Structure for lubricating cam shaft in multi-cylinder engine

Abstract

To provide a multi-cylinder engine in which cam shaft linked with a plurality of intake valves and a plurality of exhaust valves for carrying out intake and exhaust operations for a plurality of combustion chambers is rotatably supported by cam bearing portions provided on the cylinder head and a cam holder fastened to the cam bearing portions. An oil passage capable of supplying oil from an oiling passage provided in the cylinder head is formed in the cam shaft. Oil can be supplied in the oil passage in the cam shaft without restriction in the location of fastening bolts for fastening the cylinder head to the cylinder block. An oiling hole is provided in the cam shaft in such a manner as to be in communication with the oil passage, and an oil groove in communication with the outer end of the oiling hole is formed in a cam bearing portion, provided in the cylinder head, at a position corresponding to one of combustion chambers, in such a manner as to face toward the outer surface of the cam shaft. Furthermore, the oiling passage is in communication with the oil groove.

Description

BACKGROUND OF THE INVENTION

1. Field of the Invention

The present invention relates to a multi-cylinder engine in which a plurality of combustion chambers are formed between a cylinder head fastened to a cylinder block including a plurality of cylinder bores and pistons slidably fitted in the plurality of cylinder bores. A cam shaft linked with a plurality of intake valves and a plurality of exhaust valves for carrying out intake and exhaust operations for the combustion chambers is rotatably supported at a plurality of locations spaced in the axial line direction of said cam shaft by cam bearing portions provided on the cylinder head and a cam holder fastened to the cam bearing portions. Furthermore, an oil passage capable of supplying oil from an oiling passage provided in the cylinder head is formed in the cam shaft. In particular, the present invention relates to a structure for supplying oil from a cylinder head into an oil passage formed in a cam shaft.

2. Description of Related Art

In a conventional multi-cylinder engine, an oil groove for supplying oil into an oil passage in a cam shaft is generally provided in a can bearing portion for supporting one end portion of the cam shaft in the axial direction. The cam bearing portion is disposed outside of the outermost one of a plurality of combustion chambers disposed in the axial line direction of the cam shaft.

A cylinder head is fastened to a cylinder block using fastening bolts disposed at a plurality of locations other than portions corresponding to a plurality of combustion chambers. To shorten the length of the cylinder head in the axial line direction of a cam shaft, it may be desirable to make the fastening bolt disposed outside the outermost combustion chamber as close to the outermost combustion chamber as possible. If the fastening bolt can be disposed in a portion corresponding to a cam bearing portion outside the outermost combustion chamber, the length of the cylinder head can be shortened. However, since an oil groove is generally provided in the above cam bearing portion disposed outside the outermost combustion chamber as described above, it is difficult to dispose the fastening bolt in the portion corresponding to the above cam bearing portion without interference with the oil groove

SUMMARY OF THE INVENTION

In view of the foregoing, the present invention has been made, and a first object of the present invention is to provide a structure for lubricating a cam shaft in a multi-cylinder engine, which is capable of supplying oil in an oil passage formed in the cam shaft while avoiding restriction in location of fastening bolts for fastening the cylinder head to the cylinder block.

On the other hand, in a multi-cylinder engine in which a transmission mechanism is provided between the cam shaft and the crank shaft, if an oil groove is provided in a cam bearing portion between the combustion chamber closest to the transmission mechanism and the transmission mechanism, a fastening bolt is disposed between the cam bearing portion and the transmission mechanism or between the cam bearing portion and the combustion chamber. With this configuration, a gap between the combustion chamber and the transmission mechanism must be made relatively large. This is inconvenient, since the length of the cylinder head becomes longer in the axial line direction of the cam shaft.

Accordingly, a second object of the present invention is to provide a structure for lubricating a cam shaft in a multi-cylinder engine, which is capable of making the length of a cylinder head in the axial direction of the cam shaft as short as possible, and supplying oil in an oil passage formed in the cam shaft.

To achieve the first object, according to a first aspect of the present invention, there is provided a structure for lubricating a cam shaft in a multi-cylinder engine. The multi-cylinder engine is configured such that a plurality of combustion chambers are formed between the cylinder head fastened to the cylinder block including a plurality of cylinder bores and pistons slidably fitted in the plurality of cylinder bores. A cam shaft linked with a plurality of intake valves and a plurality of exhaust valves for carrying out intake and exhaust operations for the combustion chambers is rotatably supported at a plurality of locations spaced in the axial line direction of the cam shaft by cam bearing portions provided on the cylinder head and a cam holder fastened to the cam bearing portions. Furthermore, an oil passage capable of supplying oil from an oiling passage provided in the cylinder head is formed in the cam shaft. The lubricating structure includes an oiling hole provided in the cam shaft in communication with the oil passage, and an oil groove in communication with the outer end of the oiling hole is formed in one of the cam bearing portions provided in the cylinder head at a position corresponding to one of the combustion chambers in such a manner as to face toward the outer surface of the cam shaft. Furthermore, the oiling passage is in communication with the oil groove.

With this configuration, since none of the fastening bolts are disposed at a portion corresponding to the combustion chamber, by forming the oil groove in the cam bearing portion provided on the cylinder head at a position corresponding to one of the plurality of combustion chambers, it is possible to supply oil in the oil passage formed in the cam shaft without restricting the location of the fastening bolts.

To achieve the above second object, according to a second aspect of the present invention, there is provided a structure for lubricating a cam shaft in a multi-cylinder engine. The multi-cylinder engine is configured such that a plurality of combustion chambers are formed between the cylinder head fastened to the cylinder block including a plurality of cylinder bores and pistons slidably fitted in the plurality of cylinder bores. A cam shaft linked with a plurality of intake valves and a plurality of exhaust valves for carrying out intake and exhaust operations for the combustion chambers is rotatably supported at a plurality of locations spaced in the axial line direction of the cam shaft by cam bearing portions provided on the cylinder head and a cam holder fastened to the cam bearing portions. A transmission mechanism for reducing the rotational power of the crank shaft to half and transmitting the reduced rotational power to the cam shaft is provided between the crank shaft and the cam shaft. Furthermore, an oil passage capable of supplying oil from an oiling passage provided in the cylinder head is formed in the cam shaft. The lubricating structure includes a through-hole, into which one of fastening bolts for fastening the cylinder head to the cylinder block is to be inserted, is provided in one of the cam bearing portions. This cam bearing portion is provided in the cylinder head at a position between the transmission mechanism and the combustion chamber closest to the transmission mechanism disposed in the axial direction of the cam shaft. Furthermore, an oiling hole is provided in the cam shaft in communication with the oil passage, and an oil groove in communication with an outer end of the oiling hole is provided in another one of the plurality of the cam bearing portions adjacent to the above cam bearing portion in such a manner as to face toward the outer surface of the cam shaft. The oiling passage is in communication with the oil groove.

With this configuration, the though-hole into which the fastening bolt is to be inserted is provided in one cam bearing portion between the combustion chamber closest to the transmission mechanism and the transmission mechanism, and the oil groove is provided in another cam bearing portion adjacent to the above one cam bearing portion, so that the fastening bolt between the transmission mechanism and the combustion chamber is made as close to the combustion chamber as possible. This makes it possible to shorten the length of the cylinder head in the axial line, direction of the cam shaft.

According to a third aspect of the present invention, in addition to the configuration of the second aspect of the present invention, a plurality of cylinder bore rows, each of which includes a plurality of cylinder bores spaced at equal intervals in the axial line direction of the crank shaft, cross each other at an angle within a plane perpendicular to the axial line of the crank shaft and are offset from each other in the axial line direction of the crank shaft. The plurality of transmission mechanisms corresponding to the cylinder bore rows are disposed in such a manner that a gap between the transmission mechanisms is smaller than a mutual offset amount between the cylinder bore rows. The cam bearing portion in which the through-hole is formed is set in accordance with at least one of the transmission mechanisms.

With this configuration, it is possible to set the gap between the transmission mechanisms at a small value, and hence to further shorten the length of the engine in the axial line direction of the cam shaft.

According to a fourth aspect of the present invention, in addition to the configuration of the third aspect of the present invention, each of the plurality of transmission mechanisms is provided between one end portion of the crank shaft and an associated one of the cam shafts. With this configuration, it is possible to more freely set a gap between the transmission mechanisms.

According to a fifth aspect of the present invention, in addition to the configuration of the fourth aspect of the present invention, one transmission mechanism is disposed at the outermost end on one end side of the cam shafts, and two of the plurality of cam bearing portions provided in the cam shaft to which the one transmission mechanism is connected have a through-hole and an oil groove, respectively. With this configuration, it is possible to shorten the distance between the transmission mechanism and the combustion chamber, and hence to effectively shorten the length of the multi-cylinder engine in the axial line direction of the cam shaft.

Further scope of applicability of the present invention will become apparent from the detailed description given hereinafter. However, it should be understood that the detailed description and specific examples, while indicating preferred embodiments of the invention, are given by way of illustration only, since various changes and modifications within the spirit and scope of the invention will become apparent to those skilled in the art from this detailed description.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention will become more fully understood from the detailed description given hereinbelow and the accompanying drawings which are given by way of illustration only, and thus are not limitative of the present invention, and wherein:

FIG. 1 is a side view of a horizontally-opposed type engine mounted on a motorcycle;

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

FIG. 3 is an enlarged sectional view taken on line 3 — 3 of FIG. 1 ;

FIG. 4 is a sectional view taken on line 4 — 4 of FIG. 3 ;

FIG. 5 is an enlarged view taken on line 5 — 5 of FIG. 4 ;

FIG. 6 is an enlarged view taken on line 6 — 6 of FIG. 4 ;

FIG. 7 is an enlarged sectional view taken on line 7 — 7 of FIG. 4 ;

FIG. 8 is an enlarged view taken on line 8 — 8 of FIG. 4 ;

FIG. 9 is an enlarged sectional view taken on line 9 — 9 of FIG. 4 ;

FIG. 10 is a sectional view taken on line 10 — 10 of FIG. 8 ;

FIG. 11 is a sectional view taken on line 11 — 11 of FIG. 3 ;

FIG. 12 is a sectional view taken on line 12 — 12 of FIG. 11 ;

FIG. 13 is a schematic view from the rear side of a mission case; and

FIG. 14 is an enlarged sectional view taken on line 14 — 14 of FIG. 13 .

DESCRIPTION OF THE PREFERRED EMBODIMENTS

Hereinafter, one embodiment of the present invention will be described with reference to the accompanying drawings.

FIGS. 1 to 14 show one embodiment of the present invention. Referring first to FIGS. 1 and 2 , a four-cycle/multi-cylinder (e.g., six-cylinder) horizontally-opposed type engine is mounted on a motorcycle. An engine main body E of the engine includes a left engine block B L disposed on the left side when the motorcycle is directed forwardly in the running direction thereof, and a right engine block B R disposed on the right side in when the motorcycle is directed forwardly in the running direction thereof.

Referring particularly to FIGS. 3 and 4 , the left engine block B L includes a left cylinder block 23 L and a left cylinder head 24 L connected to the left cylinder block 23 L . The left cylinder block 23 L has a left side cylinder bore row 22 L including a plurality (e.g., three) of cylinder bores 21 L disposed in parallel. The left cylinder head 24 L has combustion chambers 26 L each of which is formed between the associated one of the cylinder bores 21 L and a piston 25 L slidably fitted in the cylinder bore 21 L . A left crank case 27 L is formed integrally with the side, opposed to the left cylinder head 24 L , of the cylinder block 23 L . The right engine block B R includes a right cylinder block 23 R and a right cylinder head 24 R connected to the right cylinder block 23 R . The right cylinder block 23 R has a right side cylinder bore row 22 R including a plurality (e.g., three) of cylinder bores 21 R disposed in parallel. The right cylinder head 24 R has combustion chambers 26 R each of which is formed between the associated one of the cylinder bores 21 R and a piston 25 R slidably fitted in the cylinder bore 21 R . A right crank case 27 R is formed integrally with the side, opposed to the right cylinder head 24 R , of the cylinder block 23 R .

The left and right engine blocks B L and B R are opposed to each other with the axial lines of the cylinder bores 21 L and 21 R directed substantially in the horizontal direction. The left crank case 27 L of the left engine block B L is fastened to the right crank case 27 R of the right engine block B R in such a manner as to form a crank chamber 28 therebetween.

The pistons 25 L and 25 R in the left and right engine blocks B L and B R are commonly connected to a crank shaft 29 via connecting rods 30 L and 30 R , respectively. The crank shaft 29 is disposed such that one end side is located on the front side of the motorcycle in the longitudinal direction of the motorcycle and the axial line of the crank shaft 29 extends in the longitudinal direction of the motorcycle. The crank shaft 29 is supported by one of the left and right crank cases 27 L and 27 R (left crank case 27 L in this embodiment). To be more specific, the crank shaft 29 is rotatably supported by journal walls 31 integrally formed on the left crank case 27 L at a plurality of locations spaced in the axial direction of the crank shaft 29 . Furthermore, bearing caps 32 are fastened to the journal walls 31 with a pair of bolts 33 , respectively.

Each of the cylinder bores 21 R constituting the cylinder bore row 22 R on the right engine block B R side is offset forwardly in the longitudinal direction of the motorcycle from the associated one of the opposed cylinder bores 21 L constituting the cylinder bore row 22 L on the left engine block B L side by a first offset amount L 1 .

Referring particularly to FIGS. 5 , 6 and 7 , the left cylinder head 24 L includes pairs of intake passages 34 L and exhaust passages 35 L communicating with the combustion chambers 26 L . Each pair of the intake passages 34 L and the exhaust passages 35 L are provided for the associated one of the combustion chambers 26 L . The left cylinder head 24 L also includes intake valves 36 L each being adapted to open/close the associated one of the intake passages 34 L and exhaust valves 37 L each being adapted to open/close the associated one of the exhaust passages 35 L .

The intake valves 36 L and the exhaust valves 37 L , which extend in the direction parallel to the axial line of the crank shaft 29 , are offset upwardly from a plane 38 L passing through the axial lines of the cylinder bores 21 L and the axial line of the crank shaft 29 in such a manner that the exhaust valves 37 L are offset forwardly from the intake valves 36 L in the longitudinal direction of the motorcycle. The left cylinder head 24 L also includes ignition plugs 39 L facing toward the central portion of an associated one of the combustion chambers 26 L at a position located between an associated one of the pairs of the intake valves 36 L and exhaust valve 37 L on an opposite side from the disposition side of the intake valves 36 L and the exhaust valves 37 L with respect to the plane 38 L . In other words, the ignition plugs are located on the lower side of the plane 38 L .

Each of the intake valves 36 L and the exhaust valves 37 L is mounted to the left cylinder head 24 L in such a manner as to be tilted at an acute angle with respect to the plane 38 L . On the opposite side from the disposition side of the intake valves 36 L and the exhaust valves 37 L with respect to the plane 38 L , i.e., on the lower side of the plane 38 L , the left cylinder head 24 L has plug mounting holes 40 L for mounting the ignition plugs 39 L in a state where the ignition plugs 39 L are tiled at an acute angle with respect to the plane 38 L . In other words, the ignition plugs 39 L are mounted to the left cylinder head 24 L in such a manner as to be tilted downwardly with respect to the plane 38 L .

On the projection chart crossing the axial lines of the cylinder bores 21 L at right angles, the intake passages 34 L are provided in the left cylinder head 24 L in such a manner as to cross the plane 38 L substantially at right angles, and are opened to one side surface of the left cylinder head 24 L on the disposition side of the intake valves 36 L and the exhaust valves 37 L with respect to the plane 38 L , i.e., on the upper side of the plane 38 L . The exhaust passages 35 L are opened to the other side surface of the left cylinder head 24 L on an opposite side from the disposition side of the intake valves 36 L and the exhaust valves 37 L with respect to the plane 38 L , i.e., on the lower side of the plane 38 L . To be more specific, the exhaust passages 35 L are curved to be swelled toward one end side of the crank shaft 29 or the front side of the motorcycle in order to bypass the ignition plugs 39 L , that is, the plug mounting holes 40 L for mounting the ignition plugs 39 L .

Each of the exhaust passages 35 L is formed in such a manner as to be tilted downwardly toward the central portion of the motorcycle in the width direction and to be opened to the other side surface, i.e., the lower surface of the left cylinder head 24 L . An exhaust system 43 L is provided which is composed exhaust pipes 41 L each of which is in communication with an associated one of the exhaust passages 35 L , a catalyst converter 42 , an exhaust muffler (not shown), and the like. Each of the exhaust pipes 41 L of the exhaust system 43 L is tilted such that it is closer to the central portion of the motorcycle in the width direction since it is separated apart downwardly from the left cylinder head 24 L , and is connected to an opening at the outer end of the associated one of the exhaust passages 35 L .

The center of the opening at the outer end of each exhaust passage 35 L is offset forwardly in the longitudinal direction of the motorcycle from a center C L of an associated one of the combustion chambers 26 L by a second offset amount L 2 .

A single cam shaft 46 L , which is in parallel to the crank shaft 29 and has an axial line perpendicular to the opening/closing operational lines of the intake valves 36 L and the exhaust valves 37 L , is disposed on the disposition side of the intake valves 36 L and the exhaust valves 37 L with respect to the plane 38 L . In other words, the single cam shaft 46 L is on the upper side of the plane 38 L . On the other hand, the upper ends of the intake valves 36 L and the exhaust valves 37 L biased in the valve closing direction, i.e., upwardly, by springs are in contact with valve lifters 47 L which are supported by the left cylinder head 24 L slidably in the direction of the operational axial lines of the valves 36 L and 37 L . The cam shaft 46 L includes intake side cams 48 L in contact with the valve lifters 47 L associated with the intake valves 36 L . Exhaust side cams 49 L are in contact with the valve lifters 47 L associated with the exhaust valves 37 L . In other words, the intake valves 36 L and the exhaust valves 37 L are directly opened/closed by the intake side cams 48 L and the exhaust side cams 49 L of the cam shaft 46 L , respectively.

A plurality (for example, four) of portions, spaced in the axial line direction, of the cam shaft 46 L are rotatably supported by cam bearing portions 50 L provided on the left cylinder head 24 L and a cam holder 51 L commonly fastened to the cam bearing portions 50 L . Of the four cam bearing portions 50 L , three are each provided on the left cylinder head 24 L in such a manner as to be disposed between a pair of the intake valves 36 L and the exhaust valves 37 L provided for each combustion chamber 26 L . The remaining cam bearing portion 50 L is provided on the left cylinder head 24 L in such a manner as to be located outside of the combustion chamber 26 L disposed at the outermost end on one end side of the cam shaft 46 L (front end side of the motorcycle).

An oil passage 52 L having both ends closed is coaxially provided in the cam shaft 46 L . As shown in FIG. 3 , the cam shaft 46 L has oiling holes 53 L at positions corresponding to the cam bearing portions 50 L . The oiling holes 53 L are formed in such a manner as to extend from the inside to the outside of the cam shaft 46 L . Accordingly, lubricating oil is supplied from the interior of the cam shaft 46 L to the cam bearing portions 50 L and the cam holder 51 L . Furthermore, an oil groove 54 L facing to the outer surface of the cam shaft 46 L is provided in the cam bearing portion 50 L disposed at the outermost end on one end side of the cam shaft 46 L , and an oiling passage 55 L provided in the left cylinder head 24 L and the left cylinder block 23 L is in communication with the oil groove 54 L . Accordingly, oil is supplied from the oiling passage 55 L into the oil passage 52 L in the cam shaft 46 L via the oil groove 54 L and the oiling hole 53 L .

Each of the intake side cams 48 L and the exhaust side cams 49 L has an oiling hole (not shown) communicating with the oil passage 52 L in the cam shaft 46 L . The outer end of the oiling hole is opened to the outer surface of an associated one of the intake side cams 48 L and the exhaust side cams 49 L . Accordingly, lubricating oil is also supplied to a slide-contact portion between each of the intake side cams 48 L and the exhaust side cams 49 L and the valve lifters 47 L provided for each of the intake valves 36 L and the exhaust valves 37 L .

The left cylinder head 24 L is fastened at a plurality of locations to the left cylinder block 23 L . On the opposite side from the disposition side of the intake valves 36 L and the exhaust valves 37 L with respect to the plane 38 L , i.e., on the lower side of the plane 38 L , the left cylinder head 24 L has a plurality (for example, four) of through-holes 56 L spaced in the axial line direction of the cam shaft 46 L . Of the four through-holes 56 L , two are each disposed between adjacent ones of the combustion chambers 26 L . Fastening bolts 57 L for fastening the left cylinder head 24 L to the left cylinder block 23 L are inserted in the through-holes 56 L .

Each through-hole 56 L is adjacent, on one end side (left side in FIG. 7 ) of the cam shaft 46 L , to an associated one of the exhaust passages 35 L bypassing the ignition plugs 39 L provided for the combustion chambers 26 L . The through-hole 56 L has a positional relationship such that a distance L 4 between a center of the through-hole 56 L and a center C L of the associated combustion chamber 26 L is larger than a value L 3 (L 3 <L 4 ) . The value L 3 is half a distance (2L 3 ) between the centers C L of adjacent ones of the combustion chambers 26 L .

On the disposition side of the intake valves 36 L and the exhaust valves 37 L with respect to the plane 38 L , i.e., on the upper side of the plane 38 L , the left cylinder head 24 L has a plurality (for example, four) of through-holes 58 L spaced in the axial line direction of the cam shaft 46 L . Of the four through-holes 58 L , two are each disposed between adjacent ones of the combustion chambers 26 L . Fastening bolts 59 L for fastening the left cylinder head 24 L to the left cylinder block 23 L are inserted in the through-holes 58 L . Each through-hole 58 L , i.e., fastening bolt 59 L is disposed at a position where it is partially covered by the cam shaft 46 L .

A left head cover 60 L is fastened to the left cylinder head 24 L in such a manner that a valve system chamber 61 L for containing the cam shaft 46 L and the cam holder 51 L is formed between the left head cover SO L and the left cylinder head 24 L . Since the cam shaft 46 L is disposed upwardly from the plan 38 L containing the axial lines of the cylinder bores 21 L , the valve system chamber 61 L is also formed between the left head cover SO L and the left cylinder head 24 L in such a manner as to be offset upwardly from the plane 38 L .

A cover portion 62 L is formed integrally with the left head cover 60 L . Portions of the exhaust pipes 41 L of the exhaust system 43 L connected to the exhaust passages 35 L , and the ignition plugs 39 L disposed downwardly therefrom are covered from the outside by the cover portion 62 L .

Referring particularly to FIGS. 8 and 9 , the right cylinder head 24 R includes pairs of intake passages 34 R and exhaust passages 35 R communicating with the combustion chambers 26 R , each pair being provided for an associated one of the combustion chambers 26 R . The right cylinder head 24 R also includes intake valves 36 R each being adapted to open/close an associated one of the intake passages 34 R and exhaust valves 37 R each being adapted to open/close the associated one of the exhaust passages 35 R .

The intake valves 36 R and the exhaust valves 37 R , which extend in the direction parallel to the axial line of the crank shaft 29 , are offset upwardly from a plane 38 R passing through the axial lines of the cylinder bores 21 R and the axial line of the crank shaft 29 in such a manner that the exhaust valves 37 R are offset forwardly from the intake valves 36 R in the longitudinal direction of the motorcycle. Ignition plugs 39 R , each of which faces to the central portion of an associated one of the combustion chambers 26 R , are mounted to the right cylinder head 24 R on a lower side of the plane 38 R .

Each of the intake valves 36 R and the exhaust valves 37 R is tilted at an acute angle with respect to the plane 38 R . On the lower side from the plane 38 R , the right cylinder head 24 R has plug mounting holes 40 R for mounting the ignition plugs 39 R in a state where the ignition plugs 39 R are tilted at an acute angle with respect to the plane 38 R . The ignition plugs 39 R are thus mounted to the right cylinder head 24 R in such a manner as to be tilted downwardly with respect to the plane 38 R .

On the projection chart crossing the axial lines of the cylinder bores 21 R at right angles, the intake passages 34 R are provided in the right cylinder head 24 R in such a manner as to cross the plane 38 R substantially at right angles, and are opened to one side surface of the right cylinder head 24 R on the upper side of the plane 38 R . The exhaust passages 35 R are opened to the other side surface of the right cylinder head 24 R on the lower side from the plane 38 R . To be more specific, the exhaust passages 35 R are curved to be swelled toward one end side of the crank shaft 29 in the axial direction or the front side of the motorcycle in order to bypass the ignition plugs 39 R , that is, the plug mounting holes 40 R .

Each of the exhaust passages 35 R is formed in such a manner as to be tilted downwardly toward the central portion of the motorcycle in the width direction and to be opened to the lower surface of the right cylinder head 24 R . An exhaust system 43 R is provided which is composed of exhaust pipes 41 R , each of which is in communication with an associated one of the exhaust passages 35 R , a catalyst converter (not shown), an exhaust muffler (not shown), and the like. Each of the exhaust pipes 41 R of the exhaust system 43 R is tilted in such a manner as to be closer to the central portion of the motorcycle in the width direction since being separated apart downwardly from the right cylinder head 24 R , and is connected to an opening at the outer end of the associated one of the exhaust passages 35 R .

The center of the opening at the outer end of each exhaust passage 35 R is offset forwardly in the longitudinal direction of the motorcycle from a center C R of an associated one of the combustion chambers 26 R by the second offset amount L 2 .

The upper ends of the intake valves 36 R and the exhaust valves 37 R biased in the valve closing direction by springs are in contact with valve lifters 47 R supported by the right cylinder head 24 R . Intake side cams 48 R are in contact with the valve lifters 47 R associated with the intake valves 36 R and exhaust side cams 49 R are in contact with the valve lifters 47 R associated with the exhaust valves 37 R . The intake side cams 48 R are provided on a single cam shaft 46 R which is disposed on the upper side of the plane 38 R . The cam shaft 46 R is in parallel to the crank shaft 29 and has an axial line perpendicular to the opening/closing operational axial lines of the intake valves 36 R and the exhaust valves 37 R . In other words, the intake valves 36 R and the exhaust valves 37 R are directly opened/closed by the intake side cams 48 R and the exhaust side cams 49 R of the cam shaft 46 R , respectively.

A plurality (for example, four) of portions, spaced in the axial line direction, of the cam shaft 46 R are rotatably supported by cam bearing portions 50 R provided on the right cylinder head 24 R and a cam holder 51 R commonly fastened to the cam bearing portions 50 R . Of the four cam bearing portions 50 R , three are each provided on the right cylinder head 24 R in such a manner as to be disposed between the pair of the intake valves 36 R and the exhaust valves 37 R provided for each combustion chamber 26 R , and the remaining cam bearing portion 50 R is provided on the right cylinder head 24 R in such a manner as to be located outside the combustion chamber 26 R disposed at the outermost end on one end side of the cam shaft 46 R (front end side of the motorcycle).

As shown in FIG. 3 , the cam shaft 46 R has oiling holes 53 R at positions corresponding to the cam bearing portions 50 R . The oiling holes 53 R are formed in such a manner as to extend from an inside to an outside of the cam shaft 46 R . Lubricating oil is supplied from an oil passage 52 R formed in the cam shaft 46 R to the cam bearing portions 50 R and the cam holder 51 R via the oiling holes 53 R . Furthermore, an oil groove 54 R facing to the outer surface of the cam shaft 46 R is provided in the second cam bearing portion 50 R from the outermost end on one end side of the cam shaft 46 R , and an oiling passage 55 R provided in the right cylinder head 24 R and the right cylinder block 23 R is in communication with the oil groove 54 R .

Each of the intake side cams 48 R and the exhaust side cams 49 R has an oiling hole (not shown) in communication with the oil passage 52 R in the cam shaft 46 R . Lubricating oil is thus also supplied to a slide-contact portion between each of the intake side cams 48 R and the exhaust side cams 49 R and an associated one of the valve lifters 47 R provided for each of the intake valves 36 L and the exhaust valves 37 L .

On the lower side of the plane 38 R , the right cylinder head 24 R has a plurality (for example, four) of through-holes 56 R which are spaced in the axial line direction of the cam shaft 46 R . Of the four through-holes 56 R , two are each disposed between adjacent ones of the combustion chambers 26 R . Fastening bolts 57 R for fastening the right cylinder head 24 R to the right cylinder block 23 R are inserted in the through-holes 57 R .

Each through-hole 56 R is adjacent, on one end side (right side in FIG. 9 ) of the cam shaft 46 R , to an associated one of the exhaust passages 35 R bypassing the ignition plugs 39 R provided for the combustion chambers 26 R . The through-hole 56 R has a positional relationship such that a distance L 4 between a center of the through-hole 56 R and a center C R of the associated combustion chamber 26 R is larger than a value L 3 (L 3 <L 4 ). The value L 3 is half a distance between the centers C R of adjacent ones of the combustion chambers 26 R .

On the upper side of the plane 38 R , the right cylinder head 24 R has a plurality (for example, four) of through-holes 58 R spaced in the axial line direction of the cam shaft 46 R . Of the four through-holes 58 R , two are each disposed between adjacent ones of the combustion chambers 26 R . Fastening bolts 59 R for fastening the right cylinder head 24 R to the right cylinder block 23 R are inserted in the through-holes 58 R . Each through-hole 58 R , that is, fastening bolt 59 R is disposed at a position where it is partially covered by the cam shaft 46 R .

Referring particularly to FIG. 10 , of the plurality (for example, four) of the through-holes 58 R , the through-hole 58 R disposed at the outermost end on one end side of the cam shaft 46 R is provided in the cam bearing portion 50 R , disposed at the outermost end on the one end side of the cam shaft 46 R , of the four cam bearing portions 50 R . The oil groove 54 R is provided in the cam bearing portion 50 R adjacent to the above-described cam bearing portion 50 R disposed at the outermost end on the one end side of the cam shaft 46 R .

Furthermore, a distance L 5 between a center of the through-hole 58 R disposed at the outermost end on the one end side of the cam shaft 46 R and the center C R of the combustion chamber 26 R disposed at the outermost end on the one end side of the cam shaft 46 R is set to be smaller than the value L 3 (L 5 <L 3 ). The value L 3 is, as described above, half the distance between the centers C R of adjacent ones of the combustion chambers 26 R .

A right head cover 60 R is fastened to the right cylinder head 24 R in such a manner that a valve system chamber 61 R for containing the cam shaft 46 R and the cam holder 51 R is formed between the right head cover 60 R and the right cylinder head 24 R . The valve system chamber 61 R is formed between the right head cover 60 R and the right cylinder head 24 R in such a manner as to be offset upwardly from the plane 38 R .

A cover portion 62 R is formed integrally with the right head cover 60 R . Portions of the exhaust pipes 41 R of the exhaust system 43 R connected to the exhaust passages 35 R , and the ignition plugs 39 R disposed downwardly therefrom are covered from the outside by the cover portion 62 R .

With respect to the intake passages 34 L and the exhaust passages 35 L provided in the left cylinder head 24 L and the intake passages 34 R and the exhaust passages 35 R provided in the right cylinder head 24 R as described above, the relative positional relationship between the intake passages 34 L and the exhaust passages 35 L along the axial line direction of the crank shaft 29 in the left cylinder head 24 L is set to be nearly equal to the relative positional relationship between the intake passages 34 R and the exhaust passages 35 R along the axial line direction of the crank shaft 29 in the right cylinder head 24 R .

A throttle body 63 , an intake manifold 64 and an intake system 66 including fuel injection valves 65 provided for each of the combustion chambers 26 L and 26 R are disposed over a location between both of the cylinder heads 24 L and 24 R . The intake manifold 64 is connected to the intake passages 34 L and 34 R of both of the cylinder heads 24 L and 24 R .

Secondary air supply passages 44 L each of which is in communication with the exhaust passage 35 L are provided in the cylinder head 24 L and the cylinder block 23 L of the left engine block B L , and secondary air supply passages 44 R each of which is in communication with the exhaust passage 35 R are provided in the cylinder head 24 R and the cylinder block 23 R of the right engine block B R . The secondary air supply passages 44 L are connected to control valves (not shown) via check valves 45 provided in the cylinder block 23 L , and the secondary air supply passages 44 R are similarly connected to control valves (not shown) via check valves 45 provided in the cylinder block 23 R .

Referring particularly to FIG. 11 , a transmission mechanism 68 L is provided between one end portion of the cam shaft 46 L on the left engine block B L side and one end portion of the crank shaft 29 . The transmission mechanism 68 L is adapted to reduce a rotational power of the crank shaft 29 to half and transmit the reduced rotational power to the cam shaft 46 L . A transmission mechanism 68 R is provided between one end portion of the cam shaft 46 R on the right engine block B R side and one end portion of the crank shaft 29 . The transmission mechanism 68 R is adapted to reduce a rotational power of the crank shaft 29 to half and transmit the reduced rotational power to the cam shaft 46 R .

The transmission mechanism 68 L (or 68 R ) is configured such that an endless chain 71 L (or 71 R ) is wound around a drive sprocket 69 L (or 69 R ) fixed on the one end portion of the crank shaft 29 and a driven sprocket 70 L (or 70 R ) fixed on the one end portion of the cam shaft 46 L (or 46 R ). As described above, each of the cylinder bores 21 R constituting the cylinder bore row 22 R on the right engine block B R side is offset forwardly in the longitudinal direction of the motorcycle from each of the cylinder bores 21 L constituting the cylinder bore row 22 L on the left engine block B L side by the first offset amount L 1 . Correspondingly, the transmission mechanism 68 R on the right engine block B R side is offset forwardly in the longitudinal direction of the motorcycle from the transmission mechanism 68 L on the left engine block B L side. In this case, a gap L 6 between both the transmission mechanisms 68 L and 68 R is set to be smaller than the first offset amount 1 (L 6 <L 1 ) .

A transmission chamber 72 L for containing the transmission mechanism 68 L is formed in the front end portion of the left engine block B L along the longitudinal direction of the motorcycle in such a manner as to extend from the head cover 60 L to the crank case 27 L by way of the cylinder head 24 L and the cylinder block 23 L . To be more specific, one end of the transmission chamber 72 L faces the valve system chamber 61 L and the other end thereof faces the crank shaft 29 . Similarly, a transmission chamber 72 R for containing the transmission mechanism 68 R is formed in the front end portion of the right engine block B R along the longitudinal direction of the motorcycle in such a manner as to extend from the head cover 60 R to the crank case 27 R by way of the cylinder head 24 R and the cylinder block 23 R . To be more specific, one end of the transmission chamber 72 R faces the valve system chamber 61 R and the other end thereof faces one end of the crank shaft 29 . Accordingly, the other end portions of both the transmission chambers 72 L and 72 R are commonly formed in such a manner as to face the one end of the crank shaft 29 . An opening 73 facing to the other end portions of both the transmission chambers 72 L and 72 R is provided in the left and right crank cases 27 L and 27 R , and is covered with a lid member 74 fastened to the left and right crank cases 27 L and 27 R .

In a space on the other end side of the transmission chambers 72 L and 72 R , a pulse rotor 75 is fixed to the one end portion of the crank case 29 at a position outside both of the sprockets 68 L and 68 R . A sensor 76 facing to the outer periphery of the pulse rotor 75 is mounted on one of the left and right crank cases 27 L and 27 R (left crank case 27 L in this embodiment). The sensor 76 is adapted to detect the passing of teeth provided on the outer periphery of the pulse rotor 75 . In this way, the rotational position of the crank shaft 29 is detected by the sensor 76 .

A pulse rotor 77 is fixed to the one end portion of one of the cam shafts 46 L and 46 R (cam shaft 46 L in this embodiment) at a position outside the driven sprocket 70 L . A sensor (not shown) for detecting the rotational position of the cam shaft 46 L is mounted to the left cylinder head 24 L in such a manner as to face the outer periphery of the pulse rotor 77 .

The crank shaft 29 is rotated in the rotational direction shown by an arrow 78 in FIG. 11 . At the left side transmission mechanism 68 L , a chain tensioner 79 L is elastically, slidably in contact with the forward movement portion, i.e., the lower side running portion of the chain 71 L running counterclockwise from the drive sprocket 69 L to the driven sprocket 70 L , and a chain guide 80 L is slidably in contact with the backward movement portion, i.e., the upper side running portion of the chain 71 L running counterclockwise from the driven sprocket 70 L to the drive sprocket 69 L .

The chain tensioner 79 L is extended in the running direction of the chain 71 L . One end portion of the chain tensioner 79 L is turnably supported by the bearing cap 32 , which is closest to the transmission mechanism 68 L , for rotatably supporting the crank shaft 29 in co-operation with the plurality of journal walls 31 , via a supporting shaft 81 L having an axial line parallel to the rotational axial line of the crank shaft 29 . A tensioner lifter 82 L , which is in contact with an intermediate portion of the chain tensioner 79 L in the longitudinal direction while pressing the chain tensioner 79 L onto the chain 71 L , is mounted to the left cylinder block 23 L .

The chain guide 80 L is extended in the running direction of the chain 71 L . One end portion of the chain guide 80 L is supported via a bolt 83 L on the journal wall 31 closest to the transmission mechanism 68 L ; and an intermediate portion and the other end portion of the chain guide 80 L are in contact with and supported by the left cylinder block 23 L and the left cylinder head 24 L , respectively.

At the right side transmission mechanism 68 R , a chain tensioner 79 R is elastically, slidably in contact with the forward movement portion, i.e., the upper side running portion of the chain 71 R running counterclockwise from the drive sprocket 69 R to the driven sprocket 70 R , and a chain guide 80 R is slidably in contact with the backward movement portion, i.e., the lower side running portion of the chain 71 R running counterclockwise from the driven sprocket 70 R to the drive sprocket 69 R .

The chain tensioner 79 R is extended in the running direction of the chain 71 R . One end portion of the chain tensioner 79 R is turnably supported by the journal wall 31 , which is closest to the transmission mechanisms 68 L and 68 R , is formed integrally with the left crank case 27 L , via a supporting shaft 81 R having an axial line parallel to the rotational axial line of the crank shaft 29 . A tensioner lifter 82 R , which is in contact with an intermediate portion of the chain tensioner 79 R in the longitudinal direction while pressing the chain tensioner 79 R onto the chain 71 R , is mounted to the right cylinder block 23 R .

The chain guide 80 R is extended in the running direction of the chain 71 R . One end portion of the chain guide 80 R is supported via a bolt 83 R on a supporting portion 84 formed integrally with the right crank case 27 R ; and an intermediate portion and the other end portion of the chain guide 80 R are in contact with and supported by the right cylinder block 23 R and the right cylinder head 24 R , respectively.

One end portion of the transmission chamber 72 L (or 72 R ) for containing the transmission mechanism 68 L (or 68 R ) is in communication with the valve system chamber 61 L (or 61 R ), and the valve system chamber 61 L (or SI R ) is disposed on the upper side of the plane 38 L (or 38 R ) containing the axial line of the crank shaft 29 and the axial lines of the cylinder bores 21 L (or 21 R ) . Accordingly, oil supplied from the interior of the valve system chamber 61 L (or 61 R ) into the one end of the transmission chamber 72 L (or 72 R ) can be introduced to the other end portion, facing the one end of the crank shaft 29 , of the transmission chamber 72 L (or 72 R ). A return hole 85 for communicating the bottoms of the other end portions of both of the transmission chambers 72 L and 72 R to the crank chamber 28 is provided in the left and right crank cases 27 L and 27 R .

Referring particularly to FIG. 12 , a plurality of ribs 88 in contact with and connected to the plurality of journal walls 31 formed integrally with the left crank case 27 L are formed integrally with the right crank case 27 R in such a manner as to surround the bearing caps 32 . The return hole 85 is formed in a region extending from the journal wall 31 facing both of the transmission chambers 72 L and 72 R to the rib 88 in contact with and connected to the above journal wall 31 . To be more specific, the return hole 85 is composed of a recess 86 provided in the above journal wall 31 in such a manner as to be opened toward the above rib 88 side and a recess 87 provided in the above rib 88 in such a manner as to be opened toward the above journal wall 31 side.

The bearing cap 32 is, as described above, fastened to the journal wall 31 with the pair of bolts 33 , and the return hole 85 is extended in the fastening direction of the bearing cap 32 to the journal wall 31 , i.e., the axial line direction of the bolts 33 .

The return hole 85 is formed between the crank cases 27 L and 27 R in such a manner as to be offset toward the left crank case 27 L side. To be more specific, of the recesses 86 and 87 constituting the return hole 85 , the recess 86 provided in the journal wall 31 is formed longer in the axial line direction of the bolts 33 than the recess 87 formed in the rib 88 .

A mission case 90 is continued to the left and right engine blocks B L and B R in such a manner as to extend downwardly from the crank cases 27 L and 27 R and also extend rearwardly in the longitudinal direction of the motorcycle from the cylinder blocks 23 L and 23 R . In the same manner as the above-described return hole 85 , a passage hole 89 is provided in such a manner as to extend from the bottom of the journal wall 31 disposed between the return hole 85 and the interior of the mission case 90 to the bottom of the rib 88 in contact with and connected to the journal wall 31 . Accordingly, oil returning from the transmission chambers 72 L and 72 R into the crank chamber 28 via the return hole 85 is introduced in the mission case 90 by way of the passage hole 89 .

As described above, oil in the valve system chamber 61 L and 61 R is returned to the crank chamber 28 side via the transmission chambers 72 L and 72 R on one end sides of the cam shafts 64 L and 64 R . Since the cam shafts 64 L and 64 R are disposed substantially in the horizontal direction, it may be desirable to allow the return of oil from the other end sides of the cam shafts 64 L and 64 R to the crank chamber 28 side in the valve system chambers 61 L and 61 R . To meet the above requirement, a return passage 91 L (or 91 R ) having one end in communication with the interior of the valve system chamber 61 L (or 61 R ) on the other end side of the cam shaft 64 L (or 64 R ) and having the other end in communication with the crank chamber 28 is provided in the left cylinder head 24 L (or right cylinder head 24 R ) and the left cylinder block 23 L (or right cylinder block 23 R ).

Referring particularly to FIGS. 13 and 14 , a water pump 94 including a pump shaft 95 directly connected to the crank case 29 is disposed on the back face of the mission case 90 . A casing 96 of the water pump 94 is composed of a pump body 97 for rotatably supporting the pump shaft 95 , and a pump cover 98 is fastened to the pump body 97 in such a manner as to cover an impeller 99 fixed to the pump shaft 95 .

The pump body 97 is formed integrally with the mission case 90 . The pump cover 98 is fastened to the pump body 97 with a pump chamber 100 formed between the pump cover 98 and the pump body 97 . The pump shaft 95 is rotatably supported by the pump body 97 in a state where one end thereof projects in the pump chamber 100 . An engagement plate 95 a to be engaged with an engagement recess 29 a provided in the other end of the crank shaft 29 is projectingly provided at the other end of the pump shaft 95 . In other words, one end side of the crank shaft 29 is connected to the cam shafts 64 L and 64 R via the transmission mechanisms 68 L and 68 R , while the other end side of the crank shaft 29 is directly connected to the pump shaft 95 of the water pump 94 .

The impeller 99 is disposed in the pump chamber 100 and is fixed to the one end of the pump shaft 95 . Over the impeller 99 , a containing portion 101 in communication with the central portion of the pump chamber 100 is formed in the upper portion of the pump cover 98 .

A wax type thermostat 102 , which is additionally provided on the water pump 94 , is contained in the containing portion 101 in a state where it is held between the pump body 97 and the pump cover 98 .

The thermostat 102 is of a known type, and includes a supporting plate 103 held between the pump body 97 and the pump cover 98 , a thermostat valve 104 , and a bypass valve 105 .

A first suction port 106 opened toward one end of the containing portion 101 is provided in the upper portion of the pump body 97 in such a manner as to be openable/closable by the thermostat valve 104 . A second suction port 107 opened toward the other end of the containing portion 101 is provided in the pump cover 98 in such a manner as to be openable/closable by the bypass valve 105 . A discharge port 108 for discharging cooling water discharged depending on rotation of the impeller 99 is provided in the pump cover 98 . The discharge port 108 is in communication with the pump chamber 100 .

A water jacket 109 L (or 109 R ) is provided on the left cylinder block 23 L (or right cylinder block 23 R ), and a water jacket 110 L (or 110 R ) in communication with the water jacket 109 L (or 109 R ) is provided on the cylinder block 23 L (or 23 R ). The discharge port 108 of the water pump 94 is in communication with the water jackets 109 L and 109 R via cooling water supply pipes 111 connected to the left and right cylinder blocks 23 L and 23 R .

A cooling water discharge pipe 112 L (or 112 R ) for discharge cooling water from the water jackets 110 L (or 110 R ) is connected to the left cylinder block 24 L (or right cylinder head 24 R ). The cooling water discharge pipes 112 L and 112 R are connected to the second suction port 107 of the water pump 94 , and are also connected to inlets of radiators 113 L and 113 R , respectively.

The radiators 113 L and 113 R are disposed over the left and right engine blocks B L and B R , i.e., both of the cylinder bore rows 22 L and 22 R . The outlets of both of the radiators 113 L and 113 R are connected to the first suction port 106 of the water pump 94 .

According to such a cooling water circuit, in a state where the temperature of cooling water is low before the engine is warm, the thermostat 102 closes the thermostat valve 104 and opens the bypass valve 105 . Therefore, cooling water discharged from the discharge port 108 of the water pump 94 is not sucked from the water jackets 109 L , 110 L , 109 R and 110 R into the water pump 94 by way of the radiators 113 L and 113 R . On the other hand, as the temperature of cooling water becomes higher along with termination of warming of the engine, the thermostat 102 opens the thermostat valve 104 and closes the bypass valve 105 . Therefore, cooling water discharged from the discharge port 108 of the water pump 94 is sucked from the water jackets 109 L , 110 L , 109 R and 110 R into the water pump 94 by way of the radiators 113 L and 113 R . In other words, a bottom bypass type cooling water circuit using the thermostat 102 is formed among the water pump 94 , the water jackets 109 L , 109 R , 110 L and 110 R and the radiators 113 L and 113 R .

A jiggle valve 114 for releasing air in the water pump 94 onto the first suction port 106 side is mounted on the upper portion of the supporting plate 103 of the thermostat 102 disposed over the impeller 99 .

Referring particularly to FIG. 13 , a main shaft 115 linked with the crank shaft 29 , a counter shaft 116 with a plurality of gear trains capable of being selectively established provided between the main shaft 115 and the counter shaft 116 , and an output shaft 117 linked with the counter shaft 116 via a one-way clutch (not shown) are rotatably supported by the mission case 90 . Each of the shafts 115 , 116 and 117 has an axial line parallel to that of the crank shaft 29 . The output shaft 117 for transmitting power to the rear wheel side of the motorcycle projects rearwardly from the back face of the mission case 90 .

A shifter shaft 119 for axially movably supporting a plurality of shifters 118 for selectively establishing the gear trains between the main shaft 115 and the counter shaft 116 is supported by the mission case 90 at a position below and between the main shaft 115 and the counter shaft 116 . A shift drum 120 for selectively moving one of the shifters 118 is supported by the mission case 90 at a position adjacent to the shifter shaft 119 in such a manner as to be rotatable on its axis.

A motor 121 having a rotational axial line parallel to the axial line of the crank shaft 29 is mounted on the back face of the mission case 90 at a position above and between the crank shaft 29 and the output shaft 117 . An intermediate shaft 122 is supported by the mission case 90 at a position between the crank shaft 29 and the motor 121 . A gear train (not shown), which allows transmission of rotational power from the motor 121 to the crank shaft 29 but does not allow transmission of power from the crank shaft 29 to the motor 121 , is provided between the motor 121 and the crank shaft 29 with the intermediate shaft 122 interposed therebetween. Therefore, the power of the motor 121 is transmitted to the crank shaft 29 upon start-up of the engine.

A power transmission mechanism 123 actuated upon backward movement is provided between the motor 121 and the output shaft 117 . The mechanism 123 is adapted to transmit rotational power from the motor 121 to the output shaft 117 on the basis of a driver's operation for backward movement and to rotate the output shaft 117 in a reverse direction upon forward movement. The power transmission mechanism 123 actuated for backward movement cuts off the power transmission from the output shaft 117 to the motor 121 upon operation which is not for backward movement.

An electric generator 124 linked with the crank shaft 29 is mounted on the back face of the mission case 90 in parallel to the axial line of the crank shaft 29 . A clutch 125 coaxial with the main shaft 115 , which is capable of switching the connection/disconnection between the crank shaft 29 and the main shaft 115 , is disposed on the back face of the mission case 90 . In other words, the electric generator 124 and the clutch 125 are disposed on the back face of the mission case 90 in parallel to the water pump 94 coaxial with the crank shaft 29 .

An oil pump 126 connected to the main shaft 115 via a power transmission mechanism 128 such as a chain is provided in the lower portion of the mission case 90 . Oil discharged from the oil pump 126 is supplied to respective portions to lubricate the engine main body E via an oil filter 127 (see FIG. 2 ) provided on the front surface side of the mission case 90 . The oiling passages 55 L and 55 R provided in the left and right cylinder blocks 23 L and 23 R and the left and right cylinder heads 24 L and 24 R for introducing oil to portions of the cam shafts 46 L and 46 R to be lubricated are connected to the oil filter 127 .

Referring again to FIGS. 1 and 2 , a body frame (not shown) of the motorcycle has steps 130 L and 130 R on which the driver's feet are to rest. The steps 130 L and 130 R are mounted on left and right portions positioned behind and below the left and right cylinder heads 24 L and 24 R of the engine main body E in such as manner as to project leftwardly and rightwardly therefrom. The inner end of each of the steps 130 L and 130 R is offset a distance L 7 inwardly in the width direction of the motorcycle from the opening formed at the outer end of each of the exhaust passages 35 L and 35 R provided in the cylinder heads 24 L and 24 R .

To prevent the action of the driver's feet on the steps 130 L and 130 R from being obstructed by the left and right cylinder heads 24 L and 24 R and the left and right head covers 60 L and 60 R , the lower rear corners thereof are cut off as shown by reference numeral 131 .

The function of this embodiment will now be described. In the horizontally-opposed type multi-cylinder (for example, six cylinder) engine, a pair of left and right cylinder bore rows 22 L and 22 R disposed on both sides of the crank shaft 29 extending substantially in the horizontal direction; the left cylinder bore row 22 L (or right cylinder bore row 22 R ) is composed of a plurality (for example, three) of the cylinder bores 21 L (or 21 R ) disposed in parallel; and the cam shaft 46 L (or 46 R ) corresponding to the cylinder bore row 22 L (or 22 R ) is disposed on an upper side of the plane 38 L (or 38 R ) containing the axial lines of the cylinder bores 21 L (or 21 R ) and the axial line of the crank shaft 29 . Accordingly, the valve system mechanism containing the cam shaft 46 L (or 46 R ) is offset upwardly from the axial lines of the cylinder bores 21 L (or 21 R ), so that the cylinder head 24 L (or 24 R ) can be formed in such a manner as to ensure a space under the portion corresponding to the valve system mechanism. In other words, a relatively large space can be ensured under the cylinder head 24 L (or 24 R ).

When the horizontally-opposed type multi-cylinder engine is mounted on a motorcycle in such a manner that the axial line of the crank shaft 29 extends along the longitudinal direction of the motorcycle and the cylinder heads 24 L and 24 R project on both sides of the motorcycle in the width direction, it is possible to ensure a sufficient space for allowing the driver's feet to extend forward at a position under the cylinder heads 24 L and 24 R and to set a bank angle α of the motorcycle at a relatively large value.

The pairs of the intake valves 36 L (or 36 R ) and the exhaust valves 37 L (or 37 R ), each pair being disposed for each cylinder bore 21 L (or 21 R ), i.e., for each combustion chamber 26 L (or 26 R ), are disposed in parallel in such a manner as to be offset upwardly from the plane 38 L (or 38 R ), and are directly opened/closed by the intake side cams 48 L (or 48 R ) and the exhaust cams 49 L (or 49 R ) provided on the cam shaft 46 L (or 46 R ). Accordingly, the valve system mechanism for driving the intake valves 36 L (or 36 R ) and the exhaust valves 37 L (or 37 R ) can be significantly simplified. Furthermore, since the cam shafts 46 L and 46 R are disposed for the cylinder bore rows 22 L and 22 R , respectively, the cylinder heads 24 L and 24 R can be made compact.

Since the intake valves 36 L (or 36 R ) and the exhaust valves 37 L (or 37 R ) are disposed in the cylinder head 24 L (or 24 R ) in such a manner as to be tiled at an acute angle with respect to the plane 38 L (or 38 R ), it is possible to form the ceiling of each of the combustion chambers 26 L (or 26 R ) into a pent-roof or semi-spherical shape and hence to set the S/V ratio at a relatively small value.

On the opposite side from the disposition side of the intake valves 36 L ( 36 R ) and the exhaust valves 37 L (or 37 R ) with respect to the plane 38 L (or 38 R ), i.e., on the lower side of the plane 38 L (or 38 R ), the ignition plugs 39 L ( 39 R ) are mounted to the cylinder head 24 L (or 24 R ). Each of the ignition plugs 39 L ( 39 R ) face toward the combustion chamber 26 L (or 26 R ). Furthermore, in this case, since the intake valves 36 L (or 36 R ) and the exhaust valves 37 L (or 37 R ) are tilted at an acute angle with respect to the plane 38 L (or 38 R ), it is possible to ensure a relatively wide space on the side opposite to the disposition side of the intake valves 36 L (or 36 R ) and the exhaust valves 37 L (or 37 R ) with respect to the plane 38 L (or 38 R ), i.e., the lower side of the plane 38 L (or 38 R ). Therefore, it is easy to make the ignition plugs 39 L (or 39 R ) face toward the central portions of the combustion chambers 26 L (or 26 R ) while avoiding interference with the intake valves 36 L (or 36 R ) and the exhaust valves 37 L (or 37 R ) and to increase the degree of freedom of disposition of the ignition plugs 39 L (or 39 R ).

The ignition plugs 39 L (or 39 R ) are tilted at an acute angle with respect to the plane 38 L (or 38 R ). With regard to the tilting angle of the ignition plugs 39 L (or 39 R ), since the intake valves 36 L (or 36 R ) and the exhaust valves 37 L (or 37 R ) are tilted at an acute angle with respect to the plane 38 L (or 38 R ), it is possible to make the ignition plugs 39 L (or 39 R ) face to the central portions of the combustion chambers 26 L (or 26 R ) while avoiding the interference with the cam shafts 46 L (or 46 R ) without setting the tilting angle of the ignition plugs 39 L (or 39 R ) at a large value.

The cylinder head 24 L (or 24 R ) includes the intake passages 34 L (or 34 R ) opened toward the side surface of the cylinder head 24 L (or 24 R ) on the upper side of the plane 38 L (or 38 R ). Furthermore, the cylinder head 24 L (or 24 R ) also includes the exhaust passages 35 L (or 35 R ) opened toward the other side surface of the cylinder head 24 L (or 24 R ) on the lower side of the plane 38 L (or 38 R ). In other words, since the intake valves 34 L (or 34 R ) and the exhaust valves 35 L (or 35 R ) are provided in such a manner as to be opened toward the side surfaces of the cylinder head 24 L (or 24 R ) on both sides of the plane 38 L (or 28 R ), it is easy to connect the intake system 66 and the exhaust system 43 L (or 43 R ) to the cylinder head 24 L (or 24 R ).

On the projection chart perpendicular to the axial lines of the cylinder bores 21 L (or 21 R ), the intake passages 34 L (or 34 R ) are provided in the cylinder head 24 L (or 24 R ) in such a manner as to cross the plane 38 L (or 38 R ) substantially at right angles. In other words, since the intake valves 34 L (or 34 R ) extend substantially in a straight line while being relatively gently curved toward the combustion chambers 26 L (or 26 R ), it is possible to reduce the intake resistance at the intake passages 34 L (or 34 R ) and hence to enhance the charging efficiency.

The exhaust passages 35 L (or 35 R ) are provided in the cylinder head 24 L (or 24 R ) in such a manner as to be curved or swelled to one end side of the cam shaft 46 L (or 46 R ), i.e., the front side of the motorcycle, in order to bypass the ignition plugs 39 L (or 39 R ). As a result, the flow resistance in the exhaust passages 35 L (or 35 R ) is larger than that of the intake passages 34 L (or 34 R ); however, no problems arise because the exhaust gas from the combustion chambers 26 L (or 26 R ) is pressurized.

Since the cam shaft 46 L (or 46 R ) is disposed over the axial line of the cylinder bore row 22 L (or 22 R ) and the exhaust passages 35 L (or 35 R ) bypass the ignition plugs 39 L (or 39 R ) by curving toward the front side of the motorcycle, it is easy to ensure space for allowing the driver's feet to extend forward at a position behind and below the horizontally-opposed type engine mounted on the motorcycle.

While the exhaust passages 35 L (or 35 R ) are downwardly opened toward the lower side surface of the cylinder head 24 L (or 24 R ), the ignition plugs 39 L (or 39 R ) are also mounted to the cylinder head 24 L (or 24 R ) in such a manner as to be tilted downwardly. Accordingly, in the horizontally-opposed type multi-cylinder engine mounted on the motorcycle, it is possible to improve the appearance of the ignition plugs 39 L (or 39 R ) and the surrounding area, to easily discharge water which has permeated in the vicinity of the ignition plugs 39 L ( 39 R ) on the outer surface side of the cylinder head 24 L (or 24 R ), and to easily lay out the exhaust pipes 41 L ( 41 R ) connected to the exhaust passages 35 L (or 35 R ).

Furthermore, since the cover portion 62 L (or 62 R ) for covering the ignition plugs 29 L (or 29 R ) from the outside is formed integrally with the left head cover 60 L (or right head cover 60 R ) which is connected to the left cylinder head 24 L (or right cylinder head 24 R ) with the valve system chamber 61 L (or 61 R ) for containing the camn shaft 46 L ( 46 R ), it is possible to further improve the appearance of the ignition plugs 39 L (or 39 R ) and the surrounding area.

Since the exhaust passages 35 L (or 35 R ) are provided-in the cylinder head 24 L (or 24 R ) in such a manner as to be tilted toward the central side of the motorcycle in the width direction and to be downwardly opened to allow the exhaust pipes 41 L (or 41 R ) connected to the exhaust passages 35 L (or 35 R ) to be disposed near the center portion of the motorcycle in the width direction, it is possible to loosen the restriction of the bank angle a of the motorcycle due to the exhaust pipes 41 L (or 41 R ) and hence to easily ensure the above bank angle α.

Furthermore, since the exhaust pipes 41 L (or 41 R ) are tilted in such a manner that they become closer to the central side of the motorcycle in the width direction, since they are separated apart downwardly from the cylinder head 24 L (or 24 R ) and are connected to the exhaust passages 35 L (or 35 R ), it is possible to flirter loosen the restriction of the bank angle α of the motorcycle due to the exhaust pipes 41 L (or 41 R ) and hence to more easily ensure the above bank angle α.

Since the exhaust valves 37 L ( 37 R ) are disposed on the upper side of the plane 38 L (or 38 R ) while the exhaust passages 35 L (or 35 R ) are opened toward the bottom surface of the cylinder head 24 L (or 24 R ), it is possible to relatively increase the distance between each of the combustion chambers 26 L (or 26 R ) and the opening end of an associated one of the exhaust passages 35 L (or 35 R ) opened toward the bottom surface of the cylinder head 24 L (or 24 R ). Furthermore, a relatively gentle curving of the exhaust passages 35 L ( 35 R ) within the plane perpendicular to the axial line of the crank shaft 29 can be made even though the exhaust passages 35 L (or 35 R ) are opened while being tilted to the central side of the motorcycle in the width direction. This allows suppression of the increase in exhaust resistance.

The cover portion 62 L (or 62 R ) formed integrally with the left head cover 60 L (right head cover 60 R ) functions to cover connecting portions of the exhaust passages 35 L (or 35 R ) of the exhaust pipes 41 L (or 41 R ) from outside. This makes it possible to improve the appearance of the connecting portions of the exhaust passages 35 L (or 35 R ) of the exhaust pipes 41 L (or 41 R ). Furthermore, since the exhaust pipes 41 L (or 41 R ) are separated apart from the cover portion 62 L (or 62 R ) since directed downwardly, even if the head cover 60 L (or 60 R ) is made from a synthetic resin, it is possible to avoid occurrence of thermal degradation of the cover portion 62 L (or 62 R ).

With respect to the intake passages 34 L and the exhaust passages 35 L provided in the left cylinder head 24 L and the intake passages 34 R and the exhaust passages 35 R provided in the right cylinder head 24 R , the relative positional relationship between the intake passages 34 L and the exhaust passages 35 L along the axial line direction of the crank shaft 29 is set to be nearly equal to the relative positional relationship between the intake passages 34 R and the exhaust passages 35 R along the axial line direction of the crank shaft 29 . This makes it possible to simplify the structure of the intake system 66 and the exhaust systems 43 L and 43 R .

A plurality of the through-holes 56 L ( 56 R ) spaced in the axial direction of the cam shaft 46 L (or 46 R ) are formed in the cylinder head 24 L (or 24 R ) on the lower side of the plane 38 L (or 38 R ) to fasten the cylinder head 24 L (or 24 R ) to the cylinder block 23 L (or 23 R ). The fastening bolts 57 L (or 57 R ) are inserted in the throughholes 56 L (or 56 R ). Furthermore, each through-hole 56 L (or 56 R ) is adjacent, on one end side of the cam shaft 46 L (or 46 R ), to an associated one of the exhaust passages 35 L (or 35 R ) bypassing the ignition plugs 39 L (or 39 R ) provided in the combustion chambers 26 L (or 26 R ). The through-hole 56 L (or 56 R ) has a positional relationship such that a distance L 4 between a center of the through-hole 56 L (or 56 R ) and a center C L (or C R ) of an associated combustion chamber 26 L (or 26 R ) is larger than a value L 3 . The value L 3 is half a distance between the centers C L (or C R ) of adjacent ones of the combustion chambers 26 L (or 26 R ). This makes it possible to make the curving of the exhaust passages 35 L (or 35 R ) bypassing the ignition plugs 39 L (or 39 R ) relatively small. Therefore, the flow resistance of the exhaust passages 35 L (or 35 R ) are prevented from being excessively increased.

On the disposition side of the intake valves 36 R and the exhaust valves 37 R with respect to the plane 38 R , the right cylinder head 24 R has a plurality of the through-holes 58 R which are spaced in the axial line direction of the cam shaft 46 R . Of the plurality of the through-holes 58 R , the central side through-holes 58 R are each disposed between adjacent ones of the combustion chambers 26 R . A distance L 5 between a center of the through-hole 58 R disposed at the outermost end on one end side of the cam shaft 46 R and the center C R of the combustion chamber 26 R disposed at the outermost end on the one end side of the cam shaft 46 R is set to be smaller than the value L 3 . The value L 3 is, as described above, half the distance between the centers C R of adjacent ones of the combustion chambers 26 R . Accordingly, the end portion of the cylinder head 24 R on the one end side of the cam shaft 46 R can be made as close to the center C R of the combustion chamber 26 R , which is disposed at the outermost end on the curved side of the exhaust passages 35 R bypassing the ignition plugs 39 R , as possible. This makes the length of the cylinder head 24 R along the axial direction of the cam shaft 46 R as small as possible.

The cam shaft 46 L (or 46 R ) is rotatably supported at a plurality of locations spaced in the axial direction of the cam shaft 46 L (or 46 R ) by the cam bearing portions 50 L (or 50 R ) provided on the cylinder head 24 L (or 24 R ) and the cam holder 51 L (or 51 R ) fastened to the cam bearing portions 50 L (or 50 R ). The transmission mechanism 68 L (or 68 R ), which reduces rotational power of the crank shaft 29 to half and transmits the reduced rotational power to the cam shaft 46 L (or 46 R ), is provided between the crank shaft 29 and the cam shaft 46 L (or 46 R ). The oil passage 52 L (or 52 R ), which is capable of supplying oil from the oiling passage 55 L (or 55 R ) provided in the cylinder head 24 L (or 24 R ) and the cylinder block 23 L (or 23 R ), is provided in the cam shaft 46 L (or 46 R ). On the left cylinder head 24 L side, oil is supplied from the oil groove 54 L provided in the cam bearing portion 50 L disposed at the outermost end on the one end side of the cam shaft 46 L into the oil passage 52 L in the cam shaft 46 L via the oiling hole 53 L formed in the cam shaft 46 L . On the right cylinder head 24 R side, the oil groove 54 R for supplying oil into the oil passage 52 R in the cam shaft 46 R via the oiling hole 53 R formed in the cam shaft 46 R is formed in the cam bearing portion 50 R which is provided in the cylinder head 24 R correspondingly to the combustion chamber 26 R closest to the transmission mechanism 68 R among the plurality of combustion chambers 26 R disposed in the axial direction of the cam shaft 46 R .

With this disposition of the oil groove 54 R , it is possible to supply oil into the oil passage 52 R in the cam shaft 46 R without restriction of the disposition of the fastening bolts 57 R and 59 R for fastening the right cylinder head 24 R to the right cylinder block 23 R .

The cam bearing portion 50 R closest to the transmission mechanism 68 R among the plurality of the cam bearing portions 50 R provided on the right cylinder head 24 R has the through-hole 58 R into which the fastening bolt 59 R among the fastening bolts 57 R and 59 R for fastening the cylinder head 24 R to the cylinder block 23 R is to be inserted. As a result, the fastening bolt 59 R between the transmission mechanism 68 R and the combustion chamber 26 R is made as close to the combustion chamber 26 R as possible, so that it is possible to shorten the length of the cylinder head 24 R along the axial line direction of the cam shaft 46 R .

The transmission mechanism 68 R corresponding to the cam shaft 46 R on the right cylinder head 24 R side is offset forwardly along the axial line direction of the crank shaft 29 from the transmission mechanism 68 L corresponding to the cam shaft 46 L on the left cylinder head 24 L . In other words, the outermost end on one end side of the cam shaft 46 R is offset forwardly from that of the cam shaft 46 L , and the transmission mechanism 68 R is connected to the outermost end on the one end side of the cam shaft 46 R . The above through-hole 58 R and the above oil groove 54 R are provided in two of the plurality of the cam bearing portions 50 R provided on the cam shaft 46 R . Accordingly, it is possible to shorten the length between the transmission mechanism 68 R and the combustion chamber 26 R and hence to more effectively shorten the length of the multi-cylinder engine along the axial line direction of the cam shaft 46 L (or 46 R ).

The pair of the cylinder bore rows 22 L and 22 R are offset from each other in the axial line direction of the crank shaft 29 . Furthermore, the transmission mechanisms 68 L and 68 R are disposed in such a manner that the gap L 6 therebetween is smaller than the first offset amount L 1 between the cylinder bore rows 22 L and 22 R . Accordingly, it is possible to set the gap between the transmission mechanisms 68 L and 68 R at a smaller value, and hence to decrease the length of the engine main body E along the axial line direction of the cam shaft 46 L ( 46 R ).

Furthermore, since both the transmission mechanisms 68 L and 68 R are provided between one end portion of the crank shaft 29 and one end portion of the cam shaft 46 L and between one end portion of the crank shaft 29 and the one end portion of the cam shaft 46 R , respectively, it is possible to more freely set the gap between the transmission mechanisms 68 L and 68 R .

The outer end opening of each of the exhaust passages 35 L (or 35 R ) opened towared the bottom surface of the left cylinder head 24 L (or right cylinder head 24 R ) is offset toward one end side of the cam shaft 46 L (or 46 R ), i.e., toward the transmission mechanism 68 L (or 68 R ) from the center C L (or C R ) of an associated one of the combustion chambers 26 L (or 26 R ). Accordingly, the exhaust systems 43 L and 43 R respectively connected to the exhaust passages 35 L and 35 R can be disposed by making effective use of the space between the transmission mechanisms 68 L and 68 R , so that the entire engine including the exhaust systems 43 L and 43 R can be made compact.

Since the transmission mechanisms 68 L and 68 R are disposed on the front portion of the engine main body E, a relatively large space is formed at a location positioned behind and below the left and right cylinder heads 24 L and 24 R , the steps 130 L and 130 R on which the driver's feet are to rest can be disposed behind the left and right cylinder heads 24 L and 24 R without any difficulty. Furthermore, since the inner end portion of each of the steps 130 L and 130 R is offset inwardly from the outer end opening of each of the exhaust passages 35 L and 35 R in the width direction of the motorcycle, the projecting amounts of the steps 130 L and 130 R in the width direction of the motorcycle is made as small as possible, so that the restriction of the steps 130 L and 130 R to the bank angle a can be suppressed. The transmission mechanism 68 L (or 68 R ) performs power transmission using the chain 71 L (or 71 R ). The transmission chamber 72 L ( 72 R ), having one end in communication with the valve system chamber 61 L (or 61 R ) and the other end facing toward one end of the crank shaft 29 and containing the transmission mechanism 68 L (or 68 R ), extends from the head cover 60 L (or 60 R ) to the crank case 27 L (or 27 R ) via the cylinder head 24 L (or 24 R ) and the cylinder block 23 L (or 23 R ). The other end of the transmission chamber 72 L (or 72 R ) is in communication with the crank chamber 28 .

Unlike a belt-type transmission mechanism, the transmission chamber 72 L (or 72 R ) containing the transmission mechanism 68 L (or 68 R ) allows oil to flow therethrough. Accordingly, it is possible to eliminate the necessity of provision of any means for preventing leakage of oil from the crank case 27 L (or 27 R ) side onto the transmission chamber 72 L (or 72 R ) side. More specifically, the necessity of provision of a seal structure on the crank case 27 L (or 27 R ) is eliminated. Therefore, the engine is made as compact as possible.

Furthermore, since the cam shaft 46 L (or 46 R ) is disposed over the crank shaft 29 , oil in the valve system 61 L (or 61 R ) is allowed to flow onto the crank shaft 29 side at the lower level through the transmission chamber 72 L (or 72 R ). As a result, oil in the valve system chamber 61 L (or SI R ) is easily returned to the crank case 27 L (or 27 R ) side.

In addition, the return hole 85 is provided in the left and right crank cases 27 L and 27 R to communicate the bottom portions of the other ends of the transmission chambers 72 L and 72 R into the crank chamber 28 . Accordingly, it is not required to provide oil return passages specialized for the cylinder blocks 23 L and 23 R and the cylinder heads 24 L and 24 R or returning oil from at least the transmission chambers 72 L and 72 R into the crank chambers 28 . Therefore, the cylinder blocks 23 L and 23 R and the cylinder blocks 24 L and 24 R can be made compact and reduced in weight.

The crank shaft 29 is rotatably supported by a plurality of the journal walls 31 formed integrally with the left crank case 27 L and a plurality of bearing caps 32 fastened to the journal walls 31 . The return hole 85 is extended in the fastening direction of the bearing caps 32 to the journal walls 31 . Accordingly, it is possible to make the opening area of the return hole 85 relatively wide without reducing the supporting rigidity of the crank shaft 29 . Therefore, the return of oil into the crank chamber 28 is enhanced.

The return hole 35 is formed in the left and right crank cases 27 L and 27 R in such a manner as to be offset toward the left crank case 27 L side. Accordingly, it is possible to increase the opening area of the return hole 85 avoiding a reduction in rigidity of the crank case on which the journal walls 31 are not integrally formed, i.e., the right crank case 27 R . Therefore, the return of the oil is further enhanced.

In the transmission mechanism 68 L provided between the left side cam shaft 46 L and the crank shaft 29 , the chain tensioner 79 L extending along the running direction of the chain 71 L is elastically, slidably in contact with the chain 71 L . One end of the chain tensioner 79 L in the longitudinal direction is turnably supported by the bearing cap 32 closest to the transmission mechanism 68 L among a plurality of the bearing caps 32 . With this configuration, it is possible to moderate the restriction in the rotatably supporting position of the chain tensioner 79 L and to confine the behavior of the chain 71 L by setting the length of the chain tensioner 79 L at a relatively large value.

Since the transmission mechanism 68 L is provided between one end portion of the cam shaft 46 L and one end portion of the crank shaft 29 , it is not required to take into account the disposition of the rotatably supporting portion of the chain tensioner 79 L at a position where the chain tensioner 79 L does not interfere with a crank weight of the crank shaft 29 . This makes it possible to simply set the rotatably supporting position of the chain tensioner 79 L .

Since one end of the chain tensioner 79 L for the transmission mechanism 68 L on the cylinder block 23 L side on which the journal walls 31 are integrally formed is rotatably supported by the bearing cap 32 closest to the transmission mechanism 68 L , it is possible to simply set the rotatably supporting position of the chain tensioner 79 L by making effective use of one of the bearing caps 32 necessarily provided for the horizontally-opposed type multi-cylinder engine.

The pump shaft 95 of the water pump 94 is directly connected to the other end of the crank shaft 29 with one end side connected to the transmission mechanisms 68 L and 68 R , i.e., the rear end of the crank shaft 29 along the longitudinal direction of the motorcycle, and the water pump 94 is directly driven by the crank shaft 29 . Accordingly, it is possible to eliminate the necessity of a gear, a chain, a belt, etc. required for driving the conventional water pump, and therefore simplify the drive mechanism of the water pump 94 .

The pulse rotor 75 for detecting a rotational position of the crank shaft 29 is fixed to one end portion of the crank shaft 29 . By use of the pulse rotor 75 , it is possible to easily detect a rotational position of the crank shaft 29 with no obstruction by the water pump 94 .

Since the water pump 94 is disposed on the rear side in the longitudinal direction of the motorcycle, a piping system for cooling water, connected to the water pump 94 , can be disposed at an inconspicuous position.

Since the radiators 113 L and 113 R are respectively disposed over the engine blocks B L and B R , i.e., over the cylinder bore rows 22 L and 22 R , pipes for cooling water between the engine and the radiators 113 L and 113 R are made nearly equal on the left and right sides or are even shortened.

Since the electric generator 124 and the clutch 125 are disposed in parallel with the water pump 94 , it is not required to increase the length of the crank shaft 29 for disposing the electric generator 124 and the clutch 125 in spite of the fact that the water pump 94 is directly driven by the crank shaft 29 . Accordingly, it is possible to make the engine compact in the axial direction of the crank shaft 29 .

The casing 96 of the water pump 94 is composed of the pump body 97 for rotatably supporting the pump shaft 95 , and the pump cover 98 connected to the pump body 97 in such a manner as to cover the impeller 99 fixed to the pump shaft 95 . The thermostat 102 held between the pump body 97 and the pump cover 98 is contained in the containing portion 101 formed in the pump cover 98 . As a result, in the case of additionally providing the thermostat 102 in the water pump 94 , it is possible to reduce the number of parts, and hence to reduce the cost and weight and the number of assembling steps.

The first suction port 106 opened toward one end of the containing portion 101 is provided in the pump body 97 in such a manner as to be in communication with the radiators 113 L and 113 R . The second suction port 107 opened toward the other end of the containing portion 101 for introducing water from the engine not by way of the radiators 113 L and 113 R is provided in the pump cover 98 . The thermostat 102 having the thermostat valve 104 for opening/closing the first suction port 106 and the bypass valve 105 for opening/closing the second suction port 107 is contained in the containing portion 101 . Accordingly, when the temperature of cooling water is low, the thermostat valve 104 is closed and the bypass valve 105 is opened, while as the temperature of cooling water is increased, the thermostat valve 104 is opened and the bypass valve 105 is closed. In this way, the bottom-bypass type cooling water circuit can be simply obtained.

Since the discharge port 108 for discharging cooling water discharged depending on rotation of the impeller 99 is provided in the pump cover 98 , it is possible to simply obtain a circuit for introducing cooling water from the water pump 94 .

Since the thermostat 102 is disposed over the impeller 99 , it is possible to release air in the water pump 94 by means of the jiggle valve 114 of the thermostat 102 .

As described above, according to the first aspect of the present invention, since the oil groove is provided in the cam bearing portion provided on the cylinder head at a position corresponding to one of the plurality of combustion chambers where the fastening bolts are not disposed, it is possible to supply oil in the oil passage formed in the cam shaft without restricting the location of the fastening bolts.

According to the second aspect of the present invention, the though-hole into which the fastening bolt is to be inserted is provided in one cam bearing portion between the combustion chamber closest to the transmission mechanism and the transmission mechanism, and the oil groove is provided in another cam bearing portion adjacent to the above one cam bearing portion, so that the fastening bolt between the transmission mechanism and the combustion chamber is made as close to the combustion chamber as possible. This makes it possible to shorten the length of the cylinder head in the axial line direction of the cam shaft.

According to the third aspect of the present invention, it is possible to set the gap between a plurality of the transmission mechanisms at a small value, and hence to further shorten the length of the engine in the axial line direction of the cam shaft.

According to the fourth aspect of the present invention, it is possible to more freely set a gap between the transmission mechanisms.

According to the fifth aspect of the present invention, it is possible to shorten the distance between the transmission mechanism and the combustion chamber, and hence to effectively shorten the length of the multi-cylinder engine in the axial line direction of the cam shaft.

The invention being thus described, it will be obvious that the same may be varied in many ways. Such variations are not to be regarded as a departure from the spirit and scope of the invention, and all such modifications as would be obvious to one skilled in the art are intended to be included within the scope of the following claims.

Claims

1. A structure for lubricating a cam shaft in a multi-cylinder engine, the multi-cylinder engine including a plurality of combustion chambers formed between a cylinder head and a plurality of pistons, said cylinder head being fastened to a cylinder block, the cylinder block including a plurality of cylinder bores and the pistons slidably fitted in the plurality of cylinder bores, a cam shaft linked with a plurality of intake valves and a plurality of exhaust valves for carrying out intake and exhaust operations for the plurality of combustion chambers rotatably supported at a plurality of locations spaced in the axial line direction of the cam shaft by cam bearing portions provided on the cylinder head and a cam holder removably fastened to the cam bearing portions, and an oil passage capable of supplying oil from an oiling passage provided in the cylinder head is formed in the cam shaft, said lubricating structure comprising:an oiling hole provided in the cam shaft in communication with the oil passage; and an oil groove in communication with an outer end of said oiling hole, said oil groove being formed in only one of the cam bearing portions provided in the cylinder head at a position corresponding to one of the plurality of combustion chambers, said oiling hole facing toward an outer surface of the cam shaft, said oil groove being in communication with said oiling passage.

2. The structure for lubricating a cam shaft in a multi-cylinder engine according to claim 1, further comprising:a plurality of cylinder bore rows, each of said plurality of cylinder bore rows including a plurality of cylinder bores spaced at equal intervals in the axial line direction of a crank shaft of the engine, each of said plurality of cylinder bores crossing each other at an angle within a plane perpendicular to the axial line of the crank shaft and being offset from each other in the axial line direction of the crank shaft; a plurality of transmission mechanisms corresponding to said cylinder bore rows are disposed such that a gap between each of said plurality of transmission mechanisms is smaller than a mutual offset amount between said cylinder bores; and one of the cam bearing portions includes a through-hole formed therethrough, said one cam bearing portion being set in accordance with at least one of said plurality of transmission mechanisms.

3. The structure for lubricating a cam shaft in a multi-cylinder engine according to claim 2, wherein there are a plurality of said cam shafts, and each of said plurality of transmission mechanisms is provided between one end portion of the crank shaft and an associated one of the plurality of cam shafts.

4. The structure for lubricating a cam shaft in a multi-cylinder engine according to claim 3, wherein one of said plurality of transmission mechanisms is disposed at an outermost end on one end side of said plurality of cam shafts, and one of said cam bearing portions provided in each one of said cam shafts to which said one of said plurality of transmission mechanism is connected, have said through-hole and said oil groove formed therein.

5. A structure for lubricating a cam shaft in a multi-cylinder engine, the multi-cylinder engine including a plurality of combustion chambers formed between a cylinder head and a plurality of pistons, said cylinder head being fastened to a cylinder block by a plurality of fastening bolts, the cylinder block including a plurality of cylinder bores and the pistons slidably fitted in the plurality of cylinder bores, a cam shaft linked with a plurality of intake valves and a plurality of exhaust valves for carrying out intake and exhaust operations for the plurality of combustion chambers rotatably supported at a plurality of locations spaced in the axial line direction of the cam shaft by cam bearing portions provided on the cylinder head and a cam holder fastened to the cam bearing portions, a transmission mechanism for reducing rotational speed of a crank shaft of the engine to half and transmitting the reduced rotational speed to the cam shaft is provided between the crank shaft and the cam shaft, and an oil passage capable of supplying oil from an oiling passage provided in the cylinder head is formed in the cam shaft, said lubricating structure comprising:a through-hole for receiving one of the plurality of fastening bolts for fastening the cylinder head to the cylinder block, said through hole being provided in one of the cam bearing portions provided in the cylinder head at a position between the transmission mechanism and one of the plurality of combustion chambers closest to the transmission mechanism; an oiling hole provided in the cam shaft in communication with the oil passage; an oil groove in communication with an outer end of said oiling hole is provided in another one of the cam bearing portions adjacent to said one cam bearing portion, said oil groove facing toward an outer surface of the cam shaft, said oil groove being in communication with said oiling passage.

6. The structure for lubricating a cam shaft in a multi-cylinder engine according to claim 5, further comprising:a plurality of cylinder bore rows, each of said plurality of cylinder bore rows including a plurality of cylinder bores spaced at equal intervals in the axial line direction of the crank shaft, each of said plurality of cylinder bores crossing each other at an angle within a plane perpendicular to the axial line of the crank shaft and being offset from each other in the axial line direction of the crank shaft; a plurality of the transmission mechanisms corresponding to said cylinder bores are disposed such that a gap between each of said plurality of transmission mechanisms is smaller than a mutual offset amount between said cylinder bores; and said one cam bearing portion in which said through-hole is formed is set in accordance with at least one of said plurality of transmission mechanisms.

7. The structure for lubricating a cam shaft in a multi-cylinder engine according to claim 6, wherein there are a plurality of said cam shafts, and each of said plurality of transmission mechanisms is provided between one end portion of the crank shaft and an associated one of the plurality of cam shafts.

8. The structure for lubricating a cam shaft in a multi-cylinder engine according to claim 7, wherein one of said plurality of transmission mechanisms is disposed at an outermost end on one end side of said cam shafts, and one of said plurality of cam bearing portions provided in each one of said cam shafts to which said one of said plurality of transmission mechanism is connected, have said through-hole and said oil groove formed therein.

9. A multi-cylinder engine comprising:a cylinder block, said cylinder block including a plurality of cylinder bores and pistons slidably fitted in the plurality of cylinder bores; a cylinder head fastened to said cylinder block by a plurality of fastening bolts; a plurality of combustion chambers formed between said cylinder head and said plurality of pistons, respectively; a cam shaft linked with a plurality of intake valves and a plurality of exhaust valves for carrying out intake and exhaust operations for said plurality of combustion chambers, said cam shaft being rotatably supported at a plurality of locations spaced in the axial line direction of said cam shaft by cam bearing portions provided on said cylinder head and a cam holder fastened to said cam bearing portions; a transmission mechanism for reducing rotational speed of a crank shaft of the engine to half and transmitting the reduced rotational speed to the cam shaft, said transmission mechanism being provided between the crank shaft and the cam shaft; an oil passage capable of supplying oil from an oiling passage provided in said cylinder head is formed in the cam shaft; a through-hole for receiving one of the plurality of fastening bolts for fastening said cylinder head to said cylinder block, said through hole being provided in one of said cam bearing portions provided in said cylinder head at a position between said transmission mechanism and one of said plurality of combustion chambers closest to said transmission mechanism; an oiling hole provided in said cam shaft in communication with said oil passage; an oil groove in communication with an outer end of said oiling hole is provided in another one of said cam bearing portions adjacent to said one cam bearing portion, said oil groove facing toward an outer surface of said cam shaft, said oil groove being in communication with said oiling passage.

10. The multi-cylinder engine according to claim 9, further comprising:a plurality of cylinder bore rows, each of said plurality of cylinder bore rows including a plurality of cylinder bores spaced at equal intervals in the axial line direction of said crank shaft, each of said plurality of cylinder bores crossing each other at an angle within a plane perpendicular to the axial line of said crank shaft and being offset from each other in the axial line direction of the crank shaft; a plurality of said transmission mechanisms corresponding to said cylinder bores are disposed such that a gap between each of said plurality of transmission mechanisms is smaller than a mutual offset amount between said cylinder bores; and said one cam bearing portion in which said through-hole is formed is set in accordance with at least one of said plurality of transmission mechanisms.

11. The multi-cylinder engine according to claim 10, wherein there are a plurality of said cam shafts, and each of said plurality of transmission mechanisms is provided between one end portion of said crank shaft and an associated one of said plurality of cam shafts.

12. The multi-cylinder engine according to claim 11, wherein one of said plurality of transmission mechanisms is disposed at an outermost end on one end side of said cam shafts, and one of said plurality of cam bearing portions provided in each one of said cam shafts to which said one of said plurality of transmission mechanism is connected, have said through-hole and said oil groove formed therein.

13. The structure for lubricating a camshaft in a multi-cylinder engine according to claim 1, wherein said cylinder head is fastened to said cylinder block by a plurality of fastening bolts, said lubricating structure further comprising a through-hole for receiving one of the plurality of fastening bolts, said through-hole being provided in said one of the cam bearing portions.

14. The structure for lubricating a camshaft in a multi-cylinder engine according to claim 13, wherein said cam holder is removably fastened to each of the cam bearing portions by a pair of cam fastening bolts, respectively, and said one of the plurality of fastening bolts is located between said pair of cam fastening bolts for said one of the cam bearing portions.

15. The structure for lubricating a camshaft in a multi-cylinder engine according to claim 13, wherein there are a plurality of said oiling hole, one of said oiling holes being provided for each cam bearing portion, and wherein oil flows from said oiling passage into said oil passage via said oil groove and one of said oiling holes, and oil flows out of said oil passage to the remaining oiling holes to lubricate the remaining cam bearing portions.

16. The structure for lubricating a camshaft in a multi-cylinder engine according to claim 1, wherein said one cam bearing portion is located at a same axial position of said cams haft as said one of the plurality of combustion chambers.