JP2014185585A - Variable valve gear of ohc-type internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a variable valve gear of an OHC-type internal combustion engine in which a pressing force generating source is arranged in a position that is not away from an ignition plug and does not interfere with removal and installation operation of the ignition plug, and in which good maintainability of the ignition plug is achieved while a cylinder head can be downsizing.SOLUTION: In a variable valve gear of an OHC-type internal combustion engine, a pressing force generating source (75) is attached on a wall surface (100L) where an ignition plug (49) of a cylinder head (33) projects, and housing cases (77 and 78) for housing a body of the pressing force generating source (75) are provided in a position where an ignition plug central axis (Cs) oriented by the ignition plug (49) does not overlap with them in a cylinder axis direction view.

Description

  The present invention relates to a variable valve operating apparatus in an OHC type internal combustion engine.

  In an OHC type internal combustion engine in which a valve mechanism such as a camshaft is configured on a cylinder head, a rocker arm that transmits the rotation of the camshaft to the valve opening / closing motion of the engine valve is provided adjacent to and moves in both adjacent rocker arms. A variable valve capable of changing valve timing by providing a connecting pin movably between a connecting position where both rocker arms are integrally connected so as to be swingable and a connection releasing position where the rocker arms are swingable independently of each other. The device is already known.

  A variable valve that uses a solenoid as a pressing force source to move the connecting pin, and moves the connecting pin via a transmission rod (pressing force transmitting member) in which the solenoid operating portion is slidably supported by the cylinder head. Regarding the device, there is an example related to a prior application of the same applicant (see Patent Document 1).

JP 2012-77741 A

In the OHC type internal combustion engine disclosed in Patent Document 1, a spark plug projects from a wall surface to which a solenoid of a cylinder head is attached.
Since the spark plug is mounted on the same wall so as to be inserted obliquely from the head cover side, during the maintenance of the spark plug, the spark plug is moved in the axial direction of the mounted spark plug to be attached and detached.

  In Patent Document 1, the solenoid is located at a position closer to the head cover side than the spark plug, and as shown in FIG. 2 of Patent Document 1, the axis directed by the spark plug overlaps the solenoid when viewed in the cylinder axial direction. In order to move the spark plug in the axial direction of the spark plug and attach / detach the spark plug, the solenoid becomes an obstacle, and the maintenance work is not easy.

  In particular, in an OHC type internal combustion engine mounted on a saddle-ride type vehicle in which it is difficult to secure the length of the cylinder head in the cylinder axis direction, the spark plug and the solenoid are easy to approach, and it is difficult to secure a maintenance space around the spark plug. .

  The present invention has been made in view of the above points, and the object of the present invention is to prevent the ignition plug from being attached or detached without keeping the pressing force generation source attached to the same wall surface as the ignition plug of the cylinder head away from the ignition plug. The variable valve operating apparatus for the OHC type internal combustion engine can be provided at a position where it does not become necessary, and the maintainability of the spark plug can be satisfactorily maintained while reducing the size of the cylinder head.

In order to achieve the above object, the invention according to claim 1
A cylinder block (32) and a cylinder head (33) are sequentially stacked on the crankcase (31) and fastened by a plurality of stud bolts (180) penetrating in the cylinder axial direction. The engine valve is placed inside the cylinder head (33). A plurality of rocker arms (57, 58) interlocking with (61, 62) are arranged so as to be swingably supported by a rocker arm shaft (55) adjacent to each other, and a head cover is mounted on the cylinder head (33). (34) is an OHC type internal combustion engine configured to be covered,
A connecting pin (71) that fits movably in the axial direction of the rocker arm shaft (55) in the adjacent rocker arm (57, 58) can swing the adjacent rocker arm (57, 58) integrally. It is provided so as to be movable between a coupling position to be coupled and a coupling release position that can swing independently of each other,
An OHC internal combustion engine provided with a pressing force transmission member (74, 76) for transmitting a pressing force of a pressing force generation source (75) disposed outside the cylinder head (33) to the movement of the connecting pin (71). In the variable valve system of the engine,
The pressing force source (75) is attached to the wall surface (100L) on which the ignition plug (49) of the cylinder head (33) is projected,
A housing case (77, 78) for housing the main body of the pressing force generation source (75) is provided at a position that does not overlap with the spark plug center axis (Cs) directed to the spark plug (49) when viewed in the cylinder axial direction. This is a variable valve operating apparatus for an OHC type internal combustion engine.

The invention according to claim 2 is the variable valve operating apparatus for the OHC type internal combustion engine according to claim 1,
The pressing force generation source (75) is located closer to the head cover (34) than the spark plug (49).

The invention according to claim 3 is the variable valve operating apparatus for the OHC type internal combustion engine according to claim 2,
The pressing force transmission member (74, 76) is slidably provided on the cylinder head (33).

The invention according to claim 4 is the variable valve operating apparatus for the OHC type internal combustion engine according to claim 3,
The pressing force generation source (75) has a plurality of mounting arm portions (77pr, 77qr, 77rr) radially around the housing case (77, 78) along the wall surface (100L) of the cylinder head (33). Extended and formed
The plurality of attachment arm portions (77pr, 77qr, 77rr) are attached only to the cylinder head (33).

The invention according to claim 5 is the variable valve operating apparatus for the OHC type internal combustion engine according to claim 4,
Of the plurality of mounting arm portions (77pr, 77qr, 77rr), the mounting arm portion (77pr) extending in a direction overlapping the spark plug central axis (Cs) when viewed in the cylinder axial direction is the spark plug central axis ( A concave portion (77d) that opens toward the spark plug (49) side is formed so as to straddle while avoiding Cs).

The invention according to claim 6 is the variable valve operating apparatus for the OHC type internal combustion engine according to claim 4 or 5,
The cylinder head (33) is the same as the rib portion (103pr, 103qr, 103rr) with which the mounting arm portion (77pr, 77qr, 77rr) extending around the housing case (77, 78) is brought into contact. The mounting boss part (103p, 103q, 103r) at the end of the rib part (103pr, 103qr, 103rr) is formed to project, and the mounting arm part (77pr, 77qr, 77rr) is formed on the mounting boss part (103p, 103q, 103r). ) Is attached.

The invention according to claim 7 is the variable valve operating apparatus for an OHC type internal combustion engine according to any one of claims 4 to 6,
The housing case (77, 78) and the attachment arm (77pr, 77qr, 77rr) in the pressing force generation source (75) are made of metal.

The invention according to claim 8 is the variable valve operating apparatus for an OHC type internal combustion engine according to any one of claims 4 to 6,
An oil passage (133) is formed in the vicinity of the pressing force generation source (75) on the side wall (100L) to which the pressing force generation source (75) of the cylinder head (33) is attached. .

The invention according to claim 9 is the variable valve operating apparatus for an OHC type internal combustion engine according to any one of claims 1 to 8,
The OHC type internal combustion engine (30) is mounted on the body frame of the saddle-ride type vehicle (1) in a posture in which the cylinder axis (Cc) is largely inclined to near horizontal.
The pressing force generation source (75) is attached to the side wall surface (100L) facing the vehicle width direction of the cylinder head (33),
The outer side in the vehicle width direction of the pressing force generation source (75) is covered with a part (6) of the vehicle body frame.

The invention according to claim 10 is the variable valve operating apparatus for the OHC type internal combustion engine according to claim 9,
The water pump (150) is attached to the side wall surface (100R) opposite to the side wall surface (100L) to which the pressing force generation source (75) of the cylinder head (33) is attached.

The invention according to claim 11 is the variable valve operating apparatus for the OHC type internal combustion engine according to claim 10,
The water pump (150) is disposed closer to the crankcase than the pressing force generation source (75) in the cylinder axial direction,
The head cover (34) is provided with a breather chamber (34b) inside,
The outlet portion (34c) of the breather chamber (34b) is formed on the outer wall surface of the head cover (34) with the opening facing the water pump (150) in the vehicle width direction. To do.

  According to the variable valve operating apparatus for the OHC type internal combustion engine according to claim 1, the pressing force generating source (75) is attached to the wall surface (100L) on which the ignition plug (49) of the cylinder head (33) is projected, Since the housing case (77, 78) that houses the main body of the pressing force generation source (75) is provided at a position that does not overlap with the spark plug center axis (Cs) directed by the spark plug (49) in the cylinder axial direction view, When the pressure source (75) is not moved away from the spark plug (49), and the spark plug (49) is moved in the axial direction of the spark plug center axis (Cs) pointed to by the spark plug (49) to be attached or detached Thus, the pressing force generation source (75) can be arranged at a position that does not hinder the maintenance of the spark plug (49) while maintaining the downsizing of the cylinder head (33).

  According to the variable valve operating apparatus for the OHC type internal combustion engine according to claim 2, the pressing force generation source (75) is located closer to the head cover (34) than the ignition plug (49). Maintenance space can be easily secured.

According to the variable valve operating apparatus for the OHC type internal combustion engine according to the third aspect, since the pressing force transmission member (74, 76) is slidably provided on the cylinder head (33), the pressing force transmission member (74, 76) is provided. ) Can be prevented from bulging out toward the head cover (34) and the cylinder head (33) can be prevented from being enlarged in the axial direction of the cylinder.
Therefore, it can be made suitable for a saddle-ride type vehicle that is particularly required to be downsized around the cylinder head (33).

  According to the variable valve operating apparatus for the OHC type internal combustion engine according to claim 4, the pressing force generation source (75) is arranged around the housing case (77, 78) along the wall surface (100L) of the cylinder head (33). Since a plurality of mounting arm portions (77pr, 77qr, 77rr) are radially formed and the plurality of mounting arm portions (77pr, 77qr, 77rr) are attached only to the cylinder head (33), the cylinder head (33) The rigidity can be increased and the bulge of the pressing force generation source (75) toward the head cover (34) can be further suppressed.

  Further, since the pressing force source (75) is attached only to the cylinder head (33) and not to the head cover (34), the pressing force source (75) is used for maintenance of the valve train in the cylinder head (33). The head cover (34) can be removed without removing 75), and the maintenance work of the valve train can be facilitated.

  According to the variable valve operating apparatus for the OHC type internal combustion engine according to claim 5, the plurality of mounting arm portions (77pr, 77qr, 77rr) extend in a direction overlapping the spark plug central axis (Cs) when viewed in the cylinder axial direction. Since the mounting arm (77pr) is formed with a recess (77d) that opens toward the spark plug (49) so as to straddle the spark plug center axis (Cs), the spark plug (49) is ignited. When moving in the direction of the plug center axis (Cs) and attaching and detaching, the mounting arm (77pr) does not become a hindrance due to the recess (77d), and the maintainability of the spark plug (49) can be maintained well. it can.

According to the variable valve operating apparatus for an OHC type internal combustion engine according to claim 6, the cylinder head (33) has mounting arm portions (77pr, 77qr, 77rr) extending around the housing case (77, 78). The abutting ribs (103pr, 103qr, 103rr) and the mounting bosses (103p, 103q, 103r) at the ends of the ribs (103pr, 103qr, 103rr) are formed in a protruding manner, and the mounting bosses (103p, 103q) , 103r) is attached to the mounting arm (77pr, 77qr, 77rr), so the pressure source (75) is connected to the cylinder head by the rib (103pr, 103qr, 103rr) and mounting boss (103p, 103q, 103r). (33) is held stably.
In addition, the mounting arm part (77pr, 77qr, 77rr) of the pressing force source (75) is attached to the rib part (103pr, 103qr, 103rr) and the mounting boss part (103p, 103q, 103r). The rigidity of the portions (103pr, 103qr, 103rr) and the mounting boss portions (103p, 103q, 103r) can be maintained high, and the pressing force generation source (75) can be supported more firmly.

  According to the variable valve operating apparatus for the OHC type internal combustion engine according to claim 7, the housing case (77, 78) and the mounting arm portion (77pr, 77qr, 77rr) in the pressing force generation source (75) are made of metal. The heat generated in the housing case (77, 78) of the pressing force source (75) can be conducted from the mounting arm (77pr, 77qr, 77rr) to the rib (103pr, 103qr, 103rr). The heat radiation efficiency of the pressure source (75) can be improved.

  Furthermore, since the rib part (103pr, 103qr, 103rr) and the mounting boss part (103p, 103q, 103r) are formed to protrude from the wall surface (100L) of the cylinder head (33), the rib part (103pr, 103qr, 103rr) And a portion protruding from the contact surface of the mounting arm portion (77pr, 77qr, 77rr) that contacts the mounting boss portion (103p, 103q, 103r) forms a space between the cylinder head wall surface (100L), When the traveling wind enters the space, the mounting arm portions (77pr, 77qr, 77rr) can be cooled, and the air cooling effect can be enhanced.

  According to the variable valve operating apparatus for the OHC type internal combustion engine according to claim 8, the side wall (100L) to which the pressing force generation source (75) of the cylinder head (33) is attached is close to the pressing force generation source (75). Since the oil passage (133) is formed, the pressure generation source (75) can be effectively cooled by the oil flowing through the oil passage (133).

  According to the variable valve operating apparatus for an OHC type internal combustion engine according to claim 9, the OHC type internal combustion engine (30) is mounted on the straddle-type vehicle (1) in a posture in which the cylinder axis (Cc) is largely tilted to near horizontal. Mounted on the body frame, the pressing force source (75) is attached to the side wall surface (100L) facing the vehicle width direction of the cylinder head (33), and the outer side of the pressing force source (75) in the vehicle width direction is the body frame. The pressure source (75) is disposed between the cylinder head (33) and the vehicle body frame (6), and the cylinder head (33) and the vehicle body frame (6) The pressing force source (75) can be effectively protected from external factors.

  According to the variable valve operating apparatus for the OHC type internal combustion engine according to claim 10, the water is applied to the side wall surface (100R) opposite to the side wall surface (100L) to which the pressing force generation source (75) of the cylinder head (33) is attached. Since the pump (150) is attached, the side wall surfaces (100L) on both sides facing the vehicle width direction of the cylinder head (33) so that the pressing force generation source (75) and the water pump (150), which are heavy objects, do not interfere with each other. , 100R), the weight balance around the cylinder head (33) can be improved, and both the pressure generation source (75) and the water pump (150) are attached to the cylinder head (33). Even in this case, good maintainability of the spark plug (49) can be ensured.

  According to the variable valve operating apparatus for the OHC type internal combustion engine according to claim 11, the breather chamber (34b) is provided inside the head cover (34), and the outlet of the breather chamber (34b) is provided on the outer wall surface of the head cover (34). The part (34c) is formed with the opening toward the water pump (150) side in the vehicle width direction, so it is connected to the outlet part (34c) of the breather chamber (34b) in the head cover (34) side of the water pump (150) The breather hose (146) extending to the water pump (150) provided on the crankcase (31) side from the pressing force generation source (75) does not interfere with the pressing force generation source (75) on the opposite side. Interference can be easily avoided.

1 is an overall side view of a scooter type motorcycle according to an embodiment of the present invention. It is an II arrow directional view of FIG. It is the whole left side view of a power unit. It is the right view which abbreviate | omitted one part of the internal combustion engine of the power unit. It is sectional drawing (VV sectional view taken on the line of FIG. 3) of the same internal combustion engine. It is a vertical sectional view of a cylinder head and its periphery. It is the figure which looked at the cylinder axial direction from the head cover side by removing the head cover and the cylinder head and the valve mechanism. FIG. 8 is a cross-sectional view taken along line VIII-VIII in FIGS. 6 and 7. It is the IX-IX sectional view taken on the line of FIG. 6 and FIG. FIG. 7 is a cross-sectional view of the main part of the cylinder head and the variable valve operating apparatus when the electromagnetic solenoid is not operated (cross-sectional view taken along line XX in FIG. 6). It is the principal part sectional drawing at the time of the action | operation of an electromagnetic solenoid. It is principal part sectional drawing of a cylinder head and a variable valve apparatus when the electromagnetic solenoid of another example is non-operation. It is a top view of a cylinder head. FIG. 14 is a left side view of the same cylinder head (viewed along arrow XIV in FIG. 13). It is a right side view (XV arrow view of FIG. 13) of the cylinder head single item. It is the XIII-XIII sectional view taken on the line of FIG. It is the XVII-XVII sectional view taken on the line of FIG. It is the XVIII-XVIII sectional view taken on the line of FIG. 13 and FIG.

Hereinafter, an embodiment according to the present invention will be described with reference to the drawings.
FIG. 1 is a side view of a scooter type motorcycle 1 that is a straddle-type vehicle according to an embodiment to which the present invention is applied.
In the present specification, the front, rear, left, and right are determined based on the vehicle of the motorcycle 1.

  The vehicle body front portion 1f and the vehicle body rear portion 1r are connected via a low floor portion 1c, and the vehicle body frame forming the skeleton of the vehicle body extends downward from the head pipe 2 of the vehicle body front portion 1f. A pair of floor pipes 4, 4 branching left and right at the lower end of the down tube 3 are bent horizontally and extend rearward below the floor portion 1c, bend obliquely upward at the rear portion of the floor portion 1c and rise to the rear. A pair of left and right main pipes 5 and 5 extending frontwardly and supported at the rear ends of the floor pipes 4 and 4 extend rearward and obliquely upward to connect the rear ends.

Then, connecting pipes 6 that protrude from the rear portions of the floor pipes 4 and 4 obliquely upward and have both ends fixed and bent in a U shape projecting forward are provided.
The ends of the main pipes 5 and 5 are fixed to the left and right side portions of the connecting pipe 6 so that the main pipes 5 and 5, the floor pipes 4 and 4 and the connecting pipe 6 are mutually connected and firmly assembled. (See FIG. 2).

The storage box 8 and the fuel tank 9 are supported forward and backward by the main pipes 5 and 5, and the seat 10 is disposed above them.
In the vehicle body front portion 1 f, a handle 11 is provided on the upper side of the head pipe 2, a front fork 12 extends downward, and a front wheel 13 is supported on the lower end thereof.
Brackets 7, 7 project downward from the rear rising portions of the floor pipes 4, 4, and a power unit 20 is swingably connected to the brackets 7, 7 via a link member 16.

  The power unit 20 is a single-cylinder four-stroke water-cooled OHC type internal combustion engine 30 in a front portion thereof, and is in a posture in which the cylinder axis of the cylinder is largely inclined to a substantially horizontal state. An end portion of a hanger bracket 18 protruding forward from the lower end is connected to the link member 16 via a pivot shaft 19.

The power unit 20 includes a belt-type continuously variable transmission 21 extending rearward from the internal combustion engine 30, and a rear wheel 14 is provided on a rear axle 14a that is an output shaft of a speed reduction mechanism 22 provided at a rear portion thereof.
A rear cushion 15 is interposed between a bracket 20b erected at the rear part of the power unit 20 having the speed reduction mechanism 22 and a bracket 5b erected at the rear part of the main pipe 5.

  Referring to FIG. 3 which is a side view of the power unit 20, the internal combustion engine 30 is inclined largely forward by a cylinder block 32, a cylinder head 33, and a head cover 34 being sequentially stacked substantially forward from the crankcase 31. In the upper part, the intake pipe 23 extends from the upper part of the cylinder head 33 inclined largely forward of the internal combustion engine 30 and curves backward, and the throttle body 25 connected to the intake pipe 23 is located above the cylinder block 32, An air cleaner 27 connected to the throttle body 25 via a connecting pipe 26 is disposed above the belt type continuously variable transmission 21.

The intake pipe 23 is provided with an injector 24 that injects fuel toward the intake port.
On the other hand, the exhaust pipe 28 extending downward from the lower portion of the cylinder head 33 is bent rearward, is biased to the right and extends rearward, and is connected to a muffler (not shown) on the right side of the rear wheel 21.

  The front part 1f of the vehicle body is covered from the front and back by a front cover 29a and a leg shield 29b, the lower part is covered from the front to the left and right sides by the front lower cover 29c, the floor part 1c is covered by the side cover 29d, and the rear part 1r of the vehicle body Covered by the body cover 29e from the left-right side.

FIG. 5 is a cross-sectional view of the internal combustion engine 30 in the first half of the power unit 20 (a cross-sectional view taken along line VV in FIG. 3).
In the internal combustion engine 30, a connecting rod 37 connects a piston 36 that reciprocates in a cylinder liner 38 of a cylinder block 32 and a crank pin 35 a of a crankshaft 35.
The crankcase 31 is configured by combining a left crankcase 31L and a right crankcase 31R which are divided into left and right parts. The right crankcase 31R forms a half of a crankcase portion, and the left crankcase 31L is a front crankcase 31L. The portion forms a half of the crankcase portion, and also serves as a transmission case that swells rearward and accommodates the long belt-type continuously variable transmission 21 in the front and rear.
The front and rear long left open surface of the left crankcase (transmission case) 31L is covered with a transmission case cover 40, and the belt-type continuously variable transmission 21 is accommodated therein.

In the crankcase formed by combining the front portion of the left crankcase 31L and the right crankcase 31R, the crankshaft 35 is rotatably supported by the left and right main bearings 39, 39, and extends in the horizontal direction. Among them, a centrifugal weight 41 and a drive pulley 42a of the belt type continuously variable transmission 21 are provided in the left extension portion.
Referring to FIG. 2, a belt type continuously variable transmission 21 is configured such that a V belt 42c is stretched between a driving pulley 42a and a driven pulley 42b provided on an input shaft 22a of the speed reduction mechanism 22 to transmit power. The gear ratio is automatically changed by changing the winding diameter of the V belt 42c in the driving pulley 42a and the winding diameter in the driven pulley 42b at the same time by the centrifugal weight 41 that moves according to the engine speed. Infinitely variable speed.

A cam chain drive sprocket 43 or the like is fitted on the right extension of the crankshaft 35, and an AC generator 44 is provided on the right end.
A plurality of radiator fans 45 are formed on the right side surface of the outer rotor 44 r of the AC generator 44.
The outer periphery of the radiator fan 45 is generally surrounded by a shroud 46, and a radiator 47 is provided close to and supported by the shroud 46 on the right side of the radiator fan 78. The radiator 47 is covered with a radiator cover 48 with a louver. Yes.

  The internal combustion engine 30 employs a SOHC type four-valve system, and includes four stud bolts 180 through which a cylinder block 32 and a cylinder head 33 penetrate a crankcase 31 in the direction of the cylinder axis (center axis of the cylinder bore) Cc. The valve mechanism 50 is provided in the cylinder head 33 (see FIGS. 5 and 6).

In addition, the head cover 34 is overlaid on the mating surface 100t of the cylinder head 33 via an elastic seal member 185 so as to cover the valve mechanism 50.
A cam chain 51 for transmitting power to the valve mechanism 50 in the head cover 34 is installed between the camshaft 54 and the crankshaft 35. The cam chain chamber 52 for the cam chain 51 includes a right crankcase 31R, a cylinder block 32, It is provided in communication with the cylinder head 33 (see FIG. 5).

That is, the cam chain 51 is connected to the cam chain chamber 52 between the driven cam chain sprocket 53 fitted to the right end of the cam shaft 54 oriented in the horizontal direction and the drive cam chain sprocket 43a fitted to the crankshaft 35. It is passed through the inside.
On the other hand, a spark plug 49 is inserted into the cylinder head 33 from the side opposite to the cam chain chamber 52 (left side) toward the combustion chamber 33a (see FIGS. 2 and 5).

Referring to FIGS. 6 and 10, two left and right first and second intake ports 91 and 92 extend upward from the combustion chamber 90 facing the top surface of the piston 36 of the cylinder head 33 which is largely inclined forward. The first and second intake ports 91 and 92 are joined together to extend as one upstream intake port 93, and the upstream intake port 93 is connected to the intake pipe 23.
On the other hand, two left and right first and second exhaust ports 95 and 96 extend downward from the combustion chamber 90, and the first and second exhaust ports 95 and 96 are joined together in the middle to form one downstream exhaust port 97. The downstream exhaust port 97 is connected to the exhaust pipe 28.

  Cylindrical valve guides 61g and 62g are integrally fitted to the curved outer wall portions of the first and second intake ports 91 and 92 in the cylinder head 33, and are slidably supported by the valve guides 61g and 62g, respectively. The first intake valve 61 and the second intake valve 62 open and close the respective openings of the first and second intake ports 91 and 92 facing the combustion chamber 90.

Further, the first exhaust valve 63 and the second exhaust valve slidably supported by the valve guides 63g and 64g integrally fitted to the curved outer walls of the first and second exhaust ports 95 and 96 in the cylinder head 33, respectively. The valve 64 opens and closes the opening of the first and second exhaust ports 95 and 96 facing the combustion chamber 90.
The first and second intake valves 61, 62 and the first and second exhaust valves 63, 64 are all attached upward by valve springs 61s, 62s, 63s, 64s so as to close the openings facing the combustion chamber 90. (See FIG. 6).

  Since the valve operating mechanism 50 is largely inclined forward so that the cylinder axis C is nearly horizontal, the first and second intake air that opens and closes the openings of the first and second intake ports 91 and 92 to the combustion chamber 90 are opened and closed. Valves 61 and 62 are disposed above the camshaft 54, and first and second exhaust valves 63 and 64 that open and close the opening of the first and second exhaust ports 95 and 96 to the combustion chamber 90 are provided on the camshaft 54. It is arranged below.

As shown in FIG. 6, an intake rocker arm shaft 55 and an exhaust rocker arm shaft 56 are respectively disposed at diagonally upper and lower positions in front of the camshaft 54.
6 and 7, on the upper intake rocker arm shaft 55, a first intake rocker arm 57 and a second intake rocker arm 58 are pivotally supported adjacent to each other on the left and right sides, and the lower exhaust rocker arm shaft 55 is supported. An exhaust rocker arm 59 is pivotally supported on the rocker arm shaft 56.

In the first intake rocker arm 57, a roller 57r pivotally supported on the lower end of a cam side arm portion 57c extending downward from the shaft support portion 57a is brought into rolling contact with the first intake cam lobe 54i of the camshaft 54, and upward from the shaft support portion 57a. An adjustment screw 57t screwed to the working end 57vv, which is the upper end of the extended valve arm 57v, contacts the upper end of the valve stem of the first intake valve 61 biased upward by the valve spring 61s.
In the second intake rocker arm 58, a slipper 58 s formed at a lower portion of the cam side arm portion 58 c extending downward along the first intake rocker arm 57 from a portion biased to the left side of the shaft support portion 58 a is a second intake air of the camshaft 54. A second adjustment screw 58t is slidably contacted with the cam lobe 54ii and is urged upward by a valve spring 62s. The adjustment screw 58t is screwed to a working end 58vv which is an upper end of a valve side arm 58v extending upward from the shaft support 58a. It contacts the upper end of the valve stem of the intake valve 62.

  The exhaust rocker arm 59 pivotally supported by the lower exhaust rocker arm shaft 56 is from a portion biased to the right of the cylindrical shaft support portion 59a located below the first intake rocker arm 57 and the second intake rocker arm 58. A roller 59r pivotally supported on the upper end of the cam-side arm portion 59c extending upward is in rolling contact with the exhaust cam lobe 54e of the camshaft 54, and valve-side arm portions 59c and 59cc extending downward from the left and right sides of the shaft support portion 59a, respectively. The adjusting screws 59t and 59tt screwed to the respective lower ends of the first and second exhaust valves 63 and 64s are in contact with the upper ends of the valve stems of the first and second exhaust valves 63 and 64 biased upward by the valve springs 63s and 64s.

Referring to FIG. 8, the first intake cam lobe 54 i of the camshaft 54 moves the roller 57 r of the first intake rocker arm 57 forward at a predetermined rotation angle of the camshaft 54 to move the first intake rocker arm 57. By swinging, the adjustment screw 57t at the other end pushes the first intake valve 61 against the valve spring 61s, and opens the opening of the first intake port 91 facing the combustion chamber 90 at a predetermined timing.
Similarly, the exhaust cam lobe 54e moves the roller 59r of the exhaust rocker arm 59 forward at a predetermined rotation angle of the cam shaft 54 to swing the exhaust rocker arm 59, so that the tappet screws 59t and 59tt at the other end are swung. Pushes the exhaust valves 63 and 64 against the valve springs 63s and 64s, and opens the openings of the first and second exhaust ports 95 and 96 facing the combustion chamber 90 at a predetermined timing.

However, if the outer peripheral surface of the second intake cam lobe 54ii has a substantially circumferential surface and the slipper 58s at one end of the second intake rocker arm 58 is in sliding contact, the second intake rocker arm 58 hardly swings. The second intake valve 62 is closed while the opening of the second intake port 92 facing the combustion chamber 90 is closed.
However, the second intake cam lobe 54ii has a slight cam crest at the same rotation angle as the intake cam lobe 54i, and the second intake valve 62 is opened slightly in order to prevent fuel accumulation from occurring in the closed valve closed state. I try to let them.
Therefore, the valve closing / stopping state referred to in the present embodiment is not a complete valve closing / stopping but involves a slight valve opening.

The second intake valve 62 is driven to open and close at the same timing as the first intake valve 61 when the variable intake device 70 is connected so that the second intake rocker arm 58 swings integrally with the first intake rocker arm 57. Otherwise, the valve is closed.
Hereinafter, the variable valve apparatus 70 will be described with reference to FIG.
FIG. 10 is a cross-sectional view of the main part of the cylinder head 33 and the variable valve operating device 70 as viewed from the head cover side in the cylinder axis direction.

Referring to FIG. 10, the first intake rocker arm 57 and the second intake rocker arm 58 are pivotally supported by the intake rocker arm shaft 55 through the rocker arm shaft insertion holes 57h and 58h adjacent to each other on the left and right. A first guide hole 57gh and a second guide hole 58gh drilled in parallel to the intake rocker arm shaft 55 are respectively provided in the valve side arm portions 57v and 58v extending above the shaft support portions 57a and 58a. When the valve 61 and the second intake valve 62 are closed, they are formed as circular holes of the same diameter so as to be connected to the left and right coaxial.
The first guide hole 57gh and the second guide hole 58gh are formed with bottom walls 57g and 58g on the opposite side to the surfaces communicating with each other, and the bottom wall 57g of the first guide hole 57gh has a circular hole in the center. .

A connecting pin 71 is inserted into the first guide hole 57gh so as to be slidable in the left and right axial directions, and a bottomed cylindrical connection release piston 72 has a spring 73 between the bottom wall 58g and the second guide hole 58gh. It is inserted and slidably inserted in the left-right axis direction.
The connecting pin 71 is composed of a cylindrical body 71a that completely fits in the first guide hole 57gh and a rod portion 71b that protrudes from the center of the left end surface of the cylindrical body 71a and penetrates the hollow hole of the bottom wall 57g. When the two guide holes 58gh are connected to the left and right coaxial, the cylindrical body 71a of the connecting pin 71 can move to the second guide hole 58gh and straddle both the first and second guide holes 57gh and 58gh.

  When the first intake valve 61 (and the second intake valve 62) is closed, when the first guide hole 57gh and the second guide hole 58gh are connected to the left and right coaxial, an external force is applied to the rod portion 71b of the connecting pin 71. If not, as shown in FIG. 10, the connection release piston 72 urged by the spring 73 presses the connection pin 71 to the left (right in FIG. 10), and the cylindrical body 71a is completely moved to the first guide hole. The first intake rocker arm 57 and the second intake rocker arm 58 swing independently of each other because the right end surface of the columnar body 71a with which the release piston 72 contacts is flush with the right opening end surface of the first guide hole 57gh. Is possible.

  However, as shown in FIG. 11, when an external force is applied to the rod portion 71 b of the connecting pin 71 and the connecting pin 71 is pushed rightward (leftward in FIG. 11), the connecting pin 71 is subjected to the biasing force of the spring 73. The coupling release piston 72 is pushed in against the cylindrical body 71a of the coupling pin 71 by entering into the second guide hole 58h and being inserted and positioned across both the first guide hole 57gh and the second guide hole 58gh. The first intake rocker arm 57 and the second intake rocker arm 58 are connected via a connecting pin 71 and swing together.

  When the external force to the connection pin 71 is lost, the connection release piston 72 moves backward by pushing the connection pin 71 to the left by the urging force of the spring 73, and the connection is released by placing it in the first guide hole 57gh. Can do.

  In this way, the first intake rocker arm 57 and the second intake rocker arm 58 are connected and rocked together by the advancement (movement to the right) of the connection pin 71, and the connection pin 71 is moved backward (movement to the left). Thus, the connection between the first intake rocker arm 57 and the second intake rocker arm 58 is released.

  Referring to FIG. 6 (and FIG. 10), the axis Cp of the connecting pin 71 is the same as the axis Cr of the head end portions 57tt and 58tt of the adjusting screws 57t and 58t and the rocker arm shaft insertion holes 57h and 58h in the cylinder axis direction. It is arranged between.

  The cylinder head 33 that is greatly inclined forward has an outer peripheral wall 100 having a rectangular cylindrical shape with four side walls of the left side wall 100L, the right side wall 100R, the upper side wall 100U, and the lower side wall 100S, and the left side of the connecting pin 71 on the left side wall 100L. A rod sliding hole 102 penetrating left and right is drilled in a portion where the rod portion 71b protruding in the direction (rightward in FIG. 10) is generally opposed, and a push rod 74 is slidably inserted into the rod sliding hole 102. It is.

  The push rod 74 has a disk portion 74a having an enlarged diameter at the right end, and the right end disk portion 74a from the right side (left side in FIG. 10) is inserted into the rod sliding hole 102 of the left side wall 100L inside the cylinder head 33. The left end is positioned inside the rod sliding hole 102.

The right side surface of the disc portion 43a at the right end of the push rod 74 is opposed to the rod portion 71b protruding to the right of the connecting pin 71 fitted in the first guide hole 57h of the first intake rocker arm 57.
The connecting pin 71 swings together with the first intake rocker arm 57, but the disk portion 74a of the push rod 74 always has an area that can be opposed to the rod portion 71b of the connecting pin 71 that swings within the swingable range. Have.

An electromagnetic solenoid 75, which is a pressing force generation source for driving the variable valve device 70, is attached to the left side wall 100L of the cylinder head 33 from the outside.
In addition to the electromagnetic solenoid 75, a hydraulic cylinder or the like can be applied as a pressing force generation source.
As shown in FIGS. 10 and 11, the operating rod 76 protruding rightward of the electromagnetic solenoid 75 is inserted from the left side into the rod sliding hole 102 into which the push rod 74 is inserted from the right side, and the left end of the push rod 74 is inserted. And the right end of the operating rod 76 face each other inside the rod sliding hole 102.

  Referring to FIG. 6 (and FIG. 10), the axis Cd of the pressing force transmitting member of the push rod 74 and the operating rod 76 inserted into the rod sliding hole 102 is in the first guide hole 57gh of the first intake rocker arm 57. It is always on the crankcase 31 side and on the intake rocker arm shaft 55 side with respect to the axis Cp of the connecting pin 71 that is inserted and swings.

  FIG. 10 is a cross-sectional view of the main part when the electromagnetic solenoid 75 is not in operation. The urging force of the spring 73 presses the connection pin 71 to the left via the connection release piston 72, and the cylindrical body 71a is completely first. The push rod 74 is in a retracted position on the left side in contact with the rod portion 71b of the connecting pin 71 in the released state of being accommodated in the guide hole 57h. In the rod sliding hole 102, the push rod 74 and the electromagnetic solenoid A sandwiching space 80 having an appropriate width is formed between the 75 non-actuating operating rods 76.

    FIG. 11 is a cross-sectional view of the main part when the electromagnetic solenoid 75 is operated. The operating rod 76 protruding rightward by the operation of the electromagnetic solenoid 75 resists the urging force of the spring 73 together with the connection release piston 72. The first intake rocker arm 57 and the second intake rocker arm 58 are pushed rightward (leftward in FIG. 11) so that the cylindrical main body 71a of the connecting pin 71 straddles both the first guide hole 57h and the second guide hole 58h. Is in a connected state.

The cylinder head 33 is a cast product made of an aluminum alloy non-magnetic material, and the structure of the cylinder head 33 will be described in detail with reference to FIGS.
The upper side wall 100U of the cylinder head 33 is formed with an opening of the upstream side intake port 93, and the lower side wall 100S is formed with an opening end slightly extending to the outside of the downstream side exhaust port 97.
A spark plug 49 is attached to the left side wall 100L of the cylinder head 33, and the electromagnetic solenoid 75 is attached as described above (see FIGS. 3 and 8).

Therefore, as shown in FIG. 14, the left side wall 100L of the cylinder head 33 is formed with a spark plug mounting hole 101 into which the spark plug 49 is mounted obliquely in the central recess, and the operating rod 76 of the electromagnetic solenoid 75. The rod sliding hole 102 into which the push rod 74 is inserted is drilled at a position slightly deviated from the center toward the upper side wall 100U in the vicinity of the mating surface 100t of the cylinder head 33 with the head cover 34.
The outer opening of the rod sliding hole 102 forms a rod boss portion 102b in which an enlarged inner diameter portion 102a in which the inner diameter of the rod sliding hole 102 is expanded in two steps is formed (see FIG. 17).

Referring to FIG. 14, in the left side wall 100L of the cylinder head 33, a mounting boss portion 103p having a mounting hole is formed at a position near the mating surface 100t and deviated from the center toward the lower side wall 100S. A rib portion 103pr is formed to extend along the mating surface 100t toward the mounting boss portion 103p.
The rod boss part 102b is on the upper wall 100U side from the spark plug mounting hole 101, the mounting boss part 103p is on the lower wall 100S side from the spark plug mounting hole 101, and the rib part 103pr connecting the rod boss part 102b and the mounting boss part 103p is The center spark plug mounting hole 101 is formed across the mating surface 100t side.

Further, an attachment boss portion 103q and a rib portion 103qr are formed on the opposite side of the rod boss portion 102b from the attachment boss portion 103p, and an attachment boss portion 103r is formed at a position somewhat away from the rod boss portion 102b on the opposite side of the mating surface 100t. A rib portion 103rr is formed to extend from the rod boss portion 102b toward the mounting boss portion 103r.
That is, two rib portions 103pr and 103qr extend from the rod boss portion 102b to the opposite sides along the mating surface 100t, and one rib portion 103rr extends in a direction perpendicular to the rib portions 103pr and 103qr. Mounting boss portions 103p, 103q, 103r are formed at the ends.

  The above-described three mounting boss portions 103p, 103q, 103r and the three rib portions 103pr, 103qr, 103rr bulge from the outer wall surface of the left side wall 100L, and the mounting surfaces (Fig. 14, a portion hatched with a lattice hatch is formed.

On the other hand, as shown in FIG. 10, the electromagnetic solenoid 75 is a solenoid in which a movable iron core 75d is integrally fixed to an end of an operating rod 76 that passes through a fixed iron core 75s, and a coil 75c is provided around the movable iron core 75d. The main body is accommodated in housing cases 77 and 78 divided into two parts.
A spring 79 is interposed between the fixed iron core 75s and the movable iron core 75d.
The housing cases 77 and 78 are made of metal having a good thermal conductivity.

  The housing case 77 includes a cylindrical portion 77a covering the periphery of the coil 75c, a bottom wall portion 77b thereof, and three attachment arm portions 77pr, 77qr, and 77rr extending radially from the bottom wall portion 77b. Mounting boss portions 77p, 77q, 77r having mounting holes are formed at the ends of 77pr, 77qr, 77rr (see FIGS. 3 and 14).

A rod boss portion 77bb, on which the operating rod 76 is slidably supported, is formed in the center of the bottom wall portion 77b so as to protrude inward and outward, and a portion protruding inside the rod boss portion 77bb constitutes a fixed iron core 75s.
The opening end of the cylindrical portion 77a of the housing case 77 is covered with a bottomed cylindrical housing case 78, and covers the movable iron core 75d.
An elastic member 78r is affixed to the bottom surface of the bottomed cylindrical storage case 78 so as to face the movable iron core 75d.

  Three mounting arm portions 77pr, 77qr, 77rr and three mounting boss portions 77p, 77q, 77r extending radially from the bottom wall portion 77b of the housing case 77 are three on the left side wall 100L of the cylinder head 33, respectively. The rib portions 103pr, 103qr, 103rr and the three mounting boss portions 103p, 103q, 103r are opposed to each other, and the mounting boss portions 103p, 103q, 103r and the rib portions 103pr, 103qr, 103rr are formed. The mounting boss portions 77p, 77q, and 77r and the mounting arm portions 77pr, 77qr, and 77rr are brought into contact with the continuous mounting surface that is the same plane, and the mounting boss portions are screwed together by bolts 104p, 104q, and 104r, and the electromagnetic solenoid 75 Is attached to the left side wall 100L of the cylinder head 33 (see FIGS. 3 and 14).

At this time, the rod boss portion 77bb formed to project to the center of the bottom wall portion 77b of the housing case 77 is provided with a seal member 83 and an O-ring 84 in the enlarged inner diameter portion 102a of the rod sliding hole 102 of the cylinder head 33. (See FIG. 10).
The bottom wall portion 77b of the housing case 77 of the electromagnetic solenoid 75 and the mounting arm portions 77pr and 77qr protrude from the mating surface 104h of the cylinder head 33 with the head cover 34 to the head cover 34 side, as shown by a two-dot chain line in FIG. (See FIGS. 8 and 14).
However, the electromagnetic solenoid 75 is attached only to the cylinder head 33.

  Referring to FIG. 14, the electromagnetic solenoid 75 thus attached to the cylinder head 33 is located closer to the head cover 34 than the spark plug 49, and the spark plug center axis Cs directed by the spark plug 49 as viewed in the cylinder axial direction shown in FIG. It is provided at a position where it does not overlap.

  The mounting arm portion 77qr of the housing case 77 that contacts the rib portion 103pr formed across the spark plug mounting hole 101 in the center of the cylinder head 33 on the mating surface 100t side includes the mounting boss portion 103p and the mounting arm portion A recess 77d that is open toward the spark plug 49 so as to avoid the spark plug center axis Cs directed to the spark plug 49 mounted in the spark plug mounting hole 101 between 77rr is formed (FIG. 3, FIG. 3). (See FIGS. 8 and 14).

  When the power unit 20 is mounted on the scooter type motorcycle 1, as shown in FIGS. 1 and 2, the electromagnetic solenoid 75 attached to the left side wall 110L of the cylinder head 33 of the internal combustion engine 30 in the vehicle width direction outside (left side). ) And the front of the vehicle body frame so as to surround the connecting pipe 6.

The OHC type internal combustion engine 30 is a water-cooled internal combustion engine, and a water pump 85 is attached to the right side wall 100R of the cylinder head 33 opposite to the left side wall 100L to which the electromagnetic solenoid 75 is attached.
A large-diameter circular hole 105 is formed in the right side wall 100R of the cylinder head 33 (see FIG. 15), and a water pump body 151 having a cylindrical shape of the water pump 150 is fitted and supported in a watertight manner (see FIG. 8). ).

  Referring to FIG. 8, a water pump body 151 of a water pump 150 includes a long cylindrical portion 151a that is long in the axial direction for rotatably supporting a pump drive shaft 153 via a bearing 155, and one opening thereof. The end is extended in the radial direction and is partially expanded to the radial direction to partially accommodate the impeller 154 fitted to the water pump drive shaft 153, and is composed of a short cylindrical portion 151b that is short in the axial direction. The pump drive shaft 153 is coaxial with the camshaft 54 and is fitted and fixed to the circular hole 105 of the right side wall 100R of the cylinder head 33 with an O-ring 156 interposed therebetween. The left end of the pump drive shaft 153 is connected to the camshaft 53. It is configured to be fitted directly into a fitting hole drilled in the right end surface and directly connected to rotate coaxially.

A water pump cover 152 that covers the right opening of the short cylindrical portion 151b of the water pump body 151 and accommodates the impeller 154 together with the short cylindrical portion 151b is superimposed on the opening end surface of the short cylindrical portion 151b.
Four bolt holes are formed on the outer periphery of the short cylindrical portion 151b of the water pump body 151, and four bolt holes are formed in the water pump cover 152 corresponding to the bolt holes of the water pump body 151 (see FIG. 4 and FIG. 15).

On the right side wall 100R of the cylinder head 33, there are formed mounting boss portions 106 having three female screw holes around the circular hole 105, and three corresponding bolts of the water pump body 151 and the water pump cover 152 are formed. The holes are in contact with the three mounting boss portions 106 of the cylinder head 33 and are fastened together by bolts 157a to attach the water pump 150 to the right side wall 100R of the cylinder head 33.
The other corresponding bolt hole of the water pump body 151 and the water pump cover 152 protrudes from the mating surface 100t of the cylinder head 33 with the head cover 34 toward the head cover 34, and both are fastened by bolts 157b. (See FIG. 8).

  Referring to FIG. 4, the water pump cover 152 has a water suction cylinder portion 152a extending from the suction port swelled to the right of the water pump drive shaft 153 to the cylinder block 32 side along the right side surface of the cylinder head 33. The discharge port directed in the tangential direction extends from the outer periphery of the impeller 154 to extend the water discharge tube portion 152b, and the air bleed tube portion 152c projects upward from the upper periphery of the impeller 154. Has been.

Further, the water outlet opening 107 of the water jacket 33w in the cylinder head 33 is formed on the right side wall 100R of the cylinder head 33, and at two locations around the circular hole 105 along the mating surface 100t with the head cover 34. Working holes 108 and 109 are drilled.
The working holes 108 and 109 are coaxial with the intake rocker arm shaft 55 and the exhaust rocker arm shaft 56.

Referring to FIG. 4, water suction cylindrical portion 152 a extending to the cylinder block 32 side of water pump 150 is connected to thermostat 160.
A branch connection pipe 161 protrudes from the water outlet opening 107 of the cylinder head 33, and the main pipe of the branch connection pipe 161 is connected to the radiator tank 47a on the upstream side of the radiator 47 via the radiator inflow hose 162. A branch pipe of the pipe 161 is connected to the thermostat 160 via a bypass hose 164.

A radiator tank 47 b downstream of the radiator 47 and the thermostat 160 are connected by a radiator outlet hose 163.
A water discharge hose 165 connects the water inflow opening of the water jacket in the cylinder block 32 and the water discharge cylindrical portion 152b of the water pump 150.
Note that an air vent cylinder portion 152 c protruding above the water pump 150 is connected to an upper branch connecting pipe 161 via an air vent pipe 166.

  During the warm-up operation in which the internal combustion engine 30 does not warm up, the thermostat 160 closes the water path flowing in from the radiator 47, opens the water path bypassed from the cylinder head 33, accelerates the warm-up in the water path that does not pass through the radiator 47, and warms up. After the operation is completed, the thermostat 160 closes the water path bypassing from the cylinder head 33 and opens the water path flowing in from the radiator 47, and the cooling water cooled by the radiator 47 is supplied from the cylinder block 32 to the cylinder head 33. And the cylinder block 32 and the cylinder head 33 are cooled.

In the cylinder head 33, an inner wall 110 constituting the cam chain chamber 52 is formed in parallel with the right side wall 100R between the outer side wall 100 and the right side wall 100R (see FIGS. 9 and 13).
The inner wall 110 is formed with a bearing circular hole 111 that is coaxial with the circular hole 105 formed in the right side wall 100R and has substantially the same diameter, and is coaxial with the working holes 108 and 109 formed in the right side wall 100R and has the same diameter. An intake rocker arm shaft support portion 112 and an exhaust rocker arm shaft support portion 113 having an intake rocker arm shaft support hole 112h and an exhaust rocker arm shaft support hole 113h are formed.

The working holes 108 and 109 for drilling the rocker arm shaft support holes 112h and 113h are closed from the outside by the plug members 65 and 66 (see FIGS. 7 and 9).
When the water pump 150 is attached to the right side wall 100R of the cylinder head 33, the short cylindrical portion 151b of the water pump body 151 covers the plug members 65 and 66 at positions close to the outside (see FIGS. 4 and 7).
Accordingly, the water pump 150 attached to the cylinder head 33 prevents the plug members 65 and 66 from falling off.

Stud bolt fastening holes 115 and 116 penetrating in the cylinder axial direction are formed on both outer sides of the intake rocker arm shaft support portion 112 and the exhaust rocker arm shaft support portion 113 of the inner wall 110 (see FIGS. 13 and 16).
Stud bolts 180 and 180 are inserted into the stud bolt fastening holes 115 and 116, respectively.

  The left side wall 100L protrudes inward from the mating surface 100t with the head cover 34, faces the inner wall 110, and forms a bearing circular hole 121 that is coaxial with the bearing circular hole 111 of the inner wall 110 and smaller in diameter than the bearing circular hole 111. And an intake rocker arm shaft support portion 122 having an intake rocker arm shaft support hole 122h and an exhaust rocker arm shaft support hole 123h having the same diameter so as to be coaxially opposed to the intake rocker arm shaft support hole 112h and the exhaust rocker arm shaft support hole 113h of the inner wall 110. , An exhaust rocker arm shaft support portion 123 is formed.

Stud bolt fastening holes 125 and 126 penetrating in the cylinder axial direction are formed at positions slightly offset to the left on both outer sides of the intake rocker arm shaft support portion 122 and the exhaust rocker arm shaft support portion 123 (FIGS. 13 and 14). reference).
Stud bolts 180 and 180 are inserted into the stud bolt fastening holes 125 and 126, respectively.

The rod sliding hole 102 is formed between the intake rocker arm shaft support hole 122h of the left side wall 100L and the stud bolt fastening hole 125 in the vicinity thereof and overlaps with the intake rocker arm shaft support hole 122h in the cylinder axis direction. (See FIGS. 13, 17, and 18).
As shown in FIG. 7, the rod sliding hole 102 overlaps with the nut 181 when viewed in the cylinder axial direction, and is provided close to the stud bolt fastening hole 125.

Further, in the vicinity of the stud bolt fastening hole 125, an oil supply hole 130 is opened at the end surface on the head cover 34 side of the left side wall 100L and is drilled toward the rod sliding hole 102 in the cylinder axial direction.
The oil supply hole 130 and the rod sliding hole 102 are in a positional relationship such that their central axes are separated and intersect at a right angle.
Therefore, the oil supply hole 130 communicates the inner space of the cylinder head 33 with the rod sliding hole 102.

The camshaft 54 is rotatably supported by the coaxial bearing circular hole 111 and the bearing circular hole 121 in the inner wall 110 and the left side wall 100L facing each other.
Referring to FIG. 8, the camshaft 54 is rotatably inserted into the bearing circular hole 121 at the left end and is pivotally supported by the bearing circular hole 111 through the bearing 82.
The camshaft 54 protrudes into the cam chain chamber 52 on the right side from the bearing 82, and the driven cam chain sprocket 53 is fitted to the right end thereof.
A decompression mechanism 85 is incorporated between the camshaft 54 and the exhaust cam lobe 54e on the left side of the bearing 82 by using the exhaust cam lobe 54e.

  Both ends are inserted into coaxial intake rocker arm shaft support holes 112h and intake rocker arm shaft support holes 122h on the opposed inner wall 110 and left side wall 100L, and the intake rocker arm shaft 55 is installed and supported (see FIGS. 7 and 9). Both ends of the exhaust rocker arm shaft support hole 113h and the exhaust rocker arm shaft support hole 123h are fitted to support the exhaust rocker arm shaft 56 (see FIGS. 7 and 8).

  Intake rocker arm shaft support 112 on the inner wall 110, exhaust rocker arm shaft support 113, stud bolt fastening holes 115 and 116 open end and left side wall 100L intake rocker arm shaft support 122, exhaust rocker arm shaft support 123, stud bolt fastening The opening end portions of the holes 125 and 126 all have an end surface (portion to which a lattice hatching is applied in FIG. 13) that is flush with the mating surface 104t of the cylinder head 33 with the head cover 34.

Referring to FIG. 13, the intake rocker arm shaft support portion 112 of the inner wall 110 is formed with a small-diameter pin fitting hole 112p penetrating from the end surface to the intake rocker arm shaft support hole 112h in the cylinder axis direction.
The intake rocker arm shaft 55 that is inserted into the intake rocker arm shaft support hole 112h is formed with a pin insertion hole 55p that penetrates the shaft center in the diameter direction in correspondence with the pin insertion insertion hole 112p. And the intake rocker arm shaft 55 are fixed to the intake rocker arm shaft support 112 by inserting the pin member 142 into the pin insertion holes 112p and 55p formed coaxially on the intake rocker arm shaft 55 from the head cover 34 side. (See FIG. 9).

The exhaust rocker arm shaft support portion 123 of the left side wall 100L is formed with a small-diameter pin fitting insertion hole 123p penetrating from the end surface into the exhaust rocker arm shaft support hole 123h in the cylinder axial direction.
The exhaust rocker arm shaft 56 to be inserted into the exhaust rocker arm shaft support hole 123h is formed with a pin insertion hole 56p that penetrates the shaft center in the diameter direction in correspondence with the pin insertion hole 123p. And the exhaust rocker arm shaft 56, the pin member 143 is fitted and inserted into the pin fitting insertion holes 123p, 56p coaxially formed on both sides of the exhaust rocker arm shaft 56, whereby the exhaust rocker arm shaft 56 is fixed to the exhaust rocker arm shaft support 123. (See FIG. 8).
The intake rocker arm shaft support portion 122 of the left side wall 100L is formed with a work hole 127 penetrating from the end surface to the intake rocker arm shaft support hole 122h in the cylinder axial direction.

A reinforcing plate 140 is installed between the open ends of the stud bolt fastening holes 115 and 116 of the inner wall 110 (see FIG. 7).
The reinforcing plate 140 is in contact with the end surfaces of the opening ends of the stud bolt fastening holes 115 and 116 and the end surfaces of the intake rocker arm shaft support portion 112 and the exhaust rocker arm shaft support portion 113, and both ends thereof are cylinders by stud bolts 180 and 180. It is fastened together with the head 33.

The reinforcing plate 140 has a bent plate portion 140b in which the center portion of the side edge on the cam chain chamber 52 side (left side) between both ends is bent and extended toward the bearing circular hole 111 side (FIG. 8, (See FIG. 9).
As shown in FIG. 6, the bent plate portion 140b has a width between the substantially central axes of the intake rocker arm shaft support hole 112h and the exhaust rocker arm shaft support hole 113h, and the intake rocker arm shaft support hole 112h and the exhaust rocker arm shaft support hole 113h. The tip portion recessed on the circular arc partially closes the opening of the bearing circular hole 111.

  Therefore, as shown in FIGS. 6 and 8, the reinforcing plate 140 prevents the outer race of the bearing 82 that pivotally supports the camshaft 54 from being pulled out of the bearing circular hole 111 by the bent plate portion 140b. Restricts movement in the axial direction.

At the same time, as shown in FIGS. 6 and 9, the bent plate portion 140b of the reinforcing plate 140 allows the intake rocker arm shaft 55 and the exhaust rocker arm shaft 56 to come out of the intake rocker arm shaft support hole 112h and the exhaust rocker arm shaft support hole 113h, respectively. To prevent movement in the axial direction.
Further, the reinforcing plate 140 is provided with a pin fitting insertion hole 140p coaxially at a position corresponding to the pin fitting insertion hole 112p formed in the intake rocker arm shaft support portion 112 of the cylinder head 33.

On the other hand, a reinforcing plate 141 is installed between the open ends of the stud bolt fastening holes 125 and 126 of the left side wall 100L.
The reinforcing plate 141 is in contact with the end surfaces of the respective opening end portions of the stud bolt fastening holes 125 and 126 and the end surfaces of the intake rocker arm shaft support portion 122 and the exhaust rocker arm shaft support portion 123, and both ends thereof are cylinders by the stud bolts 180 and 180. It is fastened together with the head 33.

The reinforcing plate 141 is formed with a recess 141p so as to avoid the pin fitting insertion hole 123p of the exhaust rocker arm shaft support 123 (see FIG. 7).
As shown in FIG. 7, the reinforcing plate 141 closes the working hole 127 of the intake rocker arm shaft support portion 122 and partially covers the opening of the oil supply hole 130.

  A reinforcing plate 140 installed between the opening ends of the stud bolt fastening holes 115 and 116 on the inner wall 110 is fastened together with the cylinder head 33 at both ends by the stud bolts 180 and 180, and the stud bolt fastening hole 125 on the left side wall 100L. , 126 are installed between the open end portions of the first and second ends, but both ends are fastened together with the cylinder head 33 by the stud bolts 180, 180, so that the rigidity of the cylinder head 33 can be maintained high.

The pin member 142 inserted into the pin insertion holes 112p and 55p of both the intake rocker arm shaft support portion 112 and the intake rocker arm shaft 55 penetrates the pin insertion insertion hole 140p of the reinforcing plate 140 and protrudes the end portion. (See FIG. 9).
Further, the pin member 143 inserted into the pin insertion holes 123p, 56p of both the exhaust rocker arm shaft support portion 123 and the exhaust rocker arm shaft 56 penetrates the concave portion 141p of the reinforcing plate 141 and protrudes the end portion ( (See FIG. 9).

As shown in FIG. 9, the head cover 34 divides an inner space formed by being bulged inward by a bulging portion 34 a having a large bulged central portion by a breather plate 145 attached from the inside to form a breather chamber 34 b. doing.
The breather plate 145 is stretched parallel to the mating surface 100t of the cylinder head 33 on the head cover 34 side with a predetermined interval.
As shown in FIG. 9, the end portions of the pin members 142 and 143 protruding through the reinforcing plates 140 and 141 are close to the breather plate 145 with a slight gap therebetween.

  Therefore, the breather plate 145 attached to the head cover 34 regulates the amount of movement of the pin members 142 and 143 inserted into the pin insertion holes 112p and 123p of the intake rocker arm shaft support 112 and the exhaust rocker arm shaft support 123. The pin members 142 and 143 are prevented from falling off and falling off from the pin insertion holes 112p and 123p.

Referring to FIG. 2 which is a front view of the power unit 20 mounted on the vehicle, the outlet portion 34c of the breather chamber 34b of the head cover 34 has an opening on the right side (water pump 150 side) above the bulging portion 34a. The breather hose 146 that is formed and has an end connected to the outlet portion 34c extends toward the water pump 150 and is bent to be connected to the clean side of the air cleaner 27 toward the rear.
Therefore, the breather hose 146 does not interfere with the electromagnetic solenoid 75 attached to the left side wall 100L of the cylinder head 33.

Next, the lubrication system in the cylinder head 33 and the valve mechanism 50 will be described.
The stud bolt fastening hole 115 of the cylinder head 33 is used as a passage for oil supplied from the cylinder block 32 side. Referring to FIGS. 7 and 13, the upper wall 100U from the middle of the stud bolt fastening hole 115 is used. An oil passage 131 is formed toward the end, and an end portion of the oil passage 131 is bent to communicate with the oil passage 132 in the upper side wall 100U toward the left side wall 100L, and an end portion of the oil passage 132 is bent to be left side wall 100L. The inside communicates with an oil passage 133 toward the bearing circular hole 121.

In the cylinder head 33 tilted forward to near horizontal, the oil passage 132 horizontally drilled in the upper wall 100U is at the uppermost position, and the upper portion corresponding to the first intake rocker arm 57 and the second intake rocker arm 58 in the oil passage 132. Jet holes 132a and 132b are branched and formed at two locations (see FIGS. 6 and 13).
The oil ejected from the ejection holes 132a and 132b is distributed to the end portions of the valve side arm portions 57v and 58v of the first intake rocker arm 57 and the second intake rocker arm 58 and the adjusting screws 57t and 58t (FIGS. 6 and 10). reference).

The oil passage 133 in the left side wall 100L is drilled in the vicinity of the electromagnetic solenoid 75 attached to the left side wall 100L, passes through the stud bolt fastening hole 125, and intersects the intake rocker arm shaft support hole 122h with a gap. Thus, the end of the oil passage 133 communicates with an oil introduction path 134 formed to extend to the left of the bearing circular hole 121 shown in FIG. 8 (see FIGS. 13 and 14).
The stud bolt fastening hole 125 has a structure in which the top and bottom are closed.
An oil branch passage 133a is connected between the intake rocker arm shaft support hole 122h intersecting the oil passage 133 and the oil passage 133 (see FIGS. 9 and 18).

Referring to FIG. 8, the camshaft 54 has a shaft hole 54a that opens at the left end facing the oil introduction passage 134, and lead-out oil passages 54b, 54c, and 54d are bored in the radial direction from the shaft hole 54a. .
Therefore, the oil introduced into the shaft hole 54a of the camshaft 54 from the oil passage 133 through the oil introduction path 134 is connected to the bearing circular hole 121 of the left side wall 100L through the left outlet oil path 54b to lubricate the bearing portion. The central outlet oil passage 54c opens to the outer peripheral surface of the second intake cam lobe 54ii to lubricate the sliding contact portion of the second intake rocker arm 58 with the slipper 58s, and the right outlet oil passage 54d faces the decompression mechanism 85. To open and lubricate the decompression mechanism 85.

Referring to FIG. 9, an intake rocker arm shaft 55 that is supported by being inserted into an intake rocker arm shaft support hole 122h has a shaft hole 55a that is open at the left end, and the oil branch is disposed on the left side of the shaft hole 55a. An introduction oil passage 55b that passes through the shaft hole 55a is formed coaxially with the passage 133a, and the oil that has been branched from the oil passage 133 to the oil branch passage 133a passes from the introduction oil passage 55b of the intake rocker arm shaft 55 to the shaft hole 55a. be introduced.
The intake rocker arm shaft 55 is formed with a lead-out oil passage 55c in the vicinity of the right end of the shaft hole 55a from the shaft hole 55a toward the second guide hole 58h of the second intake rocker arm 58 (see FIG. 10).

Referring to FIG. 10, the second intake rocker arm 58 is formed with an introduction oil passage 58d that communicates the lead-out oil passage 55c and the right end side of the second guide hole 58h.
The valve side arm portion 58v of the second intake rocker arm 58 is formed with an adjustment oil passage 58e that extends upward from the right end side of the second guide hole 58h.
Therefore, the oil introduced from the shaft hole 55a of the second intake rocker arm 58 into the second guide hole 58h through the lead-out oil passage 55c and the introduction oil passage 58d lubricates the sliding of the connection release piston 72 and is connected. As the release piston 72 slides, it is discharged from the adjustment oil passage 58e and adjusted.

The valve-side arm portion 57v of the first intake rocker arm 57 has an introduction oil passage 57d extending upward from the first guide hole 57h and an oil passage 57e coaxially formed on the opposite side of the introduction oil passage 57d.
The oil sprayed on the upper end of the valve-side arm portion 57v of the first intake rocker arm 57 flows on the surface and enters the introduction oil passage 57d, lubricates the sliding of the release piston 72, and the oil passing through the oil passage 57e The swing of the first intake rocker arm 57 is lubricated.

  In the variable valve operating apparatus 70, the oil supply hole 130 that connects the rod sliding hole 102 into which the operation rod 76 of the electromagnetic solenoid 75 and the push rod 74 are inserted and the inner space of the cylinder head 33 is a cylinder head inclined forward to near horizontal. 13 is a lower position of the outer periphery of the annular opening end surface 125t of the stud bolt fastening hole 125, as viewed in the cylinder axial direction shown in FIG. 13, and the cylinder head 33 is formed on the left side along the outer periphery of the opening end surface 125t. An oil guide groove 135 is formed between the surface 100t and the opening end surface 125t.

The oil guide groove 135 guides the oil that has been ejected from the oil passage 132 in the upper wall 100U of the cylinder head 33 through the ejection holes 132a and adhered to the wall surface on the upper wall 100U side of the cylinder head 33 into the oil supply hole 130.
A rib 136 extending horizontally to the left side from the position in contact with the lower edge of the oil supply hole 130 below the oil guide groove 135 and reaching the mating surface 100t is provided. Oil accumulated above the rib 136 also enters the oil supply hole 130. I am doing so.

  Further, as shown in FIG. 7, one corner of a hexagon nut 181 that passes through the stud bolt fastening hole 125 and is screwed to the stud bolt 180 that fastens the reinforcing plate 141 together with the cylinder head 33 is connected to the other corner. By tightening the hexagon nut 181 so as to face downward in comparison, the oil adhering to the hexagon nut 181 is guided to the corner facing downward and flows down the surface of the reinforcing plate 141 from the corner. It is easy to enter the oil supply hole 130 around the side edge of the reinforcing plate 141.

  In this variable valve operating apparatus 70, when the electromagnetic solenoid 75 is inactive (the first and second intake rocker arms 57 and 58 are not connected by the connecting pin 71 and swing independently), the inside of the rod sliding hole 102 The sandwiching space 80 formed between the actuating rod 76 and the push rod 74 is located at the position shown in FIG. 10, and oil is supplied to the sandwiching space 80 with respect to the sandwiching space 80. The lubrication hole 130 is offset to the push rod 74 side (right side) so that the left end of the push rod 74 faces the lubrication hole 130 and the operating rod 76 does not reach the lubrication hole 130. A part is in a positional relationship communicating with the oil supply hole 130.

  The oil supply hole 130 is oriented in the cylinder axis direction so that the rod slide hole 102 and the center axis of each other are separated from each other at right angles, and the boundary between the oil supply hole 130 and the rod slide hole 102 is The area of the communication port is narrow compared to the case where the central axes of each other are perpendicular to each other. In addition, when the electromagnetic solenoid 75 is not in operation, the oil supply hole 130 is pushed to the inner space 80. The communication port at the boundary between the oil supply hole 130 and the rod sliding hole 102 is partially blocked by the push rod 74, and the inner space 80 is in a state close to a closed space. .

In FIG. 10, the portion of oil supplied from the oil supply hole 130 to the internal space 80 when the electromagnetic solenoid 75 is not operated is indicated by dotted points.
As shown in FIG. 10, the inner space 80 is only in communication with a part of the oil supply hole 130 and is in a state close to a closed space.
Furthermore, as shown in FIG. 7, the reinforcing plate 141 installed between the opening ends of the stud bolt fastening holes 125 and 126 in the left side wall 100L of the cylinder head 33 is provided with the opening of the oil supply hole 130 as viewed in the cylinder axial direction. As a result, oil outflow from the oil supply hole 130 in the internal space 80 is suppressed.

  Thus, when the electromagnetic solenoid 75 is in the non-operating state, the internal space 80 filled with the oil supplied from the oil supply hole 130 is in a state close to the closed space, and the oil outflow from the oil supply hole 130 Therefore, in the initial stage when the electromagnetic solenoid 75 is actuated and the operating rod 76 is protruded, the outflow of oil from the oil supply hole 130 in the inner space 80 is suppressed, and the operating rod 76 is A damper function as an oil damper that presses the push rod 74 through the oil in the space 80 can be enhanced, and shocks and vibrations caused by a collision can be buffered.

As the electromagnetic solenoid 75 operates and the operating rod 76 moves to the right, the push rod 74 also moves to the right through the oil in the inner space 80.
Accordingly, the inner space 80 also moves to the right, so that the offset amount of the oil supply hole 130 that has been offset to the right with respect to the inner space 80 is reduced, and the oil in the inner space 80 is filled with the oil supply hole 130. As a result, the inner space 80 becomes narrow while gradually flowing out from the operation rod, and the operating rod 76 approaches the push rod 74 and finally comes into contact therewith.
Accordingly, since the operating rod 76 comes into contact with the push rod 74 in a state where the push rod 74 is moved to the right, the impact of the contact can be suppressed to be extremely small.

FIG. 11 shows the operating state of the electromagnetic solenoid 75 in which the operating rod 76 has finished moving to the right.
The push rod 74 and the connecting pin 71 move to the right together with the operating rod 76 so that the connecting pin 71 connects the first and second intake rocker arms 57 and 58 to swing together. The right end of this is in contact with the left end of the push rod 74 and the inner space 80 is lost, and the contact portion is in a position in contact with the right side of the oil supply hole 130.

  When the electromagnetic solenoid 75 is switched from the operating state to the non-operating state, the operating rod 76 is moved to the left at once by the spring 79 of the electromagnetic solenoid 75. Following this, the push rod 74 is moved via the connecting pin 71 and the piston 72. The spring 73 moves to the left.

  When the movement of the push rod 74 and the operating rod 76 to the left stops, the inside space 80 is formed again. Therefore, when the operation rod 76 stops, the inside space 80 communicating with the oil supply hole 130 is filled with oil. be able to.

FIG. 12 is an example in which the positional relationship between the internal space 80 and the oil supply hole 130 when the electromagnetic solenoid 75 is in an inoperative state is changed.
When the electromagnetic solenoid 75 is not in operation, the oil supply hole 130 is large with respect to the inner space 80 and is offset to the push rod 74 side (right side), and the push rod 74 is at the boundary between the oil supply hole 130 and the rod sliding hole 102. The communication port is completely blocked.
That is, when the electromagnetic solenoid 75 is in a non-operating state, the inner space 80 is a closed space.

Therefore, in the initial stage when the electromagnetic solenoid 75 is activated, there is almost no oil outflow in the internal space 80, the damper function as an oil damper is maintained high, and shock and vibration due to impact can be effectively buffered. it can.
As the electromagnetic solenoid 75 is activated and the operating rod 76 moves to the right, the inner space 80 also moves and communicates with the oil supply hole 130, so that the oil in the internal space 80 gradually flows out of the oil supply hole 130. However, the inner space 80 becomes narrower, and the operating rod 76 approaches the push rod 74 and finally comes into contact.
Accordingly, since the operating rod 76 comes into contact with the push rod 74 in a state where the push rod 74 is moved to the right, the impact of the contact can be suppressed to be extremely small.

The operation state of the electromagnetic solenoid 75 after the operation rod 76 has finished moving is shown by a two-dot chain line in FIG.
The contact portion between the right end of the actuating rod 76 and the left end of the push rod 74 faces the oil supply hole 130.When the electromagnetic solenoid 75 is switched from the operating state to the non-operating state, the push rod 74 is ahead of the operating rod 76. When the moving rod is configured to stop at a reduced speed, the operating rod 76 moves faster than the push rod 74, and the sandwiched space 80 between the left end of the push rod 74 and the right end of the operating rod 76 gradually increases. When the inner space 80 is in communication with the oil supply hole 130, oil can be sucked into the inner space 80 from the oil supply hole 130. As a result, when the operating rod 76 stops, the inner space 80 Can be filled with oil.

  As shown in FIGS. 7 and 14, the variable valve operating device 70 of the present OHC type internal combustion engine 30 has a pressing force that is attached to the wall surface of the left side wall 100L on which the ignition plug (49) of the cylinder head (33) is projected. Since the housing cases 77 and 78 for housing the main body of the electromagnetic solenoid 75 that is the generation source are provided at a position that does not overlap with the spark plug center axis Cs directed by the spark plug 49 when viewed in the cylinder axial direction, the electromagnetic solenoid 75 is connected to the spark plug. The electromagnetic solenoid 75 can be disposed at a position that does not hinder the movement of the spark plug 49 without being moved away from it, and when the spark plug 49 is moved in the axial direction of the spark plug center axis Cs directed to the spark plug 49 to be attached or detached. The maintainability of the spark plug 49 can be maintained satisfactorily while reducing the size of 33.

  As shown in FIGS. 3 and 14, the electromagnetic solenoid 75 is located closer to the head cover 34 than the spark plug 49, so that a maintenance space around the spark plug 49 can be easily secured.

As shown in FIG. 10, the push rod 74 and the actuating rod 76, which are pressing force transmission members, are slidably provided on the cylinder head 33. Therefore, the head cover of the electromagnetic solenoid 75 that applies the pushing force to the push rod 74 and the actuating rod 76. Swelling to the 34 side can be suppressed, and an increase in size in the cylinder axis direction around the cylinder head 33 can be prevented.
Therefore, the scooter type motorcycle 1 that is a straddle type vehicle that is particularly required to be downsized around the cylinder head 33 can be made suitable.

  As shown in FIGS. 3 and 14, the electromagnetic solenoid 75 has a plurality of mounting arm portions 77pr, 77qr, 77rr extending radially around the housing cases 77, 78 along the wall surface of the left side wall 100L of the cylinder head 33. In addition, since the plurality of attachment arm portions 77pr, 77qr, and 77rr are attached only to the cylinder head 33, the rigidity of the cylinder head 33 can be increased and the swelling of the electromagnetic solenoid 75 toward the head cover 34 can be further suppressed.

  In addition, since the electromagnetic solenoid 75 is attached only to the cylinder head 33 and not to the head cover 34, the head cover 34 can be removed without removing the electromagnetic solenoid 75 during maintenance of the valve train in the cylinder head 33. The maintenance work of the valve train can be facilitated.

  As shown in FIGS. 3 and 14, the mounting arm portion 77pr extending in the direction overlapping the spark plug center axis Cs when viewed in the cylinder axial direction among the plurality of mounting arm portions 77pr, 77qr, 77rr of the electromagnetic solenoid 75 Since a recess 77d that opens toward the spark plug 49 is formed so as to avoid the plug center axis Cs, the mounting arm portion is attached when the spark plug 49 is moved in the direction of the spark plug center axis Cs and is attached or detached. 77pr does not become a hindrance due to the recess 77d, and the maintainability of the spark plug 49 can be maintained well.

  As shown in FIG. 14, the cylinder head 33 includes rib portions 103pr, 103qr, 103rr and rib portions 103pr, 103pr, 103rr, which are in contact with mounting arm portions 77pr, 77qr, 77rr extending around the housing cases 77, 78. Since the mounting boss portions 103p, 103q, and 103r at the ends of 103qr and 103rr are formed to protrude, the electromagnetic solenoid 75 is stably attached to the cylinder head 33 by the rib portions 103pr, 103qr, and 103rr and the mounting boss portions 103p, 103q, and 103r. Retained.

  Further, since the mounting arm portions 77pr, 77qr, 77rr of the electromagnetic solenoid 75 are attached to the rib portions 103pr, 103qr, 103rr and the mounting boss portions 103p, 103q, 103r, the rib portions 103pr, 103qr, 103rr and the mounting boss portion are attached. The rigidity of 103p, 103q, and 103r can be maintained high, and the electromagnetic solenoid 75 can be supported more firmly.

  Since the housing cases 77, 78 and the mounting arm portions 77pr, 77qr, 77rr in the electromagnetic solenoid 75 are made of metal, the heat generated in the housing cases 77, 78 of the electromagnetic solenoid 75 is ribbed from the mounting arm portions 77pr, 77qr, 77rr. The portions 103pr, 103qr, and 103rr can be conducted, and the heat radiation efficiency of the electromagnetic solenoid 75 can be improved.

  Further, since the rib portions 103pr, 103qr, 103rr and the mounting boss portions 103p, 103q, 103r are formed to protrude from the wall surface of the left side wall 100L of the cylinder head 33, the rib portions 103pr, 103qr, 103rr and the mounting boss portions 103p, 103q are formed. , 103r abuts the mounting arm portions 77pr, 77qr, 77rr that protrude from the contact surface to form a space between the left wall 100L of the cylinder head (see FIG. 8) and run in this space. When the wind enters, the mounting arm portions 77pr, 77qr, and 77rr can be cooled, and the air cooling effect can be enhanced.

  As shown in FIGS. 10 and 14, an oil passage 133 is formed in the vicinity of the electromagnetic solenoid 75 in the left side wall 100L to which the electromagnetic solenoid 75 of the cylinder head 33 is attached. The solenoid 75 can be cooled effectively.

  The OHC type internal combustion engine 30 is mounted on the body frame of the scooter type motorcycle 1 which is a saddle type vehicle with a posture in which the cylinder axis Cc is largely tilted almost horizontally, and an electromagnetic solenoid 75 which is a source of pressure is a cylinder. Since it is attached to the wall surface of the left side wall 100L facing the vehicle width direction of the head 33 and the outer side in the vehicle width direction of the electromagnetic solenoid 75 is covered with a partial connection pipe 6 of the body frame, as shown in FIGS. The electromagnetic solenoid 75 is disposed between the cylinder head 33 and the connection pipe 6, and the cylinder head 33 and the connection pipe 6 can effectively protect the electromagnetic solenoid 75 from external factors.

  As shown in FIG. 2, the water pump 150 is attached to the wall surface of the right side wall 100R opposite to the wall surface of the left side wall 100L to which the electromagnetic solenoid 75 of the cylinder head 33 is attached. Since the 150 are attached to the side wall surfaces on both sides of the cylinder head 33 facing the vehicle width so as not to interfere with each other, the weight balance around the cylinder head 33 can be improved, and the electromagnetic solenoid 75 and the water pump 150 Even when both are attached to the cylinder head 33, the ignition plug 49 is attached to the left side wall 100L to which the electromagnetic solenoid 75 is attached as shown in FIG. Can be secured.

  As shown in FIG. 2, the head cover 34 is provided with a breather chamber 34b on the inner side, and an outlet 34c of the breather chamber 34b is formed on the outer wall surface of the head cover 34 with the opening toward the water pump 150 in the vehicle width direction. Therefore, the breather hose 146 connected to the outlet portion 34c of the breather chamber 34b in the head cover 34 and extending toward the water pump 150 does not interfere with the electromagnetic solenoid 75 on the opposite side, and is provided closer to the crankcase 31 than the electromagnetic solenoid 75. Interference with the water pump 150 used can be easily avoided.

DESCRIPTION OF SYMBOLS 1 ... Scooter type motorcycle, 4 ... Floor pipe, 5 ... Main pipe, 6 ... Connection pipe,
20 ... Power unit, 30 ... Internal combustion engine, 31 ... Crankcase, 32 ... Cylinder block, 33 ... Cylinder head, 34 ... Head cover, 34b ... Breather chamber, 49 ... Spark plug,
50 ... Valve mechanism, 54 ... Camshaft, 55 ... Intake rocker arm shaft, 56 ... Exhaust rocker arm shaft, 57 ... First intake rocker arm, 58 ... Second intake rocker arm, 59 ... Exhaust rocker arm, 61 ... First intake valve, 62 ... second intake valve, 63 ... first exhaust valve, 64 ... second exhaust valve,
70 ... Variable valve device, 71 ... Connection pin, 72 ... Connection release piston, 74 ... Push rod, 75 ... Electromagnetic solenoid, 76 ... Operating rod, 77 ... Accommodating case, 77a ... Cylinder part, 77b ... Bottom wall part, 77p , 77q, 77r ... mounting boss, 77pr, 77qr, 77rr ... mounting arm, 77d ... recessed,
100 ... outer peripheral wall, 100L ... left side wall, 100R ... right side wall, 101 ... spark plug mounting hole, 103p, 103q, 103r ... mounting boss part, 103pr, 103qr, 103rr ... rib part, 104p, 104q, 104r ... bolt,
131, 132, 133 ... oil passage, 146 ... breather hose,
150 ... Water pump.

Claims (11)

A cylinder block (32) and a cylinder head (33) are sequentially stacked on the crankcase (31) and fastened by a plurality of stud bolts (180) penetrating in the cylinder axial direction. The engine valve is placed inside the cylinder head (33). A plurality of rocker arms (57, 58) interlocking with (61, 62) are arranged so as to be swingably supported by a rocker arm shaft (55) adjacent to each other, and a head cover is mounted on the cylinder head (33). (34) is an OHC type internal combustion engine configured to be covered,
A connecting pin (71) that fits movably in the axial direction of the rocker arm shaft (55) in the adjacent rocker arm (57, 58) can swing the adjacent rocker arm (57, 58) integrally. It is provided so as to be movable between a coupling position to be coupled and a coupling release position that can swing independently of each other,
An OHC internal combustion engine provided with a pressing force transmission member (74, 76) for transmitting a pressing force of a pressing force generation source (75) disposed outside the cylinder head (33) to the movement of the connecting pin (71). In the variable valve system of the engine,
The pressing force source (75) is attached to the wall surface (100L) on which the ignition plug (49) of the cylinder head (33) is projected,
A housing case (77, 78) for housing the main body of the pressing force generation source (75) is provided at a position that does not overlap with the spark plug center axis (Cs) directed to the spark plug (49) when viewed in the cylinder axial direction. A variable valve operating apparatus for an OHC type internal combustion engine.   The variable valve operating system for an OHC type internal combustion engine according to claim 1, wherein the pressing force generation source (75) is located closer to the head cover (34) than the ignition plug (49).   The variable valve operating apparatus for an OHC type internal combustion engine according to claim 2, wherein the pressing force transmitting member (74, 76) is slidably provided on the cylinder head (33). The pressing force generation source (75) has a plurality of mounting arm portions (77pr, 77qr, 77rr) radially around the housing case (77, 78) along the wall surface (100L) of the cylinder head (33). Extended and formed
The variable valve operating system for an OHC type internal combustion engine according to claim 3, wherein the plurality of mounting arm portions (77pr, 77qr, 77rr) are mounted only on the cylinder head (33).   Of the plurality of mounting arm portions (77pr, 77qr, 77rr), the mounting arm portion (77pr) extending in a direction overlapping the spark plug central axis (Cs) when viewed in the cylinder axial direction is the spark plug central axis ( 5. A variable valve operating system for an OHC type internal combustion engine according to claim 4, wherein a recess (77d) is formed to open toward the spark plug (49) so as to straddle while avoiding Cs).   The cylinder head (33) is the same as the rib portion (103pr, 103qr, 103rr) with which the mounting arm portion (77pr, 77qr, 77rr) extending around the housing case (77, 78) is brought into contact. The mounting boss part (103p, 103q, 103r) at the end of the rib part (103pr, 103qr, 103rr) is formed to project, and the mounting arm part (77pr, 77qr, 77rr) is formed on the mounting boss part (103p, 103q, 103r). A variable valve operating apparatus for an OHC type internal combustion engine according to claim 4 or 5, wherein:   The housing case (77, 78) and the mounting arm portion (77pr, 77qr, 77rr) in the pressing force generation source (75) are made of metal. A variable valve operating apparatus for an OHC type internal combustion engine according to claim.   An oil passage (133) is formed in the vicinity of the pressing force generation source (75) on the side wall (100L) to which the pressing force generation source (75) of the cylinder head (33) is attached. The variable valve operating apparatus for an OHC type internal combustion engine according to any one of claims 4 to 6. The OHC type internal combustion engine (30) is mounted on the body frame of the saddle-ride type vehicle (1) in a posture in which the cylinder axis (Cc) is largely inclined to near horizontal.
The pressing force generation source (75) is attached to the side wall surface (100L) facing the vehicle width direction of the cylinder head (33),
9. The OHC type internal combustion engine according to claim 1, wherein an outer side in the vehicle width direction of the pressing force generation source is covered with a part of the vehicle body frame. Variable valve device.   The water pump (150) is attached to the side wall surface (100R) opposite to the side wall surface (100L) to which the pressing force generation source (75) of the cylinder head (33) is attached. The variable valve operating device for the OHC type internal combustion engine. The water pump (150) is disposed closer to the crankcase than the pressing force generation source (75) in the cylinder axial direction,
The head cover (34) is provided with a breather chamber (34b) inside,
The outlet portion (34c) of the breather chamber (34b) is formed on the outer wall surface of the head cover (34) with the opening facing the water pump (150) in the vehicle width direction. The variable valve operating apparatus for an OHC type internal combustion engine according to claim 10.

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