the concave portion (20uh), so that the upward protrusion of the actuator (61) can be suppressed as much as possible.

  According to the variable valve timing valve operating system for an on-vehicle internal combustion engine according to claim 7, the ceiling wall (20u) of the head cover (20) has the concave portion (20uh) connected to the valve operating camshaft (41) as viewed in the cylinder axial direction. Convex portions (20up, 20up) that are formed to extend in the direction in which the valve camshaft (41) is directed at the overlapping position and project upward on both sides of the recess (20uh) are valve camshaft (41) The cylinder head fastening bolt (17) and the valve mechanism rocker arm (44i, 44up) are formed by the projections (20up, 20up) of the ceiling wall (20u) of the head cover (20). It is possible to suppress the upward protrusion of the actuator (61) while avoiding interference such as 44e).

  According to the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to claim 8, the actuator (61) supported by the head cover (20) is located at a position overlapping the center line in the vehicle body width direction of the saddle riding type vehicle in a top view. Because it is arranged, the actuator (61) is completely covered by the fuel tank (6) supported so as to straddle the body frame of the saddle riding type vehicle from above, so that a separate dedicated shielding member is unnecessary. The weight balance of the vehicle body can be maintained.

  According to the variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to claim 9, the actuator (61) supported by the head cover (20) has a cylindrical shape in which the main body case is parallel to the valve operating camshaft (41). None, because the solenoid shaft moves the drive shaft back and forth in the direction that the valve camshaft (41) is directed, power transmission to the slider mechanism (52) that slides linearly can be simplified, reducing the number of parts Thus, the structure can be simplified.

1 is an overall side view of a motorcycle equipped with an internal combustion engine according to an embodiment of the present invention. FIG. 2 is a left side view in which the internal combustion engine is partially omitted, with a partial cross section. It is a right sectional view of the cylinder head of the internal combustion engine and its vicinity. It is a rear sectional view (IV-IV line sectional view of FIG. 11). It is the VV sectional view taken on the line of FIG. 4 and FIG. It is a disassembled perspective view of a valve cam shaft, a steady cam member, and a variable cam member. It is an exploded sectional view of a valve camshaft and a driven cam chain sprocket incorporating a slider mechanism and the like. It is the VIII-VIII sectional view taken on the line of FIG. It is a perspective view of a rocking arm. It is a top view of a cylinder head incorporating a valve operating mechanism. It is a top view of a head cover. It is a reverse view of the head cover. It is the XIII-XIII sectional view taken on the line of FIG. It is the XIV-XIV sectional view taken on the line of FIG. It is the XV-XV sectional view taken on the line of FIG. 1 is a plan view of a motorcycle showing an arrangement of electromagnetic solenoids.

Hereinafter, an embodiment according to the present invention will be described with reference to FIGS.
The internal combustion engine 10 according to the present embodiment is mounted horizontally on a motorcycle with a transmission integrally provided behind the internal combustion engine 10 with the crankshaft 11 oriented in the left-right direction that is the vehicle width direction.
In the present embodiment, the front, rear, left and right coincide with the front, rear, left and right when the vehicle is used as a reference.

FIG. 1 is an overall side view of a saddle type motorcycle 1 equipped with an internal combustion engine 10 according to an embodiment of the present invention.
The body frame 2 of the motorcycle 1 has a pair of left and right main frames 2m, 2m extending backwards slightly from the head pipe 2h and then bent downward to form steeply inclined portions 2ma, 2ma. Has reached.
Further, a pair of left and right down frames 2d, 2d extend downward from the head pipe 2h at an obliquely steep angle substantially parallel to the steeply inclined portion 2ma of the main frame 2m in a side view.

  The seat rails 2s, 2s extend rearward from the upper portions of the steeply inclined portions 2ma, 2ma of the main frames 2m, 2m through the gussets 2g, 2g, and the central portion of the seat rails 2s, 2s and the steeply inclined portions 2ma, 2ma. The back stays 2b and 2b connecting the lower part of the seat support the seat rails 2s and 2s.

In the body frame as described above, the front fork 3 is pivotally supported on the head pipe 2h, the front wheel Fw is pivotally supported at the lower end thereof, and the front end is pivotally supported below the steeply inclined portions 2ma and 2ma of the main frames 2m and 2m. The rear fork 4 extends rearward, a rear wheel Rw is pivotally supported at the rear end thereof, and a rear cushion 5 is interposed between the rear fork 4 and the gasset 2 g of the vehicle body frame 2.
A fuel tank 6 is installed at the front of the main frames 2m and 2m so that the fuel tank 6 extends from above (see FIG. 16), and a seat 7 is supported by seat rails 2s and 2s behind the fuel tank 6. Is provided.

The internal combustion engine 10 suspended between the main frames 3 and 3 and the down frames 2d and 2d is a SOHC type air-cooled single-cylinder four-cycle internal combustion engine. The cylinder block 14, the cylinder head 15, and the head cover 20 are suspended in an upright position by tilting slightly forward.
The fuel tank 6 covers the upper part of the head cover 20 at the upper part of the slightly tilted cylinder of the internal combustion engine 10.

  An intake pipe 8 extends rearward from the cylinder head 15 of the internal combustion engine 10 to the air cleaner 8a via a throttle body. An exhaust pipe 9 extends forward from the cylinder head 15 and bends downward to bend the internal combustion engine 10. The lower part extends rearward and reaches the muffler 9m on the right side of the rear wheel Rw.

Referring to FIG. 2, in the internal combustion engine 10, a crankcase 13 that supports the crankshaft 11 is formed with a transmission chamber 13 </ b> M that houses a transmission behind the crankcase 13 </ b> C in which the crankshaft 11 is disposed. From the transmission chamber 13M, the output shaft 12 of the transmission protrudes to the left and constitutes a power unit.
Below the crank chamber 13C, an oil sump 13P is formed integrally with the bottom wall bulging somewhat downward to store oil.
The crankcase 13 forming the crank chamber 13C, the transmission chamber 13M, and the oil reservoir 13P has a left-right split structure.

On the front crank chamber 13C of the crankcase 13, a cylinder block 14 having one cylinder 14a and a cylinder head 15 are overlaid on the cylinder block 14 via a gasket. The cylinder head 15 and the cylinder block 14 are integrally fastened to the crankcase 13 together with 16, and the head cover 20 is covered above the cylinder head 15 via an elastic seal member 18 (see FIGS. 3 and 4).
The cylinder block 14, the cylinder head 15, and the head cover 20 stacked on the crankcase 13 extend upward from the crankcase 13 in a slightly forwardly inclined posture (see FIG. 2).

  A piston 31 is fitted in the cylinder 14a of the cylinder block 14 so as to be slidable back and forth (see FIG. 3), and the piston 31 and the crankshaft 11 are connected by a connecting rod 32 to constitute a crank mechanism.

  A combustion chamber 15z is formed in the cylinder head 15 so as to face the piston 31 in the cylinder axial direction corresponding to the cylinder 14a. An intake port 15i extends rearward from the combustion chamber 15z and forwards from the combustion chamber 60. An exhaust port 15e extends (see FIG. 3), and a spark plug 19 is attached to the ceiling wall of the combustion chamber 15z with the tip facing the combustion chamber 15z (see FIG. 4).

  As shown in FIG. 3, the intake valve 33 and the exhaust valve 34 that are slidably supported by the valve guide integrally fitted to the cylinder head 13 are driven by a valve mechanism 40 provided in the internal combustion engine 10. Thus, the intake opening of the intake port 15 i and the exhaust opening of the exhaust port 15 e are opened and closed in synchronization with the rotation of the crankshaft 11.

  Referring to FIGS. 3 and 4, the valve mechanism 40 is a SOHC in which a single valve camshaft 41 is pivotally supported in the left-right direction on a camshaft holder 16 fixed on the cylinder head 15. A rocker arm shaft 43e, 43i is supported by the camshaft holder 16 at the front and rear of the valve camshaft 41, and the intake rocker arm 44i is pivotally supported by the rear rocker arm shaft 43i so that it can swing freely. The exhaust rocker arm 44e is pivotally supported by the front rocker arm shaft 43e so as to be swingable.

  A cylindrical steady cam member 42 having an intake cam lobe 42i and an exhaust cam lobe 42e formed side by side on the outer peripheral surface is press-fitted into the valve camshaft 41, and the steady cam member 42 is integrally removed from the valve camshaft 41. It is fitted.

The intake rocker arm 44i has one end roller 43ir in contact with the intake cam lobe 42i of the steady cam member 42, the other end in contact with the upper end of the valve stem of the intake valve 33, and the other exhaust rocker arm 44e has one end roller 44er in the steady cam. The member 42 is in contact with the exhaust cam lobe 42e, the other end is in contact with the upper end of the valve stem of the exhaust valve 34, and the intake cam rocker arm 44i is rotated by rotation of the steady cam member 42 (intake cam lobe 42i, exhaust cam lobe 42e) together with the valve operating camshaft 41. The exhaust rocker arm 44e swings at a predetermined timing to open and close the intake valve 33 and the exhaust valve 34.

The valve camshaft 41 has a driven cam chain sprocket 36 fixed to the end of the left shaft (see FIG. 4).
On the other hand, a drive cam chain sprocket 35 is fitted on the crankshaft 11, and a cam chain 37 is bridged between the drive cam chain sprocket 35 and the driven cam chain sprocket 36 thereabove (see FIG. 2). ), The rotational power of the crankshaft 11 is transmitted to the rotation of the valve operating camshaft 41 through the cam chain 37 at a half speed of the crankshaft 11, and the intake rocker arm 44i and the exhaust rocker arm are synchronized with the crankshaft 11. The intake valve 33 and the exhaust valve 34 are driven to open and close at the required timing by swinging 44e.

In addition, cam chain chambers 14c, 15c, and 20c are formed as a single cavity on the left side of the cylinder block 14, cylinder head 15, and head cover 20 (see FIG. 4), and the cam chain chambers 14c, 15c, and 20c As shown in FIG. 2, the front chain portion of the cam chain 37 spanned between the driving cam chain sprocket 36 and the upper driven cam chain sprocket 36 is slightly curved and extends vertically. The guide 38 is guided, and the rear rear part of the guide 38 is brought into contact with the tension slipper 39 which is curved in an arcuate shape to maintain an appropriate tension on the cam chain 37.
The tension slipper 39 is pressed behind by a tensioner lifter 39t.

FIG. 6 shows an exploded perspective view of the valve camshaft 41, the steady cam member 42, and the variable cam member 50 that are pivotally supported by the camshaft holder 16 in the left-right direction.
The valve camshaft 41 is a cylindrical member having a central shaft hole 41h. A spline forming portion 41c having a maximum outer diameter is formed at the center in the axial direction with six spline grooves 41cs. A cam fixing portion 41r having a reduced diameter is formed on the right side of the forming portion 41c via a stepped portion, and a journal portion 41j having a further reduced diameter is formed at the right end.
On the other hand, on the left side of the spline forming portion 41c, a left cylindrical portion 41l having a slightly reduced diameter is formed.

In the spline forming portion 41c of the valve camshaft 41, a pair of elongated holes 41s, 41s elongated in the axial direction are formed at the symmetrical positions on the spline grooves 41cs, 41cs at the symmetrical positions.
A keyway 41k is formed at the left end of the valve camshaft 41.
The valve camshaft 41 is accurately formed by cold forging.

A steady cam member 42 is press-fitted and fixed at a predetermined relative angle to the cam fixing portion 41r of the valve operating cam shaft 41.
The steady cam member 42 is press-fitted into the cam fixing portion 41r of the valve operating camshaft 41 with the exhaust cam lobe 42e on the left side and the intake cam lobe 42i on the right side until it comes into contact with the spline forming portion 41c from the right side. Are integrated adjacent to the spline forming portion 41c.

As described above, the steady cam member 42 is integrally fitted on the valve operating cam shaft 41 with the cam fixing portion 41r, and the variable cam member 50 is spline-fitted with the spline forming portion 41c.
Referring to FIG. 6, the variable cam member 50 has six spline protrusions 50cs which are fitted on the six spline grooves 41cs of the spline forming portion 41c of the valve camshaft 41 on the inner peripheral surface. On the outer peripheral surface, a variable cam lobe 50e is formed on the right side.
The variable cam lobe 50e has a base circle whose outer periphery is mostly the same diameter as or slightly smaller than the base circle of the exhaust cam lobe 42e, and a cam crest with a small lift amount projects partially at a predetermined phase angle.

  A pair of pin holes 50p, 50p are formed symmetrically with the thick spline protrusions 50cs, 50cs at a symmetrical position perpendicular to the central axis in the cylindrical portion of the variable cam member 50 other than the variable cam lobe 50e. , 50p, an outer peripheral groove 50v passing through the outer opening is formed on the outer peripheral surface.

  When this variable cam member 50 is spline-fitted to the spline forming portion 41c of the valve camshaft 41 with the variable cam lobe 50e from the left side at a predetermined relative angle, the pin holes 50p and 50p of the variable cam member 50 are valve-operated. It corresponds to the long holes 41s and 41s of the cam shaft 41.

  Referring to FIG. 7, a bearing 46 is fitted to the right end journal portion 41j protruding to the right side of the cam fixing portion 41r into which the steady cam member 42 is press-fitted in the valve camshaft 41, and the variable cam member 50 is splined. A bearing 45 is inserted into the left cylindrical portion 41l on the left side of the fitted spline forming portion 41c, and a flange member 47 is press-fitted at a predetermined relative angle via a key 49 so that the bearing 45 is connected to the spline forming portion 41c. Sandwiched between.

In the flange member 47, the left side portion of the cylindrical portion swells symmetrically in the centrifugal direction to form flange portions 47f and 47f. A screw hole is formed in each of the pair of flange portions 47f and 47f that are rhombic in the axial direction. 47h and 47h are perforated.
In the driven cam chain sprocket 36, the center circular hole 36c is fitted to the left end exposed to the left of the flange member 47 of the valve drive cam shaft 41, and the mounting holes 36h and 36h provided at symmetrical positions are fitted to the flange member 47. The screws 48 and 48 are threaded through and screwed together with the screw holes 47h and 47h to be fixed to the flange member 47 (see FIG. 4).

A slide rod 53 of a slider mechanism 52 that slides and displaces the variable cam member 50 is fitted into the central shaft hole 41h of the valve camshaft 41 so as to be slidable in the left-right axis direction.
The slide rod 53 is slightly reduced in diameter on both sides of the central large-diameter portion 53c, and a pin hole 53p is formed in the central large-diameter portion perpendicular to the axial direction (see FIG. 7).

The slide rod 53 is inserted into the central shaft hole 41h of the valve camshaft 41, and the pin hole 53p is matched with the long holes 41s and 41s of the valve camshaft 41 and the pin holes 50p and 50p of the variable cam member 50. One connecting pin 54 is inserted into the pin holes 50p and 50p, the long holes 41s and 41s, and the pin hole 53p.
The connecting pin 54 is shorter than the inner diameter of the outer peripheral groove 50v of the variable cam member 50, and is prevented from coming off by a retaining ring 55 fitted in the outer peripheral groove 50v, and both ends of the connecting pin 54 are pin holes 50p, 50p of the variable cam member 50. To move together with the variable cam member 50.

Therefore, when the slide rod 53 is slid in the left and right axial directions within the central shaft hole 41 h, the connecting pin 54 is guided and moved together by the long holes 41 s and 41 s of the valve camshaft 41, and is integrated with the connecting pin 54. The variable cam member 50 moves in the axial direction and is displaced.
The connecting pin 54 engages with the thick spline protrusion 50cs of the variable cam member 50 to increase the engagement margin between the connecting pin 54 and the variable cam member 50 without enlarging the variable cam member 50 in the radial direction. Engagement can be ensured.

A female screw is engraved on the inner peripheral surface of the right end of the central shaft hole 41h of the valve camshaft 41, a coil spring 56 is inserted into the central shaft hole 41h from the right, and the flanged bolt 57 is screwed into the female screw. The spring 56 is sandwiched between the central large-diameter portion 53c of the slide rod 53 and the flanged bolt 57 to urge the slide rod 53 to the left, and the left end of the slide rod 53 is moved to the left from the valve operating cam shaft 41. It is protruding.
Thus, the slider mechanism 52 that displaces the variable cam member 50 in the axial direction is configured.

As described above, the slider mechanism 52 is configured in the central shaft hole 41h of the valve camshaft 41, and the stationary cam member 42, the variable cam member 50, the driven cam chain sprocket 36, and the bearing 45 are provided on the outer periphery of the valve camshaft 41. 46 is inserted into the shaft hole of the left and right bearing walls 16L and 16R projecting opposite to the left and right of the camshaft holder 16 with the outer assembly 46 fitted, and the right bearing 46 is inserted into the shaft hole of the right bearing wall 16R. And the left bearing 45 is fitted into the shaft hole of the left bearing wall 16L, and the valve camshaft 41 is rotatably supported by the camshaft holder 16 via bearings 45 and 46, so that the steady cam It rotates with the variable cam member 50 integrally with the member 42 (refer FIG. 4, FIG. 10).
The right bearing 46 is positioned in contact with the stepped portion of the right bearing wall 16R, and the left bearing 45 is positioned on the left side by a stop plate 59 fixed to the left bearing wall 16L by a bolt 58, so that the left bearing 45 is removed. This is prevented (see FIG. 4).

Referring to FIG. 4, when the slide rod 53 urged to the left by the coil spring 56 is pushed to the right against the urging force of the coil spring 56, as shown by the solid line in FIG. The variable cam member 50 is slid to the right via the pin 54 and comes close to the exhaust cam lobe 42e on the left side of the steady cam member 42, and the roller 44er of the exhaust rocker arm 44e straddles both the exhaust cam lobe 42e and the variable cam lobe 50e. Thus, in addition to the normal opening / closing timing of the exhaust valve 34 by the exhaust cam lobe 42e, the exhaust valve 34 is opened / closed by the variable cam lobe 50e.
The opening / closing of the exhaust valve 34 by the variable cam lobe 50e executes EGR (exhaust gas recirculation).

  On the other hand, when the slide rod 53 is moved to the left by the coil spring 56, the variable cam member 50 is slid to the left via the connecting pin 54 as shown by a two-dot chain line in FIG. When the distance is greater than a predetermined distance, the roller 44er of the exhaust rocker arm 44e does not contact the variable cam lobe 50e, but only the exhaust cam lobe 42e, and the exhaust valve 34 opens and closes at the normal exhaust valve timing.

A variable valve timing drive mechanism 60 that projects to the left from the valve camshaft 41 and presses the left end of the slide rod 53 biased to the left by the coil spring 56 to the right to drive the slider mechanism 52 is a driven cam chain sprocket It is provided on the left side of 36 (see FIG. 4).
The variable valve timing drive mechanism 60 includes an electromagnetic solenoid 61 as an actuator and a swing arm 65 that transmits the drive of the electromagnetic solenoid 61 to the slider mechanism 52. The electromagnetic solenoid 61 is fixed above the ceiling wall 20u of the head cover 20. The swing arm 65 is pivotally supported by the cam chain chamber 20c of the head cover 20 so as to be swingable.

The head cover 20 has a substantially rectangular bowl shape with a ceiling wall 20u and a rectangular cylindrical peripheral wall 20s, and the ceiling wall 20u has a position where a recessed portion 20uh protruding downward overlaps the valve camshaft 41 when viewed in the cylinder axial direction. The protrusions 20up and 20up projecting upward on both front and rear sides of the recess 20uh are elongated in the direction of the valve camshaft 41. The ceiling wall 20u is formed in a wavy shape (see FIGS. 3, 4 and 11).
The central portion of the ceiling wall 20u covering the cam chain chamber 20c in the front-rear direction protrudes thickly upward to form a central protruding portion 21, and the protruding boss portion continues to the front and rear sides of the central protruding portion 21. 22 and 22 are formed to project (see FIGS. 4, 5, and 11).

The central protrusion 21 has a central gap 21c with a predetermined width at the center in the front-rear direction from the cam chain chamber 20c side, and a circular hole 21h drilled to the left from the right side surface of the central protrusion 21 is the center. The gap 21c is reached.
An internal thread is engraved on the protruding boss portions 22 and 22 from the right side surface.

A plunger 61p protrudes from a mounting cylindrical portion 62b protruding from one end face of the cylindrical body of the electromagnetic solenoid 61 so as to be able to advance and retract.
From the main body of the electromagnetic solenoid 61, mounting flange portions 62f and 62f extend forward and backward.
The electromagnetic solenoid 61 is attached to the central protrusion 21 from the right side with the plunger 61p on the left side.

At that time, referring to FIG. 11, the mounting cylindrical portion 62 b of the electromagnetic solenoid 61 is fitted into the circular hole 21 h of the central projecting portion 21, and the mounting flange portions 62 f and 62 f extending forward and backward from the main body of the electromagnetic solenoid 61 are provided. The bolts 63 and 63 are brought into contact with the protruding boss portions 22 and 22, pass through the mounting flange portions 62 f and 62 f and are screwed into the female threads of the protruding boss portions 22 and 22, and the electromagnetic solenoid 61 is connected to the ceiling wall 20 u of the head cover 20. Is fixed to the projecting bosses 22 and 22 by being cantilevered above.
Thus, since the electromagnetic solenoid 61 is cantilevered by the protruding boss portions 22 and 22 and the central protruding portion 21, the weight of the head cover 20 including the electromagnetic solenoid 61 can be reduced.

In the electromagnetic solenoid 61 attached in this way, the axial direction in which the plunger 61p moves is parallel to the axial direction in which the valve cam cam 41 and the slide rod 53 in the central shaft hole 41h slide, and the ceiling wall of the head cover 20 The lower part of the cylindrical main body of the electromagnetic solenoid 61 is inserted into the recess (20uh) of 20u.
The head cover 20 has a ceiling wall 20u formed with a concave portion 20uh and convex portions 20up, 20up to increase rigidity, and the electromagnetic solenoid 61 is supported by inserting the lower portion into the concave portion 20uh so that the electromagnetic solenoid 61 protrudes upward. Can be suppressed as much as possible.

The ceiling wall 20u of the head cover 20 is formed so as to extend in the direction in which the valve camshaft 41 faces in a position where the recess (20uh) overlaps the valve camshaft 41 when viewed in the cylinder axis direction, and is formed on both sides of the recess 20uh. Since the convex portions 20up and 20up projecting upward are formed to extend in the direction in which the valve camshaft 41 is directed, as shown in FIG. 3, the convex portions 20up projecting upward from the ceiling wall 20u. , 20up, the head bolt 17 and the rocker arms 44i, 44e are arranged so as not to interfere with each other, and the upward projection of the electromagnetic solenoid 61 can be suppressed.
Note that the plunger 61p of the electromagnetic solenoid 61 supported by being partially inserted into the recess 20uh of the head cover 20 is in a position where the slide rod 53 is translated in the direction of the cylinder axis which is the central axis of the cylinder 14a.

As shown in FIG. 12, a plurality of reinforcing ribs 23r are formed on the inner surface of the head cover 20 below the central protrusion 21, that is, on the left side. The reinforcing ribs 23r extend in parallel to the cylinder axis. ing.
Reinforcing ribs 23r that extend parallel to the cylinder axis, that is, substantially downward, collect the splashed oil from the drive of the valve mechanism (40), cam chain (37), etc. and guide it downward, and return it to the oil reservoir 13p. Make good.

A pair of guide walls 23, 23 are formed symmetrically on the front and rear sides of the central gap 21c formed in the central projecting portion 21, and the guide walls 23, 23 are also reinforcing ribs 23r. .
Referring to the cross-sectional view of FIG. 13, the guide walls 23, 23 have end faces 23a, 23a along the front and rear side faces 21a, 21a facing each other across the central gap 21c, and extend in the front-rear direction and slant in the middle. Bends leftward and expands.

The front and rear side surfaces 21a and 21a constituting the central gap 21c and the end surfaces 23a and 23a of the front and rear guide walls 23 and 23 are the same surface.
Stopper pieces 24, 24 project in a direction approaching each other at predetermined locations on the end faces 23 a, 23 a of the front and rear guide walls 23, 23.
An elastic stopper piece 29 is attached to the center of the lower end of the inner surface of the left peripheral wall facing the front and rear guide walls 23, 23 of the peripheral wall 20s of the head cover 20.
Further, pivot holes 21b and 21b are formed coaxially at predetermined positions on the front and rear side surfaces 21a and 21a constituting the central gap 21c.

  On the other hand, as shown in FIG. 9, the swing arm 65 is a straight bar-shaped arm having a U-shaped cross section in which long and parallel side plate portions 65b and 65b facing each other are connected by a long connecting plate portion 65a. It is a member and is arranged in the cam chain chamber 20c of the head cover 20 so as to be oriented substantially parallel (substantially in the vertical direction) to the cylinder axis direction. The side plate portions 65b and 65b oriented in the substantially vertical direction are arranged from the center. The shaft support holes 65bh and 65bh are coaxially arranged at a position offset to the upper part, and are respectively tapered in the vertical direction from the portions of the shaft support holes 65bh and 65bh.

  The swing arm 65 is disposed along the left surface of the driven cam chain sprocket 36 in the cam chain chamber 20c with the connecting plate portion 65a directed to the right and the opening directed to the left. However, in this case, the substantially upper half of the swing arm 65 is inserted into the central gap 21c of the central protrusion 21, and the pivot holes 65bh and 65bh are pivot holes 21b formed in the front and rear side surfaces 21a and 21a of the central gap 21c. , 21b, and the pivot bolt 64 screwed into the pivot hole 21b from the front projecting boss portion 22 passes through the pivot support holes 65bh, 65bh of the swing arm 65 and the pivot shaft of the rear projecting boss portion 22 The swing arm 65 is pivotally supported by the pivot bolt 64 so as to swing freely.

The swing arm 65 swings so that the upper half portion is sandwiched between the front and rear side surfaces 21a and 21a constituting the central gap 21c, and the lower half portion is the front and rear guide walls 23 and 23 that are flush with the front and rear side surfaces 21a and 21a. It is guided so as to be sandwiched between the end faces 23a, 23a, and smoothly swings without causing a torsion in the torsional direction.
Referring to FIG. 4, the slide rod 53 that slides in the central shaft hole 41 h of the valve camshaft 41 is substantially the same as the mating surface S of the head cover 20 and the cylinder head 15 (the lower surface of the elastic seal member 18). They are on the same plane, and the lower end of the swing arm 65 slightly protrudes below the mating surface S of the head cover 20 and the cylinder head 15.

The lower ends of the pair of front and rear guide walls 23, 23 extending downward from the central projecting portion 21 are located slightly above the slide rod 53, and the stopper piece 24 is slightly above the lower ends of the guide walls 23, 23. 24 protrude from the end faces 23a, 23a in a direction approaching each other.
The swing arm 65 pivotally supported by the pivot bolt 64 swings while being guided such that the lower half portion is sandwiched between the end faces 23a and 23a of the front and rear guide walls 23 and 23, as shown by a solid line in FIG. In this manner, the swinging is restricted by coming into contact with the stopper pieces 24, 24 from the left side.
Further, the swing arm 65 has its lower part abutting from the right side on the elastic stopper part 29 attached to the inner surface of the peripheral wall 20s of the head cover 20, and the swinging of the swing arm 65 is restricted. , 24 and the elastic stopper piece 29 are swingable.

The guide walls 23, 23 that extend in the front-rear direction have a lower end located slightly above the slide rod 53 and cover the left side of the upper half of the driven cam chain sprocket 36. The head of the screw 48 fixed to the flange member 47 of the camshaft 41 is covered nearby, so that the movement of the screw 48 in the removal direction is restricted, and the screw 48 can be prevented from falling off.
A member for retaining the screw 48 is not required separately, and the number of parts can be reduced and the weight can be reduced.

  Since the swing arm 65 is pivotally supported by a pivot bolt 64 at a position offset from the center to the top, the lower portion is longer than the upper portion of the pivot bolt 64. As shown in FIG. The pivot bolt 64 serving as the fulcrum P of the moving arm 65 is positioned above the driven cam chain sprocket 36 fixed to the valve camshaft 41, and the head cover is attached to the connecting plate portion 65a at the upper end of the pivot bolt 64. The plunger 61p protruding leftward from the mounting cylindrical portion 62b of the electromagnetic solenoid 61 fixed above the ceiling wall 20u of the 20 is in contact with the valve driving camshaft 41 on the connecting plate portion 65a at the lower end of the pivot bolt 64. The slide rod 53 that protrudes further to the left and is biased by the coil spring 56 comes into contact.

Referring to FIG. 4, the straight bar-like swing arm 65 has a force point Q at the upper point where the plunger 61p of the electromagnetic solenoid 61 abuts, where the swing center of the swing arm 65 by the pivot bolt 64 is the fulcrum P. Yes, the lower end point that contacts the slide rod 53 is the action point R, and the swing arm 65 receives the plunger 61p protruding leftward by the excitation drive of the electromagnetic solenoid 61 at the upper end force point Q, and swings to the lower end. The point of action R acts on the slide rod 53 and slides the slide rod 53 to the right against the urging force of the coil spring 56.
When the electromagnetic solenoid 61 is demagnetized, the slide rod 53 slides to the left by the urging force of the coil spring 56, swings the swing arm 65, and the plunger 61p is pushed to the right.

  That is, when the electromagnetic solenoid 61 is demagnetized, the slide rod 53 slides to the left by the urging force of the coil spring 56, and the variable cam is connected via the connecting pin 54 as shown by a two-dot chain line in FIG. The member 50 slides to the left and moves away from the steady cam member 42, and the exhaust valve 34 opens and closes at normal exhaust valve timing.

  When the electromagnetic solenoid 61 is excited, the plunger 61p protrudes to the left and swings until the swing arm 65 comes into contact with the stopper pieces 24 and 24, and the slide rod 53 is resisted against the biasing force of the coil spring 56. As shown by a solid line in FIG. 4, the variable cam member 50 slides and displaces to the right via the connecting pin 54 and comes close to the exhaust cam lobe 42 e on the left side of the steady cam member 42. Apart from the normal opening / closing timing of the exhaust valve 34 by the cam lobe 42e, the exhaust valve 34 is opened / closed by the variable cam lobe 50e.

The opening / closing timing of the exhaust valve 34 different from the normal exhaust timing is executed at a predetermined timing overlapping the opening timing of the intake valve 33, and the exhaust gas remaining in the exhaust passage by the opening of the exhaust valve 34 is removed from the combustion chamber. It is possible to realize so-called EGR (exhaust gas recirculation) for returning to 15z and for combustion.
That is, the EGR device is configured by the variable valve timing drive mechanism 60, the slider mechanism 52, and the variable cam member 50, and this EGR device is configured with a simple structure without requiring a special dedicated EGR valve or EGR port. be able to.

  In the slider mechanism 52, a slide rod 53 on which the operating point R of the swing arm 65 acts is slidably fitted into the central shaft hole 41h of the valve operating cam shaft 41, and the slide rod 53 can be slid into a variable cam member. Since the connecting pin 54 that transmits to 50 passes through the slide rod 53 and engages the variable cam member 50, the slider mechanism 52 is accommodated in the valve operating cam shaft 41, and the size can be reduced.

In the swing arm 65, the distance PR from the fulcrum P to the action point R is longer than the distance PQ from the fulcrum P to the force point Q, and the lever ratio r (= PR /) is the ratio of the distance PR to the distance PQ as a lever. PQ) is large.
The swing arm 65 is disposed such that its longitudinal direction is substantially parallel to the cylinder axis direction (substantially in the vertical direction), and the fulcrum P of the swing arm 65 is fixed to the valve camshaft 41. Since it is positioned above the sprocket 36, the swing arm 65 can be compactly incorporated into the valve operating apparatus while the lever ratio r is increased.

The swing arm 65 having a large lever ratio r is guided such that the long lower side portion extending downward from the fulcrum P is sandwiched between the end surfaces 23a and 23a of the front and rear guide walls 23 and 23, and is twisted. Prevents falling and swings smoothly.
The swing arm 65 has a straight bar shape, and the force point Q, the fulcrum P, and the action point R are linearly arranged in order from top to bottom. Therefore, the swing arm 65 is placed in a narrow space in the cam chain chamber 20c. It is easy to incorporate, and it is possible to prevent the swing arm 65 from being applied with a twisting force while reducing the weight of the swing arm 65.
Further, since the swing arm 65 has a U-shaped cross section, the swing arm 65 is lightened and the rigidity is ensured to prevent the swing arm 65 from being bent.

Therefore, the swing arm 65 that receives the operation of the electromagnetic solenoid 61 at the force point Q always moves the operating point R accurately and transmits it to the slider mechanism 52 to displace the variable cam member 50, thereby smoothly changing the valve timing. Can be executed with high accuracy.
Therefore, EGR (exhaust gas recirculation) can be executed efficiently.

  Since the head cover 20 is reinforced by reinforcing ribs 23r formed on the inner surface of the head cover 20 particularly below the central protruding portion 21, the central protruding portion 21 and the protruding boss portion 22, which cantilever-support the electromagnetic solenoid 61, Since the reinforcement and rigidity of 22 are ensured, the drive of the plunger 61p of the electromagnetic solenoid 61 fixed to the protruding boss portions 22 and 22 is accurately transmitted to the slider mechanism 52, and the valve timing is changed accurately. Can contribute.

Since the lever ratio of the swing arm 65 is large, the drive amount of the plunger 61p of the electromagnetic solenoid 61 may be small to move the slide rod 53 and the variable cam member 50 of the slider mechanism 52 by the required amount, and the small drive amount is small. The actuator can be used.
Since the head cover 20 supports the swing shaft 64 and integrally forms the pair of guide walls 23, 23, a simple structure with a reduced number of parts can be achieved.

The head cover 20 having a generally rectangular bowl shape is formed with mounting bosses 20b and 20b for attaching the head cover 20 to the cylinder head 15 with flanged bolts 70 so as to be offset from each other on the front and rear of the ceiling wall 20u (FIG. 11). 12), on the back surface of the head cover 20, as shown in FIG. 12, a groove 20v into which the elastic seal member 18 is fitted is formed on the end surface (mating surface) of the peripheral wall 20s, and on the back surface of the ceiling wall 20u. Are formed with three convenient knock holes 20n, 20n, 20n on the front side and two on the rear side.
On the upper surface of the cylinder head 15, as shown in FIG. 10, mounting bolt holes 15b, 15b and knock holes 15n, 15n corresponding to the mounting boss portions 20b, 20b and knock holes 20n, 20n, 20n of the head cover 20 are provided. 15n is formed.

Further, the head cover 20 is formed with a protrusion 25 having an oil passage 26 therein, which extends in a straight line slightly diagonally in the front-rear direction at a position slightly to the right on the back surface of the ceiling wall 20u.
The rear end of the ridge 25 reaches the peripheral wall 20s, the oil passage 26 has a front end reaching the center of the front half of the ceiling wall 20u, and injection holes 27 communicating with the oil passage 26 at four predetermined locations of the ridge 25 are provided. It is drilled downward.

As shown in FIG. 10, a head cover in which an elastic seal member 18 is fitted into a groove 20v on an end surface of a peripheral wall 20s in a cylinder head 15 in which a cylindrical knock member 72 is fitted in knock holes 15n, 15n, 15n on the upper surface. At that time, the head cover 20 is positioned and overlapped so that the knock member 72 fits into the knock holes 20n, 20n, 20n of the head cover 20 (see FIG. 12), and the mounting bolt holes 15b are coaxial. The head cover 20 is mounted on the cylinder head 15 by passing the flanged bolt 70 through the mounting boss portion 20b and tightening it through the elastic member 71 (see FIG. 3).
Therefore, the head cover 20 is elastically supported by the cylinder head 15 via the elastic seal member 18 and the elastic member 71.

  Since the head cover 20 is elastically supported by the cylinder head 15 and the shift in the direction perpendicular to the cylinder axis is restricted by the knock member 72, the head cover 20 may affect the swing of the swing arm 65 pivotally supported on the head cover 20 side. The vibration on the internal combustion engine body side is absorbed by the elastic support and transmitted to the head cover 20, and the operation of the variable valve timing drive mechanism 60 by the swing arm 65 on the head cover 20 side is suppressed to reduce the influence of the engine vibration and perform accurate operation. The valve timing can be accurately changed with guarantee.

  Further, since the displacement of the relative positional relationship between the swing arm 65 and the slide rod 53 in contact with the swing arm 65 can be prevented by the displacement restriction by the knock member 72, the swing of the swing arm 65 can be shifted to the slide rod 53. Therefore, the sliding displacement of the variable cam member 50 by driving the electromagnetic solenoid 61 can always be performed accurately, and the execution timing of EGR can be executed with high accuracy.

A knock hole 15n adjacent to the oil passage 26 on the rear side of the cylinder head 15 communicates with an oil supply path extending from the cylinder block 14 side, and as shown in FIG. Since 20n also communicates with the oil passage 26 via the oil supply passage 28, the cylinder knock member 72 causes the oil supply passage 15a on the cylinder head 15 side to communicate with the oil passage 26 of the head cover 20 so that the oil is oil. It is supplied to the passage 26.
The knock member 72 also serves as a seal for the oil connecting portion.

  As shown by the phantom line (two-dot chain line) in FIG. 10, the oil passage 26 extends obliquely in the front-rear direction above the intake rocker arm 44i and the exhaust rocker arm 44e, and from four injection holes 27 drilled in the middle thereof. The injected oil is sprayed on the intake rocker arm 44i and the exhaust rocker arm 44e and used for lubricating the valve operating mechanism 40.

When the head cover 20 is mounted on the cylinder head 15, the head cover 20 is mounted in a small assembly state in which the swing arm 65 of the variable valve timing drive mechanism 60 is incorporated in the cylinder head 15.
That is, in the cylinder head 15, the swing arm 65 pivotally supported by the central protrusion 21 via the pivot bolt 64 swings between the stopper pieces 24 and 24 and the elastic stopper piece 29 in the cam chain chamber 20c. It is arranged freely.
The lower end of the swinging arm 65 that swings slightly protrudes downward from the mating surface S of the head cover 20 and the cylinder head 15 (the lower surface of the elastic seal member 18) and can be seen from the side.

  When the head cover 20 is put on the cylinder head 15 from above, the lower part of the swing arm 65 is in contact with the elastic stopper piece 29 so as to swing most to the left side. The head cover 20 is moved to the cylinder head 15 while avoiding the slide rod 53 on the left side so that the lower end of the swing arm 65 does not come into contact with the slide rod 53 that is biased to the left and protrudes to the left from the valve camshaft 41. Attach to.

When attaching the head cover 20, the lower end of the swing arm 65 protruding downward from the head cover 20 can be seen from the side, so that the lower end of the swing arm 65 does not contact the left end of the slide rod 53 from above. The head cover 20 can be easily put on the cylinder head 15 while being visually recognized from the side.
Therefore, it is possible to prevent the lower end of the swing arm 65 from being accidentally brought into contact with the left end of the slide rod 53 from above and causing problems such as breakage.
When the head cover 20 is normally attached to the cylinder head 15, the lower end of the swing arm 65 faces the left end surface of the slide rod 53.

  Thus, in a state where the swing arm 65 is assembled to the head cover 20, the lower end of the swing arm 65 whose swing is restricted by the stopper piece 24 protrudes downward from the head cover 20. When covering the head cover 20 from above, make sure that the lower end of the swing arm 65 does not come into contact with the slide rod 53 protruding leftward from the valve camshaft 41 provided on the cylinder head 15 side. It can be easily assembled while confirming the position of the lower end of the swing arm 65 from the side, and the assemblability is good.

Thereafter, the electromagnetic solenoid 61 is attached to the central projecting portion 21 of the head cover 20 from the right side above the ceiling wall 20u of the head cover 20.
When the mounting cylindrical portion 62b of the electromagnetic solenoid 61 is inserted into the circular hole 21h of the central projecting portion 21, the plunger 61p retracted in the demagnetized state of the electromagnetic solenoid 61 abuts against the upper end of the swing arm 65 to push and swing. The lower end of the swing arm 65 is in a state indicated by a two-dot chain line in FIG. 4 which is in contact with the left end of the slide rod 53 biased by the coil spring 56 and slightly pressed.
That is, the swing arm 65 is in a state where the lower end is urged by the coil spring 56 via the slide rod 53, and does not swing freely.

  Therefore, even if the plunger 61p is advanced and retracted by driving the electromagnetic solenoid 61, the plunger 61p and the upper end of the swing arm 65 are always kept in contact with each other, and the lower end of the swing arm 65 and the slide rod 53 are always in contact with each other. Since power is transmitted to the slide rod 53 in a state where is maintained, no sound is generated due to collision, and noise can be prevented.

When the head cover 20 is attached to the cylinder head 15 by screwing the flanged bolt 70, the left end of the slide rod 53 urged to the left by the coil spring 56 abuts against and presses the lower end of the swing arm 65, and swings. The upper end of the moving arm 65 is in contact with the left end of the plunger 61p with the electromagnetic solenoid 61 retracted (see the two-dot chain line in FIG. 4).
At this time, as shown by a two-dot chain line in FIG. 4, the slide rod 53 slides to the left, displaces the variable cam member 50 to the left via the connecting pin 54, and leaves the steady cam member 42 to exhaust. The roller 44er of the rocker arm 44e contacts only the exhaust cam lobe 42e, and the exhaust valve 34 opens and closes at normal exhaust valve timing.

  When the electromagnetic solenoid 61 is driven and the plunger 61p protrudes to the left, the swing arm 65 swings by receiving the force at the upper end force point Q as shown by the solid line in FIG. The slide rod 53 is pushed to the right against the urging force of the coil spring 56, and the variable cam member 50 is slid to the right via the connecting pin 54 and close to the exhaust cam lobe 42e on the left side of the steady cam member 42. The roller 44er of the exhaust rocker arm 44e is in contact with both the exhaust cam lobe 42e and the variable cam lobe 50e so that the exhaust valve 34 of the variable cam lobe 50e is separated from the normal opening / closing timing of the exhaust valve 34 by the exhaust cam lobe 42e. By opening and closing, EGR (exhaust gas recirculation) is executed.

  When the electromagnetic solenoid 61 is driven, the swing of the swing arm 65 is restricted by contacting the stopper piece 24, so that the slide of the variable cam member 50 together with the slide rod 53 to the right is also performed at a predetermined position. Therefore, the variable cam member 50 stops at a close position slightly away from the steady cam member 42.

  To change the valve timing by sliding the slide rod 53 of the slider mechanism 52 linearly, an electromagnetic solenoid 61 that linearly moves the plunger 61p is used as an actuator, so that power transmission to the slider mechanism 52 is achieved. This can be easily achieved by the swing arm 65, and the number of parts can be reduced and the structure can be simplified.

  The oil sprayed from the injection hole 27 of the lubricating oil passage 26 formed in the ceiling wall 20u of the head cover 20 to the valve mechanism 40 is splined to the valve camshaft 41 on which the variable cam member 50 slides. Since the joint portion is also lubricated, oil enters the gap between the variable cam member 50 and the steady cam member 42, but the variable cam member 50 is not in contact with the steady cam member 42 but is in the gap. have.

  When the variable cam member 50 is in contact with the steady cam member 42, the variable cam member 50 sticks to the steady cam member 42 due to oil viscosity, and the variable cam member 50 is released from the steady cam member 42 to release the EGR. However, there is a problem that the movement of the variable cam member 50 is delayed, but the swinging arm 65 abuts against the stopper piece 24 to restrict the swinging, so that the variable cam member 50 has a gap in the steady cam member 42. Therefore, there is no such problem, and the accuracy of the execution timing of EGR can be maintained well.

  In addition to restricting the swing of the swing arm 65 by the stopper piece 24, the variable cam member 50 is stopped in proximity to the steady cam member 42, and the connecting pin 54 integrated with the slide rod 53 is connected to the valve camshaft. By contacting the long end of the long hole 41s formed in 41, the sliding of the variable cam member 50 is restricted, and the variable cam member 50 is close to the steady cam member 42 with a gap. Good.

Furthermore, only the peripheral edge portion of the shaft hole of the right end surface of the cylindrical variable cam member 50 facing the steady cam member 42 is slightly protruded in the axial direction, and the protruding peripheral edge portion of the shaft hole contacts the steady cam member 42. The movement of the variable cam member 50 may be regulated in contact therewith.
In this case, when the variable cam lobe 50e comes into contact with the steady cam member 42, only the peripheral edge portion of the shaft hole comes into contact with the steady cam member 42 to reduce the contact area, and the variable cam member 50 is stuck to the steady cam member 42 due to oil viscosity. The sticking is weak, and when the variable cam member 50 moves away from the steady cam member 42 and releases the EGR, there is no problem that the movement of the variable cam member 50 is delayed.

The oil sprayed from the injection hole 27 of the oil passage 26 in the ceiling wall 20u of the head cover 20 to the valve mechanism 40 and the oil swept up by the cam chain 37 are caused by the rocker arms 44i and 44e as the valve cam shaft 41 rotates. The driven cam chain sprocket 36 of the guide walls 23 and 23 that guides the swing arm 65 from both sides by being swung up and scattered by the swing and rotation of the driven cam chain sprocket 36 and the rotation of the cam chain 37. It also adheres to the right wall surface on the side and the outer plate surface (right plate surface) of the connecting plate portion 65 a of the swing arm 65 and flows down along the right wall surface of the guide walls 23, 23 and the right plate surface of the swing arm 65.
This oil also enters the gap between the swinging portion of the swinging arm 65 and the guide walls 23, 23, so that the swinging of the swinging arm 65 is smooth.

  As shown in FIGS. 4 and 5, the guide walls 23, 23 have a lower end on the swing arm 65 side, the lower end thereof is above the slide rod 53, and the axial direction in which the operating point R of the swing arm 65 moves. The oil flowing down the right wall surface of the guide walls 23, 23 is guided toward the swing arm 65 along the lower ends of the guide walls 23, 23 and crosses the gap between them to the swing arm 65. Since the oil has flowed down along the swing arm 65 and reaches the lower end of the lower swing arm 65, it is supplied to the operating point R of the swing arm 65, that is, the contact portion of the slide rod 53, Wear of the pressing action point of the swing arm 65 can be prevented.

  As shown in the plan view of the saddle type motorcycle 1 in FIG. 16, the electromagnetic solenoid 61 supported by the head cover 20 overlaps with the vehicle width direction center line CC ′ of the saddle type vehicle in a top view. Therefore, the upper part of the electromagnetic solenoid 61 is completely covered by the fuel tank 6 supported at the center of the vehicle body width direction so as to straddle the main frame 2m of the vehicle body frame 2 from above.

Accordingly, the electromagnetic solenoid 61 is sandwiched between the head cover 20 and the fuel tank 6, and the operation sound of the electromagnetic solenoid 61 can be blocked by the fuel tank 6 and can be made difficult to be transmitted to the occupant. 61 is protected and does not require a shielding member specifically for the electromagnetic solenoid.
Furthermore, the weight balance of the vehicle body can be maintained by arranging the electromagnetic solenoid 61, which is a relatively heavy object, at a position overlapping the vehicle width direction center line CC 'in a top view.

10 ... Internal combustion engine, 11 ... Crankshaft, 15 ... Cylinder head,
20 ... Head cover, 20u ... Ceiling wall, 20uh ... Recess, 20up ... Projection, 21 ... Center protrusion, 21c ... Center gap, 22 ... Projection boss, 23r ... Reinforcement rib, 23 ... Guide wall, 23a ... End face, 24 ... stopper piece, 25 ... projection, 26 ... oil passage, 27 ... injection hole,
40 ... Valve drive mechanism, 41 ... Valve drive cam shaft, 41s ... Long hole, 42 ... Steady cam member, 42i ... Intake cam lobe, 42e ... Exhaust cam lobe, 44i ... Intake rocker arm, 44e ... Exhaust rocker arm, 43ir, 44er ... Roller, 47… Flange member, 48… Screw,
50 ... Variable cam member, 52 ... Slider mechanism, 53 ... Slide rod, 54 ... Connecting pin, 56 ... Coil spring, 57 ... Bolt with flange,
60 ... Variable valve timing drive mechanism, 61 ... Electromagnetic solenoid, 64 ... Pivot bolt, 65 ... Oscillating arm,
72 ... Knock member.

Claims (9)

A valve camshaft (41) rotatably supported by a cylinder head (15) of an internal combustion engine mounted on the saddle riding type vehicle and covered by a head cover (20), and an outer periphery of the valve camshaft (41) A variable cam member (50) that is fitted so as not to be relatively rotatable and is slidably displaced in the axial direction to vary the valve timing, and a slide rod (53 ) that slides and displaces the variable cam member (50) in the axial direction. ) And a variable valve timing drive mechanism (60) that changes the valve timing by transmitting the drive of the actuator (61) to the slide rod (53) of the slider mechanism (52). In a variable valve timing valve operating system for an onboard internal combustion engine,
An internal combustion engine (10) is suspended on the body frame of the saddle riding type vehicle with the cylinder slightly tilted forward,
Wherein said head cover (20) in the bottom plate of the fuel tank is supported so as to extend from above the vehicle body frame (6) covers the internal combustion engine (10) from above the fuel tank (6) is adapted faces,
The actuator (61) is supported on the ceiling wall (20u ) of the head cover (20), and the actuator (61) has an axial direction of a plunger (61p) provided on the valve camshaft (41). Parallel to the axial direction of the slide rod (53) and the axial direction in which the slide rod (53) slides,
The actuator (61) is disposed at a position where the upper part is covered by the fuel tank (6) and overlaps the valve camshaft (41) as viewed in the cylinder axial direction .
The variable valve timing drive mechanism (60) is pivotally supported by a fulcrum (P), one end receives the action of the plunger (61p), and the other end acts on the slide of the plunger (61p). It has a swing arm (65) that transmits to the rod (53),
Said slide rod and an actuator (61) (53), variable valve timing valve gear of the relative oscillating arm (65) is arranged on the same side an internal combustion engine according to claim Rukoto. The variable valve timing drive mechanism (60)
Said fulcrum the rocking arm that is swingably supported by the (P) (65), the operation of the actuator (61) to the force point the slider mechanism in receiving the point (R) (Q) (52) A transmission mechanism,
The head cover (20) that supports the actuator (61),
2. The cylinder head according to claim 1, wherein the cylinder head is positioned by at least two knock members and is overlapped on a mating surface perpendicular to the cylinder axis via a seal member. The variable valve timing valve operating device for the on-vehicle internal combustion engine. The swing arm (65) is pivotally supported by a swing shaft (64) serving as a fulcrum (P) on the head cover (20),
The in-vehicle system according to claim 2, wherein the head cover (20) is elastically supported by the seal member (18) interposed between the cylinder head (15) and the mating surface. A variable valve timing valve operating apparatus for an internal combustion engine. A part of the ceiling wall (20u) of the head cover (20) protrudes upward to form protrusions (21, 22),
4. The variable valve timing valve operating system for an on-vehicle internal combustion engine according to claim 1, wherein the actuator (61) is cantilevered by the projecting portions (21, 22). .   The variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to claim 4, wherein the head cover (20) is formed with a reinforcing rib (23r) extending in parallel with a cylinder axis on the inner surface. The ceiling wall (20u) of the head cover (20) has a recessed portion (20uh) recessed downward,
The in-vehicle internal combustion engine according to claim 4 or 5, wherein the actuator (61) is cantilevered by the protrusions (21, 22) by inserting a lower portion into the recess (20uh). Variable valve timing valve. Wherein the ceiling wall of the head cover (20) (20u) is,
The recess (20uh) is formed to extend in a direction in which the valve camshaft (41) is directed at a position overlapping the valve camshaft (41) when viewed in the cylinder axis direction,
The convex part (20up) which protruded upwards on both sides of the concave part (20uh) is formed to extend in a direction in which the valve camshaft (41) is directed. A variable valve timing valve operating device for an on-vehicle internal combustion engine. The actuator (61) supported by the head cover (20),
The variable valve timing valve operating apparatus for an on-vehicle internal combustion engine according to any one of claims 1 to 7, wherein the variable valve timing valve operating apparatus is disposed at a position overlapping a center line in a vehicle body width direction of the saddle riding type vehicle in a top view. The actuator (61) supported by the head cover (20),
The main body case is an electromagnetic solenoid having a cylindrical shape parallel to the valve camshaft (41) and having a drive shaft that advances and retreats in a direction in which the valve camshaft (41) is directed. The variable valve timing valve operating device for an on-vehicle internal combustion engine according to claim 8.

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