JP2014070547A - Intake system for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an intake system for an internal combustion engine that can easily secure rigidity even when a partition plate in an intake passage is formed to be long within an intake port and can generate tumbles of strong vortex flows.SOLUTION: In an intake system for an internal combustion engine, an intake passage (P) is partially partitioned into an upper intake passage (Up) and a lower intake passage (Lp) by a partition plate (60), and intake air flowing in the upper intake passage (Up) and the lower intake passage (Lp) is controlled by an intake director valve (65) installed upstream of the partition plate (60) on the downstream side of a throttle valve (22). The partition plate (60) comprises: an inlet pipe side partition plate (61) formed in an inlet pipe (20); and an intake port side partition plate (62) formed within an intake port (44). A downstream end (61b) of the inlet pipe side partition plate (61) and an upstream end (62a) of the intake port side partition plate (62) are connected to each other in a vertically overlapping state.

Description

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

  In order to improve fuel efficiency in the low load region of an internal combustion engine, intake air taken in the combustion chamber generates tumble, and fuel is sent around the spark plug at the upper portion of the combustion chamber to stratify the combustion efficiency. There is what constituted the intake device.

  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 into the center of the combustion chamber from the inner edge near the cylinder shaft (center axis of the cylinder bore) flows down the exhaust side of the cylinder bore while flowing toward the exhaust side, and then flows along the piston top surface. A vertical vortex, so-called tumble, is formed by bending and raising the intake side.

  Therefore, in order to increase the proportion of the intake air from the inner edge near the cylinder shaft of the intake valve port, the inside of the intake port is partitioned into upper and lower passages by a partition wall, and the lower passage is opened and closed upstream of the partition wall. By providing an intake control valve that closes the lower passage immediately after engine startup, intake air flowing through the passage above the intake port is drawn from the inner edge of the intake valve port, which is an extension of the upper passage. There is an example of an intake device that generates a strong vortex tumble (see Patent Document 1).

JP 2008-151078 A

In the intake device of Patent Document 1, a cylindrical passage portion of the port liner is inserted or integrally formed on the upstream side of the intake port, and a partition wall is integrally formed in the passage portion of the port liner.
The partition wall protrudes greatly from the passage portion to the downstream side of the intake port.

Since the partition wall largely protrudes from the passage portion, it is difficult to ensure rigidity. Therefore, the amount of protrusion is limited, and the downstream end of the partition wall is the intake port as shown in FIG. It is located in front of the intake valve.
Therefore, the intake air flowing through the passage on the upper side of the partition wall of the intake port that generates the tumble diffuses downward just before entering the combustion chamber past the downstream end of the partition wall, and the combustion chamber from the inner edge side of the intake valve port It is difficult to generate a strong vortex tumble due to a decrease in air intake.

  The present invention has been made in view of the above points. The object of the present invention is to ensure rigidity even if the partition plate in the intake passage is formed long in the intake port. It is the point which provides the intake device of the internal combustion engine which can generate | occur | produce the tumble of a strong vortex | eddy_current by extending to the downstream near.

In order to achieve the above object, the invention according to claim 1
Combustion between the top surface of the piston (25) slidably fitted in the cylinder bore (16b) of the cylinder block (16) and the ceiling surface (41) of the cylinder head (17) facing the top surface Chamber (40) is constructed,
While the intake port (44) and the exhaust port (45) are curved away from each other from the intake valve port (42) and the exhaust valve port (43) opened in the ceiling surface (41) of the cylinder head (17). Formed to extend,
An inlet pipe (20) is connected to the intake port (44) to form a continuous intake passage (P),
The inlet pipe (20) is provided with a throttle valve (22),
The intake passage (P) is partly connected to the central portion of the combustion chamber (40) by the partition plate (60), and the lower intake passage (Lp) is connected to the outer peripheral portion of the combustion chamber (40). Divided into
The intake air distribution valve (65) provided downstream of the throttle valve (22) and upstream of the partition plate (60) controls the intake air flowing through the upper intake passage (Up) and the lower intake passage (Lp). And
In the intake device for an internal combustion engine in which the intake control valve (65) is driven and controlled by the intake control means (71),
The partition plate (60) consists of an inlet pipe side partition plate (61) formed in the inlet pipe (20) and an intake port side partition plate (62) formed in the intake port (44),
An internal combustion engine characterized in that a downstream end portion (61b) of the inlet pipe side partition plate (61) and an upstream end portion (62a) of the intake port side partition plate (62) are overlapped and connected to each other. It is an intake device.

The invention according to claim 2
The intake device for an internal combustion engine according to claim 1,
An injector (23) is provided on the upper intake passage (Up) side of the inlet pipe (20) so as to inject fuel toward the downstream side of the upper intake passage (Up),
The downstream end portion (61b) of the inlet pipe side partition plate (61) is connected so as to overlap the upstream end portion (62a) of the intake port side partition plate (62).

The invention described in claim 3
The intake device for an internal combustion engine according to claim 2,
The injector (23) is configured to inject fuel toward the downstream side of the connection portion (61b, 62a) between the intake port side partition plate (62) and the inlet pipe side partition plate (61). It is characterized by.

The invention according to claim 4
The intake device for an internal combustion engine according to any one of claims 1 to 3,
The inlet pipe side partition plate (61) is made of resin,
The downstream end portion (61b) of the inlet pipe side partition plate (61) is pressed against and overlapped with the upstream end portion (62a) of the intake port side partition plate (62) with a pressing force due to elastic deformation.

The invention according to claim 5
The intake device for an internal combustion engine according to any one of claims 1 to 4,
The inlet pipe side partition plate (61) is characterized in that the downstream end (61b) protrudes from the downstream opening end of the inlet pipe (20) and enters the intake port (44).

According to the intake device for an internal combustion engine according to claim 1, the intake pipe formed in the inlet pipe side partition plate (61) and the intake port (44) in which the partition plate (60) is formed in the inlet pipe (20). It is divided into a side partition plate (62), and the downstream end portion (61b) of the inlet pipe side partition plate (61) and the upstream end portion (62a) of the intake port side partition plate (62) are overlapped and connected to each other. Therefore, even if the inlet pipe side partition plate (61) and the intake port side partition plate (62) protrude from the inlet pipe (20) and the intake port (44), respectively, the protrusion amount is small, and rigidity is easily achieved. It can be secured.
Therefore, it is possible to extend the intake port side partition plate (62) to the downstream near the combustion chamber, and guide the intake air flowing through the upper intake passage (Up) to the vicinity of the intake valve port without almost diffusing in the middle. It can flow into the combustion chamber from the inner edge side of the valve port and generate a strong vortex tumble.

  According to the intake device for an internal combustion engine according to claim 2, the injector (23) injects fuel toward the downstream side of the upper intake passage (Up) on the upper intake passage (Up) side of the inlet pipe (20). Since the downstream end portion (61b) of the inlet pipe side partition plate (61) is connected so as to overlap the upstream end portion (62a) of the intake port side partition plate (62), the injector (23 ) Is less likely to enter the overlapping surface of the connecting portions (61b, 62a), and fuel can be prevented from leaking into the lower intake passage (Lp).

  According to the intake device for an internal combustion engine according to claim 3, the injector (23) is located downstream of the connection portion (61b, 62a) of the intake port side partition plate (62) with the inlet pipe side partition plate (61). The fuel injected from the injector (23) does not leak into the lower intake passage (Lp), and the fuel is injected into the intake port side partition plate (62) where the temperature is high. Thus, liquefaction of the fuel can be suppressed.

  According to the intake device for an internal combustion engine according to claim 4, the downstream end portion (61b) of the inlet pipe side partition plate (61) made of resin is connected to the upstream end portion (61a) of the intake port side partition plate (62). ) With a pressing force due to elastic deformation and overlap, so that without using an adhesive or the like, the downstream end (61b) of the inlet pipe side partition plate (61) and the upstream end portion (62a) of the intake port side partition plate (62) ) Can be easily brought into close contact with each other and the workability is good.

  According to the intake device for an internal combustion engine according to claim 5, the inlet pipe side partition plate (61) has a downstream end portion (61b) protruding beyond the downstream open end of the inlet pipe (20) so that the intake port (44) As the inlet pipe (20) is assembled, the intake pipe is visually inhaled with the downstream end (61b) of the inlet pipe side partition plate (61) protruding from the downstream opening end of the inlet pipe (20) as a guide. The inlet pipe (20) can be attached while being relatively aligned with the upstream end (62a) of the port side partition plate (62), and the workability is excellent.

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. It is principal part sectional drawing of the internal combustion engine in a low load state. It is the VII-VII sectional view taken on the line of FIG. It is the VIII-VIII sectional view taken on the line of FIG. It is a perspective view of an intake distribution valve. It is the XX sectional view taken on the line of FIG. It is a graph which shows the control of the intake distribution valve opening degree (phi) with respect to throttle opening (theta), and the change of the tumble ratio Rt. It is principal part sectional drawing of the internal combustion engine in a medium load state. It is principal part sectional drawing of the internal combustion engine in a high load state. It is a disassembled perspective view of the intake distribution valve of a modification. It is sectional drawing equivalent to FIG. 10 of the example which uses the same intake distribution valve. It is a graph which shows the control of the intake distribution valve opening degree (phi) with respect to throttle opening (theta) in another embodiment, and the change of the tumble ratio Rt.

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 12 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 with the internal combustion engine 10 mounted on the vehicle body frame slightly tilted forward via the connecting pipe 19, and the inlet pipe 20 is provided with a throttle valve 22. A built-in butterfly-type throttle body 21 is provided, an injector 23 is mounted, and an intake air distribution valve 65 described later is further provided.

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 27 extending forward from the cylinder head 17 is bent downward and further bent rearward, and is arranged rearward along the lower surface of the crankcase 11 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 through the connection pipe 19, and the exhaust port 45 is connected to the exhaust pipe 27.
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.

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.

  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 an opening edge on the cylinder head 17 side of the cylinder bore 16b as shown in FIGS. A notch curved surface 55 is formed in which the rear portion of the intake valve port 42 facing the protruding portion 42a is cut out in the moving direction of the intake valve 46 along the periphery of the ridge portion 46p of the intake valve 46 to the maximum valve lift position. ing.

  As shown in FIG. 6, the cut-out circular curved surface 55 is obliquely cut out at a portion covering the end face of the flangeless cylinder liner 16L of the aluminum alloy cylinder block 16 into which the cast iron cylinder liner 16L is cast. Is formed.

  Since the peripheral edge of the cap portion 46p of the intake valve 46 moves along the notched circular curved surface 55 and close to the notched circular curved surface 55, the intake valve port 42 is opened while the intake valve 46 is opened and moved to the maximum valve lift position. The intake air from the outer edge side (the protruding portion 42a side) of the intake valve 46 must pass through a very narrow gap between the peripheral edge of the umbrella portion 46p of the intake valve 46 and the notched circular curved surface 55, and the intake into the combustion chamber 40 is almost hindered and masked. It is in the state that was done.

Therefore, it is masked from the outer edge side of the intake valve port 42 and only a little is sucked into the combustion chamber 40, and the intake from the inner edge side of the intake valve port 42 is mainly performed. It has become.
It should be noted that the maximum valve lift position of the intake valve 46 may be at a position slightly beyond the notched circular curved surface 55.

  A portion of the peripheral surface of the top surface 25t of the piston 25 facing the protruding portion 42a of the intake valve port 42 is cut out in parallel with the end face 46pf of the ridge portion 46p of the intake valve 46 to form a piston cutout surface 56. (See FIG. 6) When the intake valve 46 opens and lifts as the piston 25 descends during the intake stroke, the intake flow direction from the outer edge and the piston notch surface (56) are perpendicular to each other. Inhalation of intake air is not promoted from the outer edge side of the mouth 42 to the combustion chamber 40, and the occurrence of reverse tumble is further suppressed.

  In the intake system, the intake passage P extending from the inlet pipe 20 to the intake port 44 via the connecting pipe 19 is separated from the upper intake passage Up by the partition plate 60 from the downstream portion of the inlet pipe 20 to the curved portion of the intake port 44. A side intake passage Lp is partitioned.

Whereas the cylinder head 17 is made of an aluminum alloy including the portion that forms the intake port 44, the inlet pipe 20 is made of resin.
Therefore, the partition plate 60 includes an inlet pipe side partition plate 61 formed integrally with the inlet pipe 20 and an intake port side partition plate 62 formed integrally with the cylinder head 17 in the intake port 44. The downstream end portion 61b of the partition plate 61 and the upstream end portion 62a of the intake port side partition plate 62 are connected to each other so as to overlap each other.

2 and 6, the inlet pipe side partition plate 61 has a downstream end 61b protruding from the downstream opening end of the inlet pipe 20 into the intake port 44, and the intake port side partition plate 62 is The upstream end 62 a reaches the upstream opening end of the intake port 44.
The downstream end 61b of the resin inlet pipe side partition plate 61 that has entered the intake port 44 is pressed and overlapped with the upstream end portion 62a of the intake port side partition plate 62 with a pressing force due to elastic deformation. ing.

The intake passage P has a circular cross section. As shown in FIG. 6, the partition plate 60 that partitions the intake passage P up and down includes an inlet pipe side partition plate 61 and an intake port side partition plate 62. The upper cross-sectional area of the upper intake passage Up is located above the passage center line Cp, which is the central locus of the maximum vertical width of the intake passage P (in the case of the intake passage P, a circular central locus which is a passage section). It is smaller than the passage sectional area of the lower intake passage Lp (see FIG. 7).
As shown in FIG. 7, in the case of the main intake passage P, the ratio of the cross-sectional area of the upper intake passage Up and the lower intake passage Lp is approximately 3 to 7 from the upstream opening to the downstream opening.

The intake port side partition plate 62 is bent along the shape of the intake port 44, and the downstream end portion 62b of the intake port side partition plate 62 is an intake valve stem 46s of the intake valve 46 located at the curved portion of the intake port 44. As shown in FIG. 8, the downstream end 62b is formed with a recess 62u that is recessed in a U shape from the leading edge, and the U-shaped recess 60u extends into the intake port 44. The guide 34i penetrates.
The outer diameter of the valve guide 34i is equal to the width of the U-shaped recess 60u, and the valve guide 34i is fitted to the back of the U-shaped recess 60u so that no gap is formed. The intake passage P is vertically divided as close as possible to the intake valve port 42 of the intake port 44.

  Therefore, referring to FIG. 6, the upper intake passage Up leads from the inner edge side (cylinder shaft C side) of the intake valve port 42 to the central portion of the combustion chamber 40, and the lower intake passage Lp extends outside the intake valve port 42. It leads to the outer peripheral portion of the combustion chamber 40 from the edge side (the protruding portion 42a side).

  As shown in FIG. 6, the injector 23 attached to the inlet pipe 20 faces the upper intake passage Up, and is an upstream end portion that is a connecting portion 61b, 62a of the intake port side partition plate 62 with the inlet pipe side partition plate 61. It is attached to inject fuel toward the downstream side of 62a.

An intake distribution valve 65 is provided in the inlet pipe 20 downstream of the throttle valve 22 and upstream of the inlet pipe side partition plate 61.
The intake distribution valve 65 is a flap valve configured by integrally extending a plate-like valve body 67 from a rotating shaft 66 pivotally supported by the inlet pipe 20, and the plate-like valve body 67 is shaken by a motor drive mechanism 72. Be moved.

As shown in FIGS. 9 and 10, a semi-cylindrical notch recess 65d cut out in a plane parallel to the rotation center line Cv of the rotation shaft 66 is formed in the intake passage P between the left and right bearings. A plate-like valve element 67 extends along the notch bottom surface of the notch recess 65d.
In addition, a recessed portion slightly cut out is formed also on the back side of the notched recessed portion 65d of the rotation shaft 66.
The plate-like valve body 67 has a semi-elliptical shape in which the axial width of the notch recess 65d is a short diameter, and a base end portion having a straight side abuts the notch bottom surface of the notch recess 65d to form a recess on the back surface Then, a screw 68 is screwed in from the back via a washer 68w, and the plate-like valve body 67 is integrally fastened to the rotating shaft 66.
It may be fastened with rivets.

  When the base end portion of the plate valve body 67 is attached to the notch recess 65 d of the rotating shaft 66, the base end edge 67 a of the base end portion of the plate valve body 67 is an extended peripheral surface of the outer peripheral surface of the rotating shaft 66. The notch recess 65 d remains on the surface of the base end portion of the plate-like valve body 67 as a recess.

  Such an intake distribution valve 65 directs the rotation center line Cv of the rotation shaft 66 in parallel to the upstream end edge 61aa of the upstream end portion 61a of the inlet pipe side partition plate 61 directed in the horizontal direction, and In a state of being positioned near the lower end of the upstream edge 61aa, the rotary shaft 66 is pivotally supported by the inlet pipe 20, and the plate-like valve body 67 is directed from the rotary shaft (66) toward the intake upstream side. It is attached with the posture which extended.

  The plate-shaped valve body 67 swings up and down integrally with the rotation of the rotation shaft (66), and contacts with a semi-elliptical outer peripheral edge inclined to the inner peripheral surface of the intake passage P having a circular cross section. Then, half of the intake passage P can be completely closed.

The rotation shaft 66 of the intake distribution valve 65 is pivotally supported at a position where the rotation center line Cv is orthogonal to the passage center line Cp of the intake passage P.
The throttle valve 22 pivotally supported in the inlet pipe 20 on the upstream side of the intake distribution valve 65 rotates about a rotation center line oriented in the horizontal direction perpendicular to the passage center line Cp of the intake passage P. It is a butterfly valve.

  The intake divide valve 65 swings with the tip toward the upstream throttle valve 22 to distribute the intake air downstream from the throttle valve 22 up and down and change the ratio of intake air flowing through the upper intake passage Up and the lower intake passage Lp. can do.

  An ECU (electronic control unit) 70 that controls the internal combustion engine 10 includes an intake control means 71. The intake control means 71 analyzes the operation state of the internal combustion engine 10 and drives the throttle valve 22 and the injector 23 of the intake system. Although controlled, the intake distribution valve 65 is also driven and controlled by the intake control means 71.

Referring to FIG. 6, the throttle opening θ of the throttle valve 22 is a fully open state when it is rotated from the fully closed state and becomes parallel to the intake passage, and indicates a load state of the internal combustion engine 10.
The intake distribution valve 65 is controlled to swing according to the load state of the internal combustion engine 10, and the intake distribution valve opening φ, which is the swing angle of the intake distribution valve 65, is the intake distribution in the low load state shown in FIG. The swing angle increases clockwise in FIG. 6 with the low load position of the valve 65 as the reference 0 degree.

The tumble state can be represented by a tumble ratio Rt which is the number of rotations of the tumble per revolution of the crankshaft 12.
Tumble ratio Rt = Tumble rotation angular velocity / Crankshaft angular velocity If the tumble ratio Rt is large, a strong vortex tumble is generated.

FIG. 11 shows a change in the intake distribution valve opening φ and the change in the tumble ratio Rt for swinging the intake distribution valve 65 in accordance with the throttle opening θ.
Hereinafter, the swing control of the intake distribution valve 65 and the tumble ratio Rt according to the load state of the internal combustion engine 10 will be considered with reference to FIG.

When the internal combustion engine 10 is in a low load operation state, as shown in FIG. 6, the throttle valve 22 is opened small (throttle opening θ: small), and the intake distributing valve 65 has a leading edge of the plate-like valve body 67. It is positioned at a low load position (intake distribution valve opening φ = 0 degree) in contact with the lower peripheral surface of the intake passage P.
When the leading edge of the plate-like valve element 67 of the intake distributing valve 65 is in contact with the lower peripheral surface of the intake passage P, the base end edge 67a above the rotation center line Cv of the plate-like valve element 67 is the inlet pipe. It is in contact with the lower surface of the upstream end 61a of the side partition 61, and therefore the upstream opening of the lower intake passage Lp is completely closed by the intake distribution valve 65.
Therefore, the intake distribution valve 65 can distribute the intake air substantially upward to flow through the upper intake passage Up.

  Accordingly, the intake air that has passed through the slightly opened opening of the throttle valve 22 is guided by the intake air distribution valve 65 to the relatively narrow upper intake passage Up, almost entirely upward, so that the intake air becomes high speed. Is guided to the vicinity of the intake valve port 42 by the partition plate 60 extending to the intake valve stem 46s located at the center of the combustion chamber 40 from the inner edge side (cylinder axis C side) of the intake valve port 42. As shown in FIG. 6, a strong vortex tumble is generated (the tumble ratio Rt is increased).

  The intake valve port 42 is offset so as to have a crescent-shaped protruding portion 42a protruding outward from the circular hole of the cylinder bore 16b in the cylinder axial direction, and the outer edge side (the protruding portion 42a side) of the intake valve port 42 is masked. In addition, since there is almost no intake air passing through the lower intake passage Lp, there is no intake air to be sucked into the combustion chamber 40 from the outer edge side of the intake valve port 42, no reverse tumble that prevents tumble is generated, and tumble is generated more strongly. The tumble ratio Rt becomes high, and the combustion efficiency at low load can be improved.

When the internal combustion engine 10 is in a medium load operation state, as shown in FIG. 12, the throttle valve 22 opens to an intermediate opening (throttle opening θ: medium), and the intake distribution valve 65 has a leading edge above the intake passage P. Since it is positioned at a medium load position (intake distribution valve opening φ = β degrees) approaching the peripheral surface, the intake distribution valve 65 distributes the intake air so that the intake rate is smaller from below.
Therefore, as shown by the arrows in FIG. 12, sufficient intake air flows through the lower intake passage Lp, but intake through the upper intake passage Up is suppressed.

  When the leading edge of the plate-like valve element 67 of the intake distribution valve 65 is separated from the lower peripheral surface of the intake passage P, the base edge 67a of the plate-like valve element 67 becomes the upstream end 61a of the inlet pipe side partition plate 61. The notch recessed portion 65d of the intake distribution valve 65 forms an intermediate passage Mp with the upstream end portion 61a of the inlet pipe side partition plate 61.

  Since the intermediate passage Mp communicates with the lower intake passage Lp, most of the intake air distributed up and down by the intake distribution valve 65 flows into the upper intake passage Up, but the upper intake passage Up. A portion of the intake air that has not been able to enter can smoothly flow into the lower intake passage Lp through the intermediate passage Mp without stagnation, and the disturbance of the intake air flow can be suppressed and the upper intake passage Up The intake air flowing into the engine is further suppressed.

  Therefore, even if the suppressed intake air flowing through the upper intake passage Up enters the combustion chamber 40 from the inner edge side of the intake valve port 42, only a weak vortex tumble is generated, and further, the combustion chamber starts from the outer edge side of the intake valve port 42. Since some intake air is sucked into the outer peripheral portion of 40 and a reverse tumble is generated to suppress the tumble, the tumble is suppressed as much as possible, and the tumble ratio Rt is lowered.

  When the internal combustion engine 10 is in a high load operation state, as shown in FIG. 13, the throttle valve 22 is fully open (throttle opening θ: fully open), and the intake distribution valve 65 is the upstream end 61a of the inlet pipe side partition plate 61. Is positioned at a high load position (intake distribution valve opening φ = α degrees) on the plane including the passage center line Cp of the intake passage P, and the intake distribution valve 65 causes the intake air to be in a ratio of 1: 1. The intake air is distributed up and down.

  However, as shown in FIG. 10, which is a sectional view taken along line XX of FIGS. 13 and 13, an intermediate passage Mp is formed between the upstream end 61 a of the inlet pipe side partition plate 61 in the notch recess 65 d of the intake distribution valve 65. Therefore, a part of the intake air distributed upward by the intake air distribution valve 65 flows smoothly into the lower intake passage Lp without staying straight through the intermediate passage Mp. The air flows into the upper intake passage Up and the lower intake passage Lp at a ratio of approximately 3 to 7 partitioned by the inlet pipe side partition plate 61.

  Therefore, as indicated by arrows in FIG. 13, sufficient intake air flows through the upper intake passage Up and the lower intake passage Lp, and the intake air that has flowed through the upper intake passage Up enters the combustion chamber 40 from the inner edge side of the intake valve port 42. The intake air that has been inhaled to generate a tumble and flows through the lower intake passage Lp enters the combustion chamber 40 from the outer edge side of the intake valve port 42 while being masked, and causes some reverse tumble, but from the upper intake passage Up Since a sufficient amount of intake air is inhaled, a moderate vortex tumble with a relatively high tumble ratio Rt can be generated, and the intake efficiency can be well maintained by sufficient intake.

  As described above, the intake device of the internal combustion engine 10 has the rotation center line Cv of the rotation shaft 66 of the intake distribution valve 65 oriented parallel to the upstream end edge 61aa of the partition plate (60), and the upstream end A plate-like valve body 67, which is positioned in the vicinity of the lower edge of the edge 61aa and pivotally supported by the inlet pipe 20 and extends from the pivot shaft 66 toward the upstream side of the intake air, swings up and down, so that the throttle valve (22) The ratio of the intake air flowing through the upper intake passage Up and the lower intake passage Lp can be changed by distributing the intake air downstream from the upper and lower sides, so that the strength of the tumble vortex is adjusted according to the load state of the internal combustion engine Thus, the combustion efficiency can be optimized.

  The intake device of the present internal combustion engine 10 is divided into an inlet pipe side partition plate 61 formed in the inlet pipe 20 and an intake port side partition plate 62 formed in the intake port 44. Since the downstream end 61b of the plate 61 and the upstream end 62a of the intake port side partition plate 62 are connected to each other so as to overlap each other, the inlet pipe side partition plate 61 and the intake port side partition plate 62 are respectively connected to the inlet pipe 20 and Even if it protrudes from the intake port 44, the protrusion amount is small, and rigidity can be secured easily.

  Even if the intake port side partition plate 62 is long, rigidity is ensured. Therefore, the downstream end 62b of the intake port side partition plate 62 is connected to the intake valve stem 46s of the intake valve 46 located at the curved portion of the intake port 44. And the recess 62u of the downstream end 62 extends over the intake valve stem 46s, and the intake port side partition plate (62) extends to the downstream near the combustion chamber, and thus flows through the upper intake passage (Up). It is possible to guide the intake air to the vicinity of the intake valve port without almost diffusing and flow into the center of the combustion chamber from the inner edge side of the intake valve port toward the exhaust side to generate a strong vortex tumble ( (See FIG. 6).

  An injector 23 is provided on the upper intake passage Up side of the inlet pipe 20 so as to inject fuel toward the downstream side of the upper intake passage Up, and the downstream end 61b of the inlet pipe side partition plate 61 is connected to the intake port side partition plate 62. Since it is connected so as to overlap the upstream end portion 62a, the fuel injected by the injector 23 is difficult to enter the overlapping surface of the connecting portions 61b and 62a, and prevents the fuel from leaking into the lower intake passage Lp. In addition, the fuel can be efficiently used for combustion to reduce fuel consumption.

  Since the injector 23 is configured to inject fuel toward the downstream side of the connecting portions 61b and 62a of the intake port side partition plate 62 with the inlet pipe side partition plate 61, the injected fuel of the injector 23 is injected into the lower intake passage. The fuel is less likely to leak into Lp and the fuel is injected into the intake port side partition plate 62 having a high temperature, so that liquefaction of the fuel can be suppressed.

  Since the downstream end portion 61b of the inlet pipe side partition plate 61 formed of resin is pressed against and overlapped with the upstream end portion 61a of the intake port side partition plate 62 with a pressing force due to elastic deformation, the inlet pipe is not used. The downstream end portion 61b of the side partition plate 61 and the upstream end portion 62a of the intake port side partition plate 62 can be easily brought into close contact with each other and workability is good.

  Since the inlet pipe side partition plate 61 has a structure in which the downstream end 61b protrudes from the downstream opening end of the inlet pipe 20 and enters the intake port 44, the downstream opening end of the inlet pipe 20 is assembled when the inlet pipe 20 is assembled. The inlet pipe 20 can be attached to the cylinder head 17 while visually aligning with the upstream end portion 62a of the intake port side partition plate 62 by visually observing the downstream end portion 61b of the inlet pipe side partition plate 61 protruding further. Excellent workability.

A modification of the intake distribution valve, which is a flap valve, will be described with reference to FIGS.
In the intake distribution valve 80, a pair of cutout recesses 81a and 81b are formed in a portion corresponding to the inside of the intake passage P of the rotation shaft 81 and cut out in a plane parallel to the central axis plane including the rotation center axis Cv. A slit 81s is formed in the flat plate portion 81c between the cutout recesses 81a and 81b so as to penetrate the flat plate portion 81c in parallel with both flat surfaces.
The left and right widths of the slits 81s are equal to the inner diameter of the intake passage P, like the cutout recesses 81a and 81b.
Mounting holes 81ch and 81ch are drilled in two places on the left and right of the flat plate portion 81c.

The base end portion of the plate-like valve body 82 is fitted into the slit 81s of the flat plate portion 81c of the rotating shaft 81.
The plate-like valve body 82 has a semi-elliptical shape in which the left and right widths of the slits 81 s have a short diameter, and mounting holes 82 h and 82 h are provided on the left and right of the base end portion having a straight side, and the flat plate portion of the rotating shaft 81. The holes are drilled corresponding to the mounting holes 81ch and 81ch of 81c.

As shown in FIG. 14, the base end portion of the plate-like valve body 82 is fitted into the slit 81 s of the flat plate portion 81 c of the rotary shaft 81, and the mounting holes 81 ch and 81 ch of the rotary shaft 81 and the plate-like valve body 82 are connected. With the mounting holes 82h and 82h, the ends of the tubular rivets 83 and 83 projecting from the notch recess 81b through the tubular rivets 83 and 83 through the mounting holes 81ch and 81ch and the mounting holes 82h and 82h from the notch recess 81b side. By caulking, a plate-like valve body 82 is attached to the rotation shaft 81 to form an intake distribution valve 80.
The intake distribution valve 80 is attached to the inlet pipe 20 according to the above-described embodiment with the rotation center line Cv of the rotation shaft 81 positioned near the lower portion of the upstream end 61a of the inlet pipe side partition plate 61.

  The plate-shaped valve body 82 swings up and down integrally with the rotation of the rotation shaft 81, and when the internal combustion engine 10 is in a low load operation state, the semicircular elliptical outer peripheral edge is a passage of the intake passage P having a circular cross section. When contacting the inner peripheral surface in an inclined posture, the end edge of the flat plate portion 81c of the rotation shaft 81 is in contact with the lower surface of the upstream end portion 61a of the inlet pipe side partition plate 61, and the upstream side opening of the lower intake passage Lp is It is completely closed by the intake distribution valve 65, and intake air passes only through the upper intake passage Up, so that tumble can be generated strongly.

When the internal combustion engine 10 is in the middle and high load operation state, the upstream opening of the lower intake passage Lp is opened, and the notch recess 81a of the intake distribution valve 80 is intermediate between the upstream end 61a of the inlet pipe side partition plate 61. The passage Mp is formed, and a part of the intake air that has not been able to enter the upper intake passage Up can flow smoothly into the lower intake passage Lp through the intermediate passage Mp without stagnation. can do.
15 is a cross-sectional view corresponding to the cross-sectional view taken along the line XX of FIG. 13 in a high-load operation state, in which the notch recess 81a of the intake distribution valve 80 is located between the upstream end 61a of the inlet pipe side partition plate 61. An intermediate passage Mp is formed in the middle.

  In the above embodiment, the intake valve port 42 protrudes outward from the circular ceiling surface opening edge 41 s corresponding to the circular hole of the cylinder bore 16 b of the ceiling surface 41 of the combustion chamber 40 and is offset to the combustion. Although the protruding portion of the outer peripheral portion of the chamber is masked, the present invention is also applied to an internal combustion engine using a normal cylinder head in which the intake valve port 42 does not protrude from the ceiling surface opening edge 41s.

  That is, even if the outer peripheral portion of the combustion chamber 40 is not masked, when the internal combustion engine 10 is in a low load operation state, the intake distribution valve 65 closes the upstream opening of the lower intake passage Lp (intake distribution valve opening φ) = 0 degree), by distributing the intake air substantially upward and flowing through the upper intake passage Up, the intake air that is guided to the relatively narrow upper intake passage Up and flows at a high speed is on the inner edge side of the intake valve port 42 (cylinder It is sucked at a high speed from the axis C side) to the center of the combustion chamber 40 toward the exhaust side, and a strong vortex tumble can be generated.

  When the internal combustion engine 10 is in the middle and high load operation state, the upstream opening of the lower intake passage Lp is opened, and the notch recess 81a of the intake distribution valve 80 is located between the upstream end 61a of the inlet pipe side partition plate 61. The intermediate passage Mp is formed in the upper intake passage Up so that a portion of the intake air that has not fully entered the upper intake passage Up can flow smoothly into the lower intake passage Lp through the intermediate passage Mp without stagnation. Can be suppressed.

  Further, in the present embodiment, when the intake distribution valve 65 is in the middle load operation state, the middle load position (intake distribution valve opening φ = β) where the leading edge of the intake distribution valve 65 approaches the upper peripheral surface of the intake passage P However, without such control, the intake valve opening φ is increased in direct proportion to the increase in throttle opening θ from the low load operation state to the high load operation state. You may make it make it.

  When the control is performed so that the intake valve opening φ is increased in direct proportion to the increase in the throttle opening θ from the low load operation state to the high load operation state without masking the outer periphery of the combustion chamber 40. FIG. 16 shows a change in the intake distribution valve opening φ and the change in the tumble ratio Rt for swing control of the intake distribution valve 65 according to the throttle opening θ.

  When the internal combustion engine 10 is in a low load operation state, the throttle valve 22 is opened small (throttle opening θ: small), and the intake distributing valve 65 has a tip edge of the plate-like valve body 67 on the lower side of the intake passage P. Positioned at a low load position (intake distribution valve opening φ = 0 degree) in contact with the surface, the upstream opening of the lower intake passage Lp is completely closed by the intake distribution valve 65.

  Therefore, the intake air that flows while being guided by the relatively narrow upper intake passage Up is sucked at high speed from the inner edge side (cylinder shaft C side) of the intake valve port 42 toward the center of the combustion chamber 40 toward the exhaust side. Thus, a strong vortex tumble is generated, the tumble ratio Rt is increased, and the combustion efficiency at low load can be improved.

  As the throttle opening θ increases and the load operating state of the internal combustion engine 10 increases, when the intake distribution valve opening φ is increased in direct proportion to the throttle opening θ, the intake distribution valve 65 is moved to the lower intake passage. Since the upstream opening of Lp is opened and the intake air flows through the lower intake passage Lp, the intake air distributed to the upper intake passage Up also flows through the lower intake passage Lp through a partially formed intermediate passage Mp. By reducing the intake air flowing through Up, even when entering the combustion chamber 40 from the inner edge side of the intake valve port 42, only a weak vortex tumble is generated, and the tumble ratio Rt decreases.

When the throttle opening θ becomes larger than a certain level, the intake distribution valve opening φ enters the upper intake passage Up from before the intake pipe side partition plate 61 is parallel to the upstream end 61a (intake distribution valve opening φ = α degrees). Since the ratio of the intake air to be distributed does not change, the stable weak vortex tumble continues and the tumble ratio Rt becomes substantially constant.
In this way, it is possible to optimize the combustion efficiency by adjusting the strength of the tumble vortex.

DESCRIPTION OF SYMBOLS 1 ... Motorcycle, 2 ... Body frame, 10 ... Internal combustion engine, 11 ... Crankcase, 12 ... Crankshaft, 13 ... Main shaft, 14 ... Countershaft, 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 , 46s ... Intake valve stem, 47 ... Exhaust valve, 48 ... Plug hole,
51 ... Dome-shaped recess, 52 ... Squish, 53 ... Guide wall, 55 ... Notched circular surface, 56 ... Piston notched surface,
60 ... partition plate, 61 ... inlet pipe side partition plate, 61a ... upstream end, 61b ... downstream end, 62 ... intake port side partition plate, 62a ... upstream end, 62b ... downstream end,
65 ... Intake distribution valve, Cv ... Center of rotation, 65d ... Notch recess, 66 ... Rotating shaft, 67 ... Plate-shaped valve element, 67a ... Base edge, 68 ... Screw,
70 ... ECU, 71 ... Intake control means, 72 ... Motor drive mechanism,
80 ... Intake distribution valve, 81 ... Rotating shaft, 81a, 81b ... Notch recess, 81s ... Slit, 82 ... Plate-shaped valve element, 82, 83 ... Tubular rivet,
P: intake passage, Cp: passage center line, Up: upper intake passage, Lp: lower intake passage, Mp: intermediate passage.

Claims (5)

Combustion between the top surface of the piston (25) slidably fitted in the cylinder bore (16b) of the cylinder block (16) and the ceiling surface (41) of the cylinder head (17) facing the top surface Chamber (40) is constructed,
While the intake port (44) and the exhaust port (45) are curved away from each other from the intake valve port (42) and the exhaust valve port (43) opened in the ceiling surface (41) of the cylinder head (17). Formed to extend,
An inlet pipe (20) is connected to the intake port (44) to form a continuous intake passage (P),
The inlet pipe (20) is provided with a throttle valve (22),
The intake passage (P) is partly connected to the central portion of the combustion chamber (40) by the partition plate (60), and the lower intake passage (Lp) is connected to the outer peripheral portion of the combustion chamber (40). Divided into
The intake air distribution valve (65) provided downstream of the throttle valve (22) and upstream of the partition plate (60) controls the intake air flowing through the upper intake passage (Up) and the lower intake passage (Lp). And
In the intake device for an internal combustion engine in which the intake control valve (65) is driven and controlled by the intake control means (71),
The partition plate (60) consists of an inlet pipe side partition plate (61) formed in the inlet pipe (20) and an intake port side partition plate (62) formed in the intake port (44),
An internal combustion engine characterized in that a downstream end portion (61b) of the inlet pipe side partition plate (61) and an upstream end portion (62a) of the intake port side partition plate (62) are overlapped and connected to each other. Intake device. An injector (23) is provided on the upper intake passage (Up) side of the inlet pipe (20) so as to inject fuel toward the downstream side of the upper intake passage (Up),
The downstream end (61b) of the inlet pipe side partition plate (61) is connected so as to overlap the upstream end portion (62a) of the intake port side partition plate (62). An intake device for an internal combustion engine as described.   The injector (23) is configured to inject fuel toward the downstream side of the connection portion (61b, 62a) between the intake port side partition plate (62) and the inlet pipe side partition plate (61). The intake device for an internal combustion engine according to claim 2. The inlet pipe side partition plate (61) is made of resin,
The downstream end portion (61b) of the inlet pipe side partition plate (61) is pressed and overlapped with the upstream end portion (62a) of the intake port side partition plate (62) with a pressing force due to elastic deformation. The intake device for an internal combustion engine according to any one of claims 1 to 3.   The inlet pipe side partition plate (61) has a downstream end portion (61b) protruding from the downstream opening end of the inlet pipe (20) and entering the intake port (44). Item 5. The intake device for an internal combustion engine according to any one of Items 4 to 5.

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