JP2013227966A - Internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an internal combustion engine configured to secure a large masking ratio of an intake valve port to easily generate tumbles of strong swirl, thereby improving combustion efficiency.SOLUTION: In an internal combustion engine, an intake valve port (42) is offset to have a crescent projecting part (42a) projected to the outside of a circular hole of a cylinder bore (16b), as seen in a cylinder axis direction, and a cut-out circular face (55) is formed by cutting out a portion facing the projecting part (42a) of the intake valve port (42) at an opening edge on a cylinder head (17) side of the cylinder bore (16b) of a cylinder block (16), in a moving direction of an intake valve (46) along a peripheral edge of a shade (46p) of the intake valve (46).

Description

  The present invention relates to an internal combustion engine mounted on a vehicle.

  In order to increase combustion efficiency of an internal combustion engine and reduce fuel consumption, a method of stabilizing combustion by stratifying the intake air taken in the combustion chamber to form a tumble and sending fuel around the spark plug at the top of the combustion chamber There is.

  The intake port and the exhaust port extend from the intake valve port and the exhaust valve port on the ceiling surface of the combustion chamber of the cylinder head while curving in a direction away from each other. Of the intake air that is guided to the combustion chamber, the intake valve The intake air sucked from the inner edge near the cylinder shaft (the center axis of the cylinder bore) descends the exhaust side of the cylinder bore while flowing toward the exhaust side, and then the flow is bent along the piston top surface to raise the intake side. By doing so, a so-called tumble is formed.

On the other hand, the intake air sucked from the outer edge side far from the cylinder axis of the intake valve port generates a so-called reverse tumble opposite to the tumble and acts to prevent the tumble.
Thus, there is an example in which the reverse intake tumble is suppressed by arranging a center intake valve port located between the left and right side intake valve ports of a five-valve engine so as to protrude outward from the cylinder bore (see Patent Document 1).

JP-A-6-221168

  In Patent Document 1, since the center intake valve port at the center of the three intake valve ports arranged on the ceiling surface of the combustion chamber is arranged so as to protrude outward from the cylinder bore, the protruding side of the center intake valve port, that is, the cylinder axis line Since the intake air sucked from the outer edge side far from the inlet does not directly enter the cylinder bore and is blocked by the opening edge of the cylinder bore, that is, a part of the outer edge side of the intake valve port is masked, and the reverse tumble is It is assumed that the occurrence of tumble can be suppressed and promoted.

  However, only the center intake valve port at the center of the three intake valve ports is arranged so as to protrude outside the cylinder bore, and the other two left and right intake valve ports do not protrude from the cylinder bore. Since the ratio (masking ratio) of the opening circumference of the center intake valve port to the total opening circumference, which is the sum of the opening circumferences of the mouth, is small, reverse tumble occurs to a considerable extent and the occurrence of tumble is suppressed. ing.

  The present invention has been made in view of such a point, and the object of the present invention is to ensure a large masking ratio of the intake valve port, and to easily generate a strong vortex tumble by effectively forming the intake flow. Therefore, it is possible to provide an internal combustion engine that can improve combustion efficiency.

In order to achieve the above object, the invention according to claim 1
The ceiling surface (41) of the cylinder head (17) facing the top surface (25t) and the top surface (25t) of the piston (25) slidably fitted in the cylinder bore (16b) of the cylinder block (16). Combustion chamber (40) is formed between
The cylinder head (17) has an intake valve port (42) and an exhaust valve port (43) on the ceiling surface (41) at positions opposite to each other with respect to the cylinder axis (C) which is the central axis of the cylinder bore (16b). Is opened facing the combustion chamber (40), and the intake port (44) and the exhaust port (45) are curved away from the intake valve port (42) and the exhaust valve port (43), respectively. However, in the internal combustion engine formed to extend,
The intake valve port (42) is formed to be offset from the circular hole of the cylinder bore (16b) so as to protrude outward from the cylinder axial view and to have a crescent-shaped protrusion (42a),
A portion of the opening of the cylinder block (16) on the cylinder head (17) side of the cylinder bore (16b) facing the protruding portion (42a) of the intake valve port (42) is moved in the moving direction of the intake valve (46). The internal combustion engine is characterized in that a notched circular curved surface (55) is formed along the periphery of the bevel (46p) of the intake valve (46).

The invention according to claim 2
The internal combustion engine of claim 1,
A ratio (Rm) of the opening circumferential length of the protruding portion (42a) of the intake valve port (42) to the entire circumferential length of the opening of the intake valve port (42) is 20% to 50%.

The invention described in claim 3
The internal combustion engine according to claim 1 or 2,
The ceiling surface (41) of the cylinder head (17) has an elliptical cross-sectional shape surrounding the intake valve port (42) and the exhaust valve port (43) on both sides in the major axis direction, and has a dome-shaped recess. (51) is formed,
A squish (52, 52) surrounds the intake valve port (42) and the exhaust valve port (43) in a pair of crescent-shaped portions outside the dome-shaped recess (51) in the ceiling surface (41). Thus, it is formed in an elliptical shape.

The invention according to claim 4
The internal combustion engine according to claim 3,
Around both ends of the crescent-shaped protrusion (42a) of the intake valve port (42) at the boundary between the squish (52, 52) and the combustion chamber (40) on the outer periphery of the intake valve port (42) A pair of guide wall surfaces (53, 53) curved along the opening edge (42s) of the intake valve port (42) from each other gradually expand toward the exhaust valve port (43) side facing each other It is characterized by being formed.

The invention according to claim 5
The internal combustion engine according to any one of claims 1 to 4,
The intake valve (46) is offset to the outside of the cylinder bore (16b),
The cylinder bore (16b) is offset toward the exhaust valve port (43) with respect to the cylinder head (17) and the crankshaft (12).

The invention described in claim 6
The internal combustion engine according to claim 4 or 5,
The pair of guide wall surfaces (53, 53) are formed on an outer periphery of at least half of the side of the protruding portion (42a) of the intake valve port (42).

The invention described in claim 7
The internal combustion engine according to any one of claims 1 to 6,
The portion of the peripheral portion of the top surface (25t) of the piston (25) that faces the protruding portion (42a) of the intake valve port (42) is the end surface (46pf) of the top portion (46p) of the intake valve (46). A piston notch surface (56) is formed by being cut out in parallel with each other.

The invention described in claim 8
The internal combustion engine according to any one of claims 1 to 7,
The cast iron cylinder liner (16L) is characterized by having a flangeless shape up to the sliding area of the piston top ring (25r).

The invention according to claim 9
The internal combustion engine according to claim 1 or 2,
The maximum lift position of the bevel (46p) of the intake valve (46) is located away from the notched circular curved surface (55) in the lift direction.

  According to the internal combustion engine of the first aspect, one intake valve port (42) formed on the ceiling surface (41) of the cylinder head (17) is located outward from the circular hole of the cylinder bore (16b) in the cylinder axial direction. Since it is offset so as to have a protruding crescent-shaped protrusion (42a), the ratio of the opening peripheral length of the protruding part (42a) to the entire opening peripheral length of the intake valve port (42), that is, the masking ratio (Rm ) Can be easily secured, and the portion facing the protruding portion (42a) of the intake valve port (42) at the opening edge on the cylinder head (17) side of the cylinder bore (16b) of the cylinder block (16) is provided. A notched circular curved surface (55) is formed in the moving direction of the intake valve (46) along the peripheral edge of the bevel (46p) of the intake valve (46). 42) The intake air from the outer edge side (the protruding part side) of the intake valve (46) has a rim (46p) edge and a notched circular curved surface (55). It is necessary to pass through a very narrow gap, so that the suction into the combustion chamber (40) is hindered. Therefore, by suppressing the occurrence of reverse tumble, a strong tumble vortex can be generated.

  According to the internal combustion engine of the second aspect, the ratio of the opening circumferential length of the protruding portion (42a) of the intake valve port (42) to the entire circumferential length of the opening of the intake valve port (42), that is, the masking ratio (Rm) is 20 By setting the ratio to at least%, it is possible to form a strong tumble vortex that can clearly be expected to improve combustion efficiency.

  According to the internal combustion engine of the third aspect, the ceiling surface (41) of the combustion chamber (40) of the cylinder head (17) surrounds the intake valve port (42) and the exhaust valve port (43) on both sides in the major axis direction. A dome-shaped recess (51) is formed having an elliptical cross-sectional shape, and a squish (52, 52) is formed on each pair of crescent-shaped portions outside the dome-shaped recess (51) on the ceiling surface (41). Is formed in an elliptical shape so as to surround the intake valve port (42) and the exhaust valve port (43), so that the intake air that is blocked from being sucked from the outer edge side (the protruding part side) of the intake valve port is the intake valve It is guided by the crescent-shaped squish (52, 52) on both sides along the surface of the intake port side of the head and flows to the exhaust valve port (43) side, which can promote the tumble and increase the tumble of the stronger vortex It is possible to improve the combustion efficiency.

  According to the internal combustion engine of claim 4, the crescent shape of the intake valve port (42) is formed at the boundary between the squish (52, 52) and the combustion chamber (40) on the outer periphery of the intake valve port (42). A pair of guide wall surfaces (53, 53) curved along the opening edge (42s) of the intake valve port (42) from both ends of the protruding portion (42a) face each other and the exhaust valve port (43) The exhaust valve port (43) is formed by gradually expanding toward the side, so that a pair of guide wall surfaces (53, 53) rectify the intake air drawn from the outer periphery of the intake valve port (42). By guiding to the side, the tumble can be further promoted, and the tumble vortex can be further strengthened.

  According to the internal combustion engine of the fifth aspect, the intake valve (46) is offset to the outside of the cylinder bore (16b), and the cylinder bore (16b) is connected to the cylinder head (17) and the crankshaft (12) through the exhaust valve port ( Since it is offset to the 43) side, the friction of the piston (25) can be reduced and the intake pipe length can be increased.

  According to the internal combustion engine of the sixth aspect, the pair of guide wall surfaces (53, 53) are formed on the outer periphery of at least half of the intake valve port (42) on the protruding portion (42a) side. The pair of guide wall surfaces (53, 53) rectify the intake air drawn from the outer periphery of the valve port (42) and efficiently guide it to the exhaust valve port (43) side to further promote the tumble. The eddy current can be made even stronger.

  According to the internal combustion engine of claim 7, the portion of the peripheral surface of the top surface (25t) of the piston (25) that faces the protruding portion (42a) of the intake valve port (42) is the bulk of the intake valve (46). Since the piston notch surface (56) is formed by cutting out in parallel with the end face (46pf) of the part (46p), the intake valve (46) opens and lifts as the piston (25) descends during the intake stroke Sometimes the inflow direction of the intake air from the outer edge side and the piston notch surface (56) are perpendicular to each other, so that the intake chamber is not urged from the outer edge side of the intake valve port (42), and the reverse tumble is not promoted. Occurrence is suppressed.

  According to the internal combustion engine according to claim 8, the cylinder liner (16L) made of cast iron has a flangeless shape up to the sliding area of the top ring (25r) of the piston (25), so that the layout of the gasket is free. This improves the degree of processing and facilitates processing of the opening edge on the cylinder head 17 side of the cylinder bore 16b.

  According to the internal combustion engine of the ninth aspect, the maximum lift position of the bevel portion (46p) of the intake valve (46) is located away from the notch circular curved surface (55) in the lift direction. Most of the moving distance to lift is that the intake air from the outer edge side (the protruding part side) of the intake valve port (42) is extremely low between the rim (46p) edge of the intake valve (46) and the notched circular curved surface (55). It must pass through a narrow gap, preventing suction into the combustion chamber (40), generating a strong tumble vortex, and the intake valve (46) bulge (46p) is notched circularly curved surface (55 Combustion as a whole is achieved by increasing the amount of intake air by intake from the opening between the bulkhead portion (46p) of the intake valve (46) and the notched circular curved surface (55) at the end of the lift in the lift direction. Efficiency can be improved.

1 is a right side view of a motorcycle equipped with an internal combustion engine according to an embodiment of the present invention. It is a right side sectional view of the internal combustion engine. It is a top view of a cylinder block. It is a bottom view of a cylinder head. It is explanatory drawing of the ceiling surface of a combustion chamber. FIG. 6 is a cross-sectional view of the main part of the intake port in FIG. 5 taken along the lines XX, YY, and ZZ. It is sectional drawing of the combustion chamber periphery of a state in which the intake valve closed the intake valve port. It is sectional drawing of a combustion chamber periphery when an intake valve lifts to an intermediate valve lift position. It is sectional drawing of a combustion chamber periphery when an intake valve lifts to the maximum valve lift position. It is explanatory drawing which showed a mode that the valve effective opening area S changed as the lift of an intake valve became large. It is a graph which shows the change of the tumble ratio Rt with respect to the masking ratio Rm. It is the graph which showed change of tumble ratio Rt to valve effective opening area S for every masking ratio Rm. It is a perspective view of a piston. It is sectional drawing of a combustion chamber periphery when the intake valve in another embodiment lifts to the maximum valve lift position. It is explanatory drawing which showed a mode that the valve effective opening area S changed as the lift of an intake valve became large in the same embodiment.

Hereinafter, an embodiment according to the present invention will be described with reference to FIGS.
FIG. 1 is an overall side view of a motorcycle 1 equipped with an internal combustion engine 10 according to the present embodiment.

The body frame 2 of the motorcycle 1 has a pair of left and right main frames 2b, 2b extending rearward from the head pipe 2a and then bent downward to form steeply inclined portions 2ba, 2ba. Is bent forward to reach the lower end.
Further, a pair of left and right down frames 2c, 2c are extended substantially parallel to the steeply inclined portion 2ba of the main frame 2b in a side view when viewed downward from the head pipe 2a.

  The seat rails 2d and 2d extend rearward from the upper portions of the steeply inclined portions 2ba and 2ba of the main frames 2b and 2b, and the back connecting the central portion of the seat rails 2d and 2d and the lower portion of the steeply inclined portions 2ba and 2ba. The stays 2e and 2e support the seat rails 2d and 2d.

In the vehicle body frame 2 as described above, the front fork 3 is pivotally supported on the head pipe 2a, the front wheel 4 is pivotally supported at the lower end thereof, and the front end is pivoted on the pivot plate 2f provided at the lower part of the main frames 2b and 2b. The supported rear fork 5 extends rearward, a rear wheel 6 is pivotally supported at the rear end thereof, and a rear cushion 7 is interposed between the rear portion of the rear fork 5 and the central portion of the seat rails 2d and 2d. .
A fuel tank 8 is installed on the main frames 2b and 2b, and a seat 9 is provided behind the fuel tank 8 and supported by seat rails 2d and 2d.

  The internal combustion engine 10 mounted on the vehicle body frame 2 is an SOHC type two-valve single-cylinder four-stroke internal combustion engine. The crankshaft 20 is oriented in the vehicle body width direction with respect to the vehicle body, and the cylinder is raised slightly forward. Suspended in posture.

  A crankcase 11 that rotatably supports a crankshaft 12 of an internal combustion engine 10 includes a transmission gear mechanism 15 between a main shaft 13 and a countershaft 14 disposed behind the crankshaft 12, and a counter The shaft 14 is an output shaft, and a chain (not shown) is bridged between the rotating shaft of the rear wheel 6 and power is transmitted to the rear wheel 6.

Referring to FIG. 2, a cylinder block 16 in which one cast iron cylinder liner 16L is cast on a crankcase 11, and a cylinder head 17 is overlaid on the cylinder block 16 via a gasket. The cylinder head cover 18 covers the upper portion of the cylinder head 17 by being integrally fastened by a stud bolt.
The cylinder block 16, the cylinder head 17, and the cylinder head cover 18 stacked on the crankcase 11 extend upward from the crankcase 11 in a slightly tilted posture (see FIGS. 1 and 2).

  In this way, the inlet pipe 20 extends from the cylinder head 16 erected from the internal combustion engine 10 mounted on the vehicle body frame with a slight forward inclination to the rear via the connecting pipe 19, and the inlet pipe 20 has a butterfly-type throttle. A throttle body 21 incorporating a valve 22 is provided, and an injector 23 is mounted.

An air cleaner 24 connected to the rear end of the inlet pipe 20 is disposed in a space surrounded by the main frame 2a, the seat rail 2d, and the backstay 2e in a side view (see FIG. 1).
Further, the exhaust pipe 25 extending forward from the cylinder head 13 is bent downward and further bent rearward, and is arranged rearward along the lower surface of the crankcase 12 and on the right side of the rear wheel 6 toward the right side. It is connected to the muffler 26.

  Referring to FIG. 2, the crankcase 11 is divided into left and right parts, and the lower end portion of the cylinder liner 16L is inserted into the opening formed in the mating surface of the left and right crankcases so that the cylinder block 16 is slightly tilted forward and protrudes upward. The piston 25 is slidably fitted in the cylinder bore 16b inside the cylinder liner 16L, and the connecting rod 26 is connected between the piston pin 25p of the piston 25 and the crank pin 12p of the crankshaft 12 to provide a crank mechanism. Is configured.

A combustion chamber 40 is formed between the top surface 25t of the piston 25 sliding in the cylinder bore 16b of the cylinder block 16 and the ceiling surface 41 of the cylinder head 17 facing the same top surface 25t.
In the cylinder head 17, an intake valve port 42 and an exhaust valve port 43 are opened on the ceiling surface 41 at positions opposite to each other with respect to the cylinder axis C, which is the central axis of the cylinder bore 16b, facing the combustion chamber 40, and An intake port 44 and an exhaust port 45 are formed so as to extend from the valve port 42 and the exhaust valve port 43 while being curved away from each other.

The intake port 44 extends rearward from the intake valve port 42, communicates with the inlet pipe 20 via the connection pipe 19, and the exhaust port 45 is connected to the exhaust pipe 25.
An intake valve 46 and an exhaust valve 47 that are slidably supported by valve guides 34i and 34e fitted integrally with the cylinder head 16 are driven by a valve mechanism 30 provided on the cylinder head 13, The intake valve port 42 of the intake port 44 and the exhaust valve port 43 of the exhaust port 45 are opened and closed in synchronization with the rotation of the crankshaft 12.

  Referring to FIG. 2, a valve mechanism 30 is a valve mechanism of a SOHC type internal combustion engine in which one camshaft 31 is pivotally supported on a cylinder head 17 in the left-right direction. Rocker arm shafts 32e and 32i are supported diagonally forward and backward, and an intake rocker arm 33i is pivotally supported by the rear rocker arm shaft 32i so that it can swing freely. An exhaust rocker arm 33e can be pivoted by the front rocker arm shaft 32e. It is pivotally supported.

  One end of the intake rocker arm 33i is in contact with the intake cam lobe of the cam shaft 31, the other end is in contact with the upper end of the valve stem 46s of the intake valve 46 biased by a spring via an adjusting screw, and one end of the exhaust rocker arm 33e is The shaft 31 is in contact with the exhaust cam lobe, the other end is in contact with the upper end of the valve stem 47s of the exhaust valve 47 biased by a spring via an adjusting screw, and the intake rocker arm 33i and the exhaust rocker arm 33e are swung by the rotation of the cam shaft 31. Then, the intake valve 46 and the exhaust valve 47 are opened and closed.

  The intake valve 46 is offset to the outside of the cylinder bore 16b, and the cylinder bore 16b is offset to the exhaust valve port 43 side with respect to the cylinder head 17 and the crankshaft 12, reducing the friction of the piston 25 and increasing the length of the intake pipe .

FIG. 3 is a top view of the cylinder block 16. A circular hole of the cylinder bore 16b and a rectangular hole of the chain chamber 16c through which a chain for transmitting power to the valve mechanism 30 is inserted in the mating surface 16f with the cylinder head 17. Has been.
FIG. 4 is a bottom view of the cylinder head 17 superimposed on the cylinder block 16. The ceiling surface 41 of the combustion chamber 40 is recessed in the mating surface 17f facing the mating surface 16f of the cylinder block 16 corresponding to the cylinder bore 16b. In addition, a chain chamber 17c communicating with the chain chamber 16c is formed.

A circular opening edge 41s of the ceiling surface 41 of the combustion chamber 40 at the mating surface 17f of the cylinder head 17 coincides with the circular hole of the cylinder bore 16b.
A large-diameter intake valve port 42 is opened on the rear side of the ceiling surface 41, and an exhaust valve port 43 that is somewhat smaller in diameter than the intake valve port 42 is opened on the front side of the ceiling surface 41.
The ceiling surface 41 is provided with a plug hole 48 through which a spark plug (not shown) protrudes.

  FIG. 5 is a view of the combustion chamber 40 of the cylinder head 17 as viewed in the axial direction of the cylinder axis C, that is, as viewed in the cylinder axial direction, and referring to FIG. The circular ceiling surface opening edge 41s corresponding to the circular hole of the cylinder bore 16b of the ceiling surface 41 of the ceiling surface 41 protrudes outward from the cylinder axial direction and is offset, and the intake valve port 42 is in a crescent shape protruding from the ceiling surface opening edge 41s. Has a protruding portion 42a (the portion indicated by the dotted points in FIG. 5).

  When the ratio of the opening circumferential length of the protruding portion 42a to the entire opening circumferential length of the opening edge 42s of the intake valve port 42 is a masking rate Rm, the masking rate Rm due to the offset of the intake valve port 42 is about 20 to 50%.

  Referring to FIG. 5, the ceiling surface 41 is formed with a dome-shaped recess 51 having an elliptical cross-sectional shape surrounding the intake valve port 42 and the exhaust valve port 43 on both sides in the major axis direction. Squishes 52 and 52 are formed in a pair of right and left crescent-shaped portions outside the dome-shaped recess 51 in the ceiling surface 41, respectively.

  A pair of guide wall surfaces 53, 53 curved around the opening edge 42 s of the intake valve port 42 from both ends of the crescent protrusion 42 a of the intake valve port 42 around the outer periphery of the intake valve port 42, Opposite to each other, they are formed so as to gradually expand toward the exhaust valve port 43 side.

  FIGS. 6 (1), (2), and (3) are a cross-sectional view of the main portion of the intake port 44 in FIG. The change of the wall surfaces 53 and 53 is shown.

FIG. 6 (1) is a cross-sectional view taken along line XX closest to the protruding portion 42a, and the opening angle of the guide wall surfaces 53 and 53 facing each other is 33 degrees, while the cut surfaces are sequentially cut on the exhaust port 43 side. As shown in FIGS. 6 (2) and (3), the opening angles of the guide wall surfaces 53 and 53 are gradually expanded to 40 degrees and 53 degrees.
The pair of guide wall surfaces 53 and 53 are formed on the outer periphery of at least half of the intake valve port 42 on the protruding portion 42a side.

  With respect to the ceiling surface 41 of the combustion chamber 40 of the cylinder head 17 formed as described above, the cylinder bore 16b of the cylinder block 16 has a cylinder bore 16b as shown in FIG. 3, FIG. 8, FIG. A notch in which the rear side portion of the opening edge on the head 17 side facing the protruding portion 42a of the intake valve port 42 is cut out in the moving direction of the intake valve 46 to the maximum valve lift position along the periphery of the ridge portion 46p of the intake valve 46 A circular curved surface 55 is formed.

The cast iron cylinder liner 16L has a flangeless shape up to the sliding area of the top ring 25r of the piston 25 (see FIG. 7).
Accordingly, the degree of freedom in the layout of the gasket is improved, and the processing of the opening edge on the cylinder head 17 side of the cylinder bore 16b, that is, the processing of the cut circular surface 55 and the like is facilitated.
7, 8, and 9, the notched circular curved surface 55 is inclined at a portion covering the end surface of the cylinder liner 16 </ b> L of the aluminum alloy cylinder block 16 into which the cast iron cylinder liner 16 </ b> L is cast. Notched and formed.

  Since the peripheral edge of the bevel 46p of the intake valve 46 moves along the notch circular curved surface 55 in the vicinity of the notched circular curved surface 55, the intake valve 46 opens and moves to the maximum valve lift position (see FIG. 9). The intake air from the outer edge side (the protruding portion 42a side) of the intake valve port 42 must pass through a very narrow gap between the peripheral edge of the umbrella portion 46p of the intake valve 46 and the cut-out circular curved surface 55, and is sucked into the combustion chamber 40 Is almost obstructed and masked.

  The valve effective opening area S of the cylindrical peripheral surface, which is the locus of movement of the peripheral edge of the bevel 46p of the intake valve 46 when the intake valve 46 is lifted, is an opening through which intake air is actually taken into the combustion chamber 40.

FIG. 10 illustrates the change in the valve effective opening area S.
As the lift amount of the intake valve 46 increases from 1 mm to 5.8 mm, the valve effective opening area S is shown to increase. The masked outer edge side of the intake valve port 42 (the protruding portion 42a side) is shown. There is almost no expansion of the intake air, and the inner edge side of the intake valve port 42 gradually expands toward the exhaust valve port 43 side.

That is, the intake air that is sucked into the combustion chamber 40 from the intake valve port 42 of the intake port 44 is almost sucked from the inner edge side of the intake valve port 42 as shown in FIGS. As shown in FIG. 9, the intake air sucked into the combustion chamber 40 from the inner edge side of the port 42 is vertically lowered by descending the exhaust side of the cylinder bore 16b and then bending the flow along the piston top surface to raise the intake side. A vortex forms a so-called tumble.
Since the outer edge side of the intake valve port 42 is masked and is only slightly sucked into the combustion chamber 40, so-called reverse tumble is suppressed, and strong vortex tumble is easily generated.

The tumble state can be expressed by a tumble ratio Rt which is the number of rotations of the tumble per rotation of the crankshaft.
Tumble ratio Rt = Tumble rotation angular velocity / Crankshaft angular velocity

FIG. 11 is a graph showing the change in the tumble ratio Rt with respect to the masking ratio Rm due to the offset of the intake valve port.
As shown in FIG. 11, the larger the masking ratio Rm, the larger the tumble ratio Rt. In particular, the tumble ratio Rt increases rapidly from around the masking ratio Rm exceeding 15%. Since Rm is about 26%, the tumble ratio Rt exceeds 1.3.

  In the configuration in which one of the three intake valve ports is masked as in Patent Document 1, there is a limit to the masking ratio Rm, which is also kept within a small limit (approximately 15% or less). Therefore, the tumble ratio Rt can be kept small.

FIG. 12 shows the results of calculating the change in the tumble ratio Rt with respect to the valve effective opening area S when the masking ratio Rm is 0%, 15%, and 26%.
As shown in FIG. 12, when the masking ratio Rm is 15%, the tumble ratio Rt is almost the same as the masking ratio Rm of 0% while the valve effective opening area S is small, and the combustion efficiency is improved. However, when the masking ratio Rm is 26%, the tumble ratio Rt is larger than the masking ratio Rm of 0% since the valve effective opening area S is small. Improvement of combustion efficiency can be expected over a long period of time.

  Further, the main combustion chamber 40 has an elliptical cross-sectional shape surrounding the intake valve port 42 and the exhaust valve port 43 on both sides in the major axis direction on the ceiling surface 41 of the combustion chamber 40 of the cylinder head 17, and has a dome-shaped recess 51. And squish 52 and 52 are formed in the pair of crescent-shaped portions outside the dome-shaped recess 51 in the ceiling surface 41, respectively, so that the suction from the outer edge side (the protruding portion 42a side) of the intake valve port 42 Inhaled air is guided to the crescent-shaped squish 52, 52 on both sides along the surface of the intake port 44 side of the cap portion 46p of the intake valve 46 and rectified to the exhaust valve port 43 side to promote tumble. It is possible to generate a stronger vortex tumble and improve the combustion efficiency.

  The pair of crescent squishes 52 and 52 can be formed on the ceiling surface 41 of the combustion chamber 40 in this manner because it has one intake valve 42 and one exhaust valve port 43. When the three intake valve ports and the two exhaust valve ports are opened on the ceiling surface of the chamber, there is no room for forming a squish.

  Further, a pair of guide wall surfaces curved along the opening edge 42 s of the intake valve port 42 around both ends of the crescent-shaped protruding portion 42 a of the intake valve port 42 around the outer periphery of the intake valve port 42 of the combustion chamber 40. As shown in FIGS. 5 and 6, 53 and 53 are formed so as to gradually expand toward the exhaust valve port 43 so as to face each other. Is formed in at least half of the outer periphery on the side of the protruding portion 42a, so that a pair of guide wall surfaces 53, 53 rectify the intake air sucked from the outer periphery of the intake valve port 42, and the efficiency is increased toward the exhaust valve port 43. The tumble can be further enhanced, and the tumble vortex can be further enhanced.

  Further, as shown in FIGS. 7 and 13, a portion of the peripheral surface of the top surface 25t of the piston 25 that faces the protruding portion 42a of the intake valve port 42 is notched in parallel with the end surface 46pf of the bevel 46p of the intake valve 46. As a result, a piston notch surface 56 is formed.

  Therefore, when the intake valve 46 opens and lifts with the lowering of the piston 25 during the intake stroke, the intake inflow direction from the outer edge side and the piston notch surface (56) become perpendicular, so the outside of the intake valve port 42 Inhalation of intake air is not urged from the edge to the combustion chamber, and the occurrence of reverse tumble is further suppressed.

Although the masking ratio Rm due to the offset of the intake valve port 42 in the present embodiment is about 26%, the masking ratio Rm is preferably 20% to 50%.
By setting the masking ratio Rm to 20% or more, a strong tumble vortex that can clearly be expected to improve the combustion efficiency can be formed.

In addition, by offsetting the intake valve port 42, the valve diameter of the intake valve 46 can be increased, and a decrease in the flow rate can be prevented.
Further, it is possible to arrange the spark plug in the center of the combustion chamber 40.
Furthermore, the valve diameter of the exhaust valve 47 can be increased, and the residual gas can be reduced.

An embodiment in which the maximum valve lift amount of the intake valve 46 is made larger than in the above embodiment will be described with reference to FIGS. 14 and 15.
In the present embodiment, the maximum valve lift amount of the intake valve 46 is about 6.5 mm, and as shown in FIG. 14, the maximum lift position of the bevel 46p of the intake valve 46 is the opening edge on the cylinder head 17 side of the cylinder bore 16b. The ridge 46p of the intake valve 46 at the maximum lift position is in the lift direction from the notch circular surface 55 in a position that passes through the notch circular surface 55 of the rear side of the intake valve port 42 facing the protruding portion 42a. Away.

  FIG. 15 illustrating the change of the valve effective opening area S in the present embodiment shows the lift amount of the intake valve 46 of FIG. 10 illustrating the change of the valve effective opening area S for the above embodiment as 5.8 mm (FIG. 10). The valve effective opening area S with a maximum lift amount of 6.5 mm is added beyond (6)) and is shown in FIG. 15 (7).

  When the lift amount of the intake valve 46 exceeds 5.8 mm, as shown in FIG. 14, the bulk portion 46p of the intake valve 46 moves away from the notched circular curved surface 55 in the lift direction, as shown in FIG. In addition, the valve effective opening area S in the rear portion where the notched circular curved surface 55 is present is enlarged, and the intake air is passed through the enlarged opening between the notched circular curved surface 55 and the bevel 46p of the intake valve 46. It enters the combustion chamber 16b and increases the intake air amount.

  Therefore, until the intake valve 46 starts to open and the lift amount of the intake valve 46 is up to 5.8 mm, the outer edge side (the protruding portion 42a side) of the intake valve port 42 is masked and only a little is sucked into the combustion chamber 40. Generation of so-called reverse tumble is suppressed, strong vortex tumble can be generated, and at the end when the lift amount of intake valve 46 exceeds 5.8 mm, masking is released and tumble is suppressed by reverse tumble, but intake By increasing the amount, the combustion efficiency can be improved as a whole.

DESCRIPTION OF SYMBOLS 1 ... Motorcycle, 2 ... Body frame, 10 ... Internal combustion engine, 11 ... Crankcase, 12 ... Crankshaft, 13 ... Main shaft, 14 ... Countershaft, 15 ... Crankcase, 16 ... Cylinder block, 16b ... Cylinder bore, 17 ... Cylinder head, 18 ... Cylinder head cover, 19 ... Connecting pipe,
20 ... Inlet pipe, 21 ... Throttle body, 22 ... Throttle valve, 23 ... Injector, 24 ... Air cleaner, 25 ... Piston, 26 ... Connecting rod,
30 ... Valve mechanism, 31 ... Cam shaft, 32e, 32i ... Rocker arm shaft, 33i ... Intake rocker arm, 33e ... Exhaust rocker arm, 34i, 34e ... Valve guide,
40 ... Combustion chamber, 41 ... Ceiling surface, 42 ... Intake valve port, 42a ... Projection part, 43 ... Exhaust valve port, 44 ... Intake port, 45 ... Exhaust port, 46 ... Intake valve, 46p ... Bulk part, 46pf ... End face , 47 ... exhaust valve, 48 ... plug hole,
51 ... Domed concave part, 52 ... Squish, 53 ... Guide wall surface, 54 ..., 55 ... Notched circular curved surface, 56 ... Piston notched surface.

Claims (9)

The ceiling surface (41) of the cylinder head (17) facing the top surface (25t) and the top surface (25t) of the piston (25) slidably fitted in the cylinder bore (16b) of the cylinder block (16). Combustion chamber (40) is formed between
The cylinder head (17) has an intake valve port (42) and an exhaust valve port (43) on the ceiling surface (41) at positions opposite to each other with respect to the cylinder axis (C) which is the central axis of the cylinder bore (16b). Is opened facing the combustion chamber (40), and the intake port (44) and the exhaust port (45) are curved away from the intake valve port (42) and the exhaust valve port (43), respectively. However, in the internal combustion engine formed to extend,
The intake valve port (42) is formed to be offset from the circular hole of the cylinder bore (16b) so as to protrude outward from the cylinder axial view and to have a crescent-shaped protrusion (42a),
A portion of the opening of the cylinder block (16) on the cylinder head (17) side of the cylinder bore (16b) facing the protruding portion (42a) of the intake valve port (42) is moved in the moving direction of the intake valve (46). An internal combustion engine characterized in that a notched circularly curved surface (55) is formed along the periphery of the bevel (46p) of the intake valve (46).   The ratio (Rm) of the opening circumferential length of the protruding portion (42a) of the intake valve port (42) to the entire circumferential length of the opening of the intake valve port (42) is 20% to 50%. Item 6. An internal combustion engine according to Item 1. The ceiling surface (41) of the cylinder head (17) has an elliptical cross-sectional shape surrounding the intake valve port (42) and the exhaust valve port (43) on both sides in the major axis direction, and has a dome-shaped recess. (51) is formed,
A squish (52, 52) surrounds the intake valve port (42) and the exhaust valve port (43) in a pair of crescent-shaped portions outside the dome-shaped recess (51) in the ceiling surface (41). 3. The internal combustion engine according to claim 1, wherein the internal combustion engine is formed in an elliptical shape.   Around both ends of the crescent-shaped protrusion (42a) of the intake valve port (42) at the boundary between the squish (52, 52) and the combustion chamber (40) on the outer periphery of the intake valve port (42) A pair of guide wall surfaces (53, 53) curved along the opening edge (42s) of the intake valve port (42) from each other gradually expand toward the exhaust valve port (43) side facing each other The internal combustion engine according to claim 3, wherein the internal combustion engine is formed as follows. The intake valve (46) is offset to the outside of the cylinder bore (16b),
The cylinder bore (16b) is offset toward the exhaust valve port (43) with respect to the cylinder head (17) and the crankshaft (12), according to any one of claims 1 to 4. Internal combustion engine.   The said pair of guide wall surface (53, 53) is formed in the outer periphery of the at least half of the protrusion part (42a) side of the said intake valve port (42), The Claim 4 or Claim 5 characterized by the above-mentioned. Internal combustion engine.   The portion of the peripheral portion of the top surface (25t) of the piston (25) that faces the protruding portion (42a) of the intake valve port (42) is the end surface (46pf) of the top portion (46p) of the intake valve (46). The internal combustion engine according to any one of claims 1 to 6, wherein a piston notch surface (56) is formed by notching in parallel with the piston.   The internal combustion engine according to any one of claims 1 to 7, wherein the cylinder liner (16L) made of cast iron has a flangeless shape extending to a sliding area of the top ring (25r) of the piston. .   The internal combustion engine according to claim 1 or 2, wherein the maximum lift position of the bevel (46p) of the intake valve (46) is located away from the notch circular curved surface (55) in the lift direction. organ.

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