WO2023053346A1 - 内燃機関の吸気装置 - Google Patents
内燃機関の吸気装置 Download PDFInfo
- Publication number
- WO2023053346A1 WO2023053346A1 PCT/JP2021/036152 JP2021036152W WO2023053346A1 WO 2023053346 A1 WO2023053346 A1 WO 2023053346A1 JP 2021036152 W JP2021036152 W JP 2021036152W WO 2023053346 A1 WO2023053346 A1 WO 2023053346A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- intake
- valve
- passage
- internal combustion
- combustion engine
- Prior art date
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 186
- 238000005192 partition Methods 0.000 claims abstract description 80
- 239000000446 fuel Substances 0.000 claims description 80
- 238000002347 injection Methods 0.000 claims description 42
- 239000007924 injection Substances 0.000 claims description 42
- 238000011144 upstream manufacturing Methods 0.000 claims description 35
- 238000004891 communication Methods 0.000 claims description 33
- 239000000203 mixture Substances 0.000 description 7
- 230000013011 mating Effects 0.000 description 5
- 230000007246 mechanism Effects 0.000 description 5
- 230000008859 change Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 239000012212 insulator Substances 0.000 description 3
- 101000904177 Clupea pallasii Gonadoliberin-1 Proteins 0.000 description 1
- 239000000579 Gonadotropin-Releasing Hormone Substances 0.000 description 1
- 101000857870 Squalus acanthias Gonadoliberin Proteins 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000004927 fusion Effects 0.000 description 1
- XLXSAKCOAKORKW-AQJXLSMYSA-N gonadorelin Chemical compound C([C@@H](C(=O)NCC(=O)N[C@@H](CC(C)C)C(=O)N[C@@H](CCCNC(N)=N)C(=O)N1[C@@H](CCC1)C(=O)NCC(N)=O)NC(=O)[C@H](CO)NC(=O)[C@H](CC=1C2=CC=CC=C2NC=1)NC(=O)[C@H](CC=1N=CNC=1)NC(=O)[C@H]1NC(=O)CC1)C1=CC=C(O)C=C1 XLXSAKCOAKORKW-AQJXLSMYSA-N 0.000 description 1
- 230000003434 inspiratory effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000000746 purification Methods 0.000 description 1
- 230000003584 silencer Effects 0.000 description 1
- 238000000638 solvent extraction Methods 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 230000003313 weakening effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B27/00—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues
- F02B27/02—Use of kinetic or wave energy of charge in induction systems, or of combustion residues in exhaust systems, for improving quantity of charge or for increasing removal of combustion residues the systems having variable, i.e. adjustable, cross-sectional areas, chambers of variable volume, or like variable means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
- F02B31/04—Modifying induction systems for imparting a rotation to the charge in the cylinder by means within the induction channel, e.g. deflectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
- F02B31/04—Modifying induction systems for imparting a rotation to the charge in the cylinder by means within the induction channel, e.g. deflectors
- F02B31/06—Movable means, e.g. butterfly valves
- F02B31/08—Movable means, e.g. butterfly valves having multiple air inlets, i.e. having main and auxiliary intake passages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
Definitions
- the present invention relates to an intake system for an internal combustion engine, which has a partition in an intake passage leading to a combustion chamber and a resonator.
- Patent Document 1 discloses a structure in which an intake passage of an internal combustion engine is divided into a main flow path and a sub-flow path by a partition portion to generate a tumble flow.
- a tumble control valve is provided downstream of a throttle valve, and a partition plate portion, which is a partition portion, is provided downstream of the tumble control valve from an inlet pipe to an intake port.
- the portion divides the intake passage into an upper and lower sub passage and an upper main passage.
- the lower secondary passage serves as a tumble flow passage, and the tumble control valve substantially opens and closes the upper main passage.
- the tumble control valve is closed, and the opening of the throttle valve provided upstream of the tumble control valve is also relatively small. Therefore, at this time, in the intake stroke from when the intake valve opens to when it closes, the volume on the intake port side increases as the piston descends. If the inflow is not in time, the inside of the intake port will suddenly become a negative pressure state, and the flow inside the intake passage will become weak.
- An object of the present invention is to provide an internal combustion engine in which a partition is provided in an intake passage on the downstream side of a throttle valve, and to provide a configuration that makes it possible to improve intake of intake air when the opening of the throttle valve is relatively small. to do.
- one aspect of the present invention is a partition extending in the intake flow direction so as to divide an intake passage on the downstream side of the throttle valve into a plurality of flow paths; and a resonator provided so as to communicate with the intake passage on the downstream side of the intermediate portion of the partition in the intake air flow direction.
- the resonator is provided so as to communicate with the intake passage on the downstream side of the intermediate portion of the partition in the intake air flow direction. Therefore, when the throttle valve is throttled, i.e., when the opening of the throttle valve is relatively small, such as when the internal combustion engine is operating in a low-load region, the intake air can flow from the resonator side into the intake passage on the downstream side of the partition. Therefore, the inflow of intake air from the intake passage to the combustion chamber can be improved.
- the axis of the downstream outlet of the communication passage that connects the resonator to the intake passage is designed to face the combustion chamber.
- the resonator is directly connected via a communication passage to a cylinder head of the internal combustion engine defining a ceiling surface of the combustion chamber. This makes it easier to guide the air flowing in from the resonator more directly into the combustion chamber.
- the partition section divides the intake passage into first intake air intakes arranged in order in the first direction. It is provided so as to be divided into a flow path and the second intake flow path. Thereby, for example, a tumble flow can be generated by the intake air flowing into the combustion chamber from the first intake passage.
- the communication passage that connects the resonator to the intake passage communicates with a downstream portion of the second intake passage or a downstream junction of the first intake passage and the second intake passage.
- the intake air from the resonator can be introduced into the combustion chamber from the second intake passage side or the downstream confluence portion.
- a deflector configured to deflect intake air from the first intake passage into the combustion chamber to one side of the imaginary plane.
- the flow channel cross-sectional area of the second intake flow channel is larger than the flow channel cross-sectional area of the first intake flow channel, and the fuel injection valve is provided on the second intake flow channel side.
- the intake air can be strongly introduced into the combustion chamber from the first intake passage, and the fuel sprayed from the fuel injection valve can be suitably injected into the combustion chamber while maintaining the flow of the intake air in the first intake passage. be able to guide.
- the fuel injection direction of the fuel injection valve is substantially parallel to the axis of the downstream outlet of the communication passage that connects the resonator to the intake passage.
- the air flow from the resonator can be made substantially the same as the fuel injection direction, so that the atomized fuel can be more effectively diffused in the combustion chamber.
- a tumble control valve that opens and closes the second intake flow path is further provided at an upstream end of the partition or upstream of the upstream end.
- the intake air from the first intake passage can more preferably generate a tumble flow in the combustion chamber.
- a notch is further provided at a downstream outlet of the communication passage connecting the resonator to the intake passage.
- FIG. 1 is a sectional view of an internal combustion engine and its surroundings according to an embodiment of the present invention
- FIG. FIG. 2 is a right side view of the cylinder head of the internal combustion engine of FIG. 1 and its vicinity
- FIG. 3 is a cross-sectional view of the internal combustion engine of FIG. 1 along line III-III of FIG. 2
- 2 is a bottom view of the cylinder head of the internal combustion engine of FIG. 1
- FIG. FIG. 2 is a front view of a three-dimensional model of an intake system and an exhaust system in the vicinity of a combustion chamber of the internal combustion engine of FIG. 1
- FIG. 6 is a plan view of the three-dimensional model of FIG. 5
- FIG. 6 is a cross-sectional view of the three-dimensional model of FIG.
- FIG. 6 is a cross-sectional view along line VIII-VIII in FIG. 6, mainly of the intake system in the three-dimensional model of FIG. 5;
- FIG. 6 is a cross-sectional view along line IX-IX in FIG. 6, mainly of the intake system in the three-dimensional model of FIG. 5;
- FIG. 6 is a cross-sectional view of mainly the intake system in the three-dimensional model of FIG. 5, taken along line XX of FIG. 6, and is a view schematically showing sprayed fuel.
- FIG. 9 is a perspective view of the three-dimensional model of FIG. 8;
- FIG. 8 is a cross-sectional view of the three-dimensional model of FIG. 5 along line XII-XII of FIG.
- FIG. 7 is a perspective view of the three-dimensional model of FIG. 6 and schematically shows sprayed fuel.
- FIG. 6 is a perspective view of the three-dimensional model of FIG. 5 and schematically shows sprayed fuel.
- FIG. 2 is a schematic view of the combustion chamber and its surroundings of the internal combustion engine of FIG. 1 as seen from the cylinder axis direction;
- FIG. 2 is a diagram schematically showing the direction of a communication passage that connects a resonator to an intake passage in the internal combustion engine of FIG. 1;
- FIG. 2 is a schematic view of the internal combustion engine of FIG. 1 as viewed from the upstream side in the intake flow direction to the intake valve port side;
- FIG. 4 is a schematic diagram of an intake passage showing a region downstream of a throttle valve;
- FIG. 18 shows the pressure variation at the point indicated in FIG. 17 during the cycle of the internal combustion engine;
- 4 is an operation map of a throttle valve and a tumble control valve;
- 4 is a graph showing the relationship between throttle opening and intake flow rate;
- 4 is a graph showing the correlation between throttle opening and vortex intensity;
- FIG. 11 is a view showing a confluence portion of a resonator with an intake passage in an intake device of a modified example;
- FIG. 1 is a cross-sectional view of an internal combustion engine 10 to which an intake system S according to one embodiment is applied and its surroundings.
- FIG. 2 is a right side view of the cylinder head of the internal combustion engine of FIG. 1 and its vicinity.
- 3 is a cross-sectional view of the internal combustion engine of FIG. 1 along line III-III of FIG. 2; 4 is a bottom view of the cylinder head of the internal combustion engine of FIG. 1.
- FIG. 1 is a cross-sectional view of an internal combustion engine 10 to which an intake system S according to one embodiment is applied and its surroundings.
- FIG. 2 is a right side view of the cylinder head of the internal combustion engine of FIG. 1 and its vicinity.
- the internal combustion engine 10 is a SOHC type 2-valve, single-cylinder, 4-stroke internal combustion engine, and is suspended in an upright posture with the crankshaft 12 oriented in the width direction of the vehicle body and the cylinders tilted slightly forward.
- a transmission gear mechanism 20 is formed between a main shaft 16 arranged behind the crankshaft 12 and a counter shaft 18 that is an output shaft. ing.
- a cylinder block 22 with one cylinder liner 22L cast and a cylinder head 24 are superimposed on the cylinder block 22 via a gasket, and are integrally fastened with stud bolts to form a cylinder.
- a cylinder head cover 26 covers the top of the head 24 .
- a cylinder block 22, a cylinder head 24, and a cylinder head cover 26, which are superimposed on the crankcase 14, extend upward from the crankcase 14 in a slightly forward-inclined posture.
- the internal combustion engine 10 is not limited to the single-cylinder internal combustion engine configured as described above, and may be an internal combustion engine configured in various types.
- crankcase 14 is split left and right, and the lower ends of the cylinder liners 22L are fitted into openings formed in the mating surfaces of the left and right crankcases.
- the cylinder block 22 is slightly inclined forward and protrudes upward from the crankcase 14 .
- a piston 28 is fitted in a cylinder bore 22b inside the cylinder liner 22L so as to be reciprocally slidable.
- a connecting rod 30 connects between the piston pin 28p of the piston 28 and the crankpin 12p of the crankshaft 12 to form a crank mechanism.
- a combustion chamber 32 is formed in the The combustion chamber 32 is generally defined by the cylinder bore 22b of the cylinder block 22, the top surface 28t of the piston 28, and the ceiling surface 24t of the cylinder head 24.
- an intake valve port 34 and an exhaust valve port 36 are opened on the ceiling surface 24t at mutually opposite positions with respect to the cylinder axis C, which is the central axis of the cylinder bore 22b, facing the combustion chamber 32.
- An intake port 38 and an exhaust port 40 extend from the valve port 34 and the exhaust valve port 36 while curving in directions away from each other.
- the cylinder head 24 is defined with a single intake port 38 and a single exhaust port 40 .
- An intake valve 44 and an exhaust valve 46 which are respectively slidably supported by valve guides 42i and 42e integrally fitted to the cylinder head 24, are driven by a valve mechanism 48 provided on the cylinder head 24,
- the intake valve opening 34 of the intake port 38 and the exhaust valve opening 36 of the exhaust port 40 are opened and closed in synchronization with the rotation of the crankshaft 12 . That is, the cylindrical intake valve guide 42i is fitted integrally with the curved outer wall portion 38a of the intake port 38 in the cylinder head 24.
- An intake valve 44 slidably supported by an intake valve guide 42i opens and closes the intake valve 44 facing the combustion chamber 32 of the intake port 38 .
- an exhaust valve 46 slidably supported by an exhaust valve guide 42e integrally fitted to the curved outer wall portion 40a of the exhaust port 40 in the cylinder head 24 is an exhaust valve opening facing the combustion chamber 32 of the exhaust port 40. Open and close 36.
- the valve mechanism 48 is a valve mechanism for an SOHC internal combustion engine in which a single camshaft 48a is rotatably supported on the cylinder head 24 in the left-right direction.
- Rocker arm shafts 47i and 47e are supported diagonally above the cam shaft 48a in the front and rear direction, the rear rocker arm shaft 47i pivotally supports the intake rocker arm 48i at its central portion, and the front rocker arm shaft 47e swings the exhaust rocker arm 48e.
- the central part is freely pivoted.
- One end of the intake rocker arm 48i contacts the intake cam lobe of the camshaft 48a, and the other end contacts the upper end of the valve stem 44s of the spring-biased intake valve 44 via an adjusting screw.
- One end of the exhaust rocker arm 48e contacts the exhaust cam lobe of the camshaft 48a, and the other end contacts the upper end of the valve stem 46s of the spring-biased exhaust valve 46 via an adjusting screw.
- the intake rocker arm 48i and the exhaust rocker arm 48e are swung by the rotation of the cam shaft 48a, thereby driving the intake valve 44 and the exhaust valve 46 to open and close.
- the camshaft 48a protrudes leftward from the bearing, and a cam chain sprocket 50 is pivotally supported at the left end thereof.
- the camshaft 48a rotates in the same direction in synchronization with the crankshaft 12 at half the number of rotations thereof.
- cam chain chambers 22c and 24c which are rectangular holes through which the cam chain 52 is inserted, are formed.
- the right side wall of the cylinder head 24 is fitted with a spark plug 54, which is an ignition means, fitted toward the combustion chamber 32.
- a cylinder internal pressure sensor (not shown) may be fitted toward the combustion chamber 32 in the vicinity of the ignition plug 54 .
- FIG. 4 is a bottom view of the cylinder head 24 superimposed on the cylinder block 22, and the cylinder axis C in the internal combustion engine 10 is represented by a dot.
- the ceiling surface 24t of the combustion chamber 32 is recessed corresponding to the cylinder bore 22b on the mating surface 24f of the cylinder head 24 facing the mating surface of the cylinder block 22.
- the combustion chamber 32 does not have the shape of a so-called pent-roof combustion chamber, and the ceiling surface 24t is formed into a concave curved surface and is generally hemispherical.
- a cam chain chamber 24c communicating with the cam chain chamber 22c is formed on the left side of the combustion chamber 32 in the mating surface 24f.
- the circular opening edge 24e of the ceiling surface 24t of the combustion chamber 32 on the mating surface 24f of the cylinder head 24 matches the circular hole of the cylindrical cylinder bore 22b.
- a large-diameter intake valve port 34 opens behind the cylinder axis C on the ceiling surface 24t, and an exhaust valve port 36 with a slightly smaller diameter than the intake valve port 34 opens on the front side of the cylinder axis C on the ceiling surface 24t.
- a plug hole 56 for projecting the electrode of the spark plug 54 into the combustion chamber 32 is formed on the right side of the cylinder axis C of the ceiling surface 24t. That is, the spark plug 54 is not positioned at the center of the ceiling surface 24t, but is provided offset from the center.
- the spark plug 54 is positioned on one side of the imaginary plane IS when defining the imaginary plane IS extending from the intake valve port 34 side to the exhaust valve port 36 side and extending parallel to the cylinder axis C.
- the ignition plug 54 is arranged on one side opposite to the cam chain chamber 24c with respect to the imaginary plane IS. 4, the virtual plane IS is defined so as to pass through the central portion 34a of the intake valve port 34 and the central portion 36a of the exhaust valve port 36.
- the imaginary plane IS is defined so as to pass through the center portion 34a of the intake valve port 34 and the center portion 36a of the exhaust valve port 36 and extend parallel to the cylinder axis C.
- the center portion 34a of the intake valve port 34 is preferably the center of the intake valve port 34
- the center portion 36a of the exhaust valve port 36 is also preferably the center of the exhaust valve port 36.
- both the intake valve opening 34 and the exhaust valve opening 36 are substantially circular, and their respective centers are center portions 34a and 36a.
- Each of the intake valve opening 34 and the exhaust valve opening 36 may be circular or elliptical, for example.
- the spark plug 54 includes a center electrode 54e and side electrodes (or ground electrodes) 54f.
- the side electrode 54f has a base end portion 54g on the side of the plug main body portion 54b of the spark plug 54 and a curved portion 54h that curves and extends from the base end portion 54g so as to cover the tip portion of the central electrode 54e.
- a base end portion 54g of the side electrode 54f extends substantially parallel to the axis of the plug main body portion 54b of the spark plug 54. As shown in FIG.
- the upstream end of the intake port 38 opens toward the upper side of the cylinder head 24 and is connected to the inlet pipe 58 via an insulator 63 to form a continuous intake passage 60.
- On the upstream side of the inlet pipe 58 is a throttle.
- a body 62 is connected.
- the throttle body 62 has an intake passage 62a having a substantially circular cross section forming a part of the intake passage 60 communicating with the combustion chamber 32 of the internal combustion engine 10, and the upstream side of the intake passage 62a is connected to an air cleaner device (not shown).
- the throttle body 62 is rotatably supported in the throttle body 62 by a throttle valve shaft 62b that intersects the central axis of the intake passage 62a perpendicularly to the flow direction of intake air in the intake passage 62a. It has a throttle valve 62c that can variably control the flow passage area of the air intake passage 62a to open and close the intake passage 62a.
- the throttle valve 62c is of the butterfly type, and has a throttle valve shaft 62b and a disc-shaped valve body 62d that is fixed to the throttle valve shaft 62b and rotates integrally with the throttle valve shaft 62b.
- the throttle valve 62c is rotatable clockwise in FIG. 1 in the valve opening direction by the driver's operation or the like. It is urged counterclockwise in the valve closing direction so as to be in the fully closed position in contact with the wall surface.
- a downstream end of the exhaust port 40 opens downward from the cylinder head 24 and is connected to an exhaust pipe (not shown) to form a continuous exhaust passage 64 .
- An exhaust purification device and a silencer may be provided downstream of the exhaust passage 64 .
- the intake device S for giving a tumble swirl or tumble flow of the fuel/air mixture in the combustion chamber 32 in order to obtain more favorable combustion of the fuel or mixture in the combustion chamber 32, that is, longitudinal rotation.
- the intake device S includes a partition portion 70 provided in the intake passage 60 so as to divide the intake passage 60 into a plurality of sections.
- the intake passage 60 is divided into a plurality of intake passage portions 72, 74 by the partition portion 70.
- the intake passage 60 is divided into the plurality of intake passage portions 72, 74 in the direction of the cylinder axis C.
- the intake passage 60d on the downstream side of the throttle valve 62c is divided along the intake air flow direction by the partition portion 70 continuing from the inlet pipe 58 to the intake port 38, and the passing intake air tumbles in the combustion chamber 32. It is partitioned into a tumble flow path 72 that is an intake flow path section configured to allow turbulence to occur, and a main flow path 74 that is an intake flow path section excluding the tumble flow path 72 .
- the intake channel portion 72 that can be a tumble channel for generating a tumble flow in the combustion chamber 32 is called a tumble channel, which corresponds to the first intake channel, and the main channel 74 corresponds to the second intake channel. do.
- the tumble flow path 72 is an intake air flow path for generating a tumble flow in the combustion chamber 32 when the opening degree of the throttle valve 62c is low, for example, when the internal combustion engine 10 is operated under a low load.
- the tumble flow path 72 may be referred to as a sub-passage.
- the partition portion 70 extending in the direction of the intake air flow in a plate shape divides the downstream side of the intake passage 60 substantially in the vertical direction, that is, divides the downstream side of the intake passage 60 into substantially the cylinder axis C. It is provided so as to bisect in direction, here extending substantially parallel to an axis extending in the direction of intake air flow.
- the channel cross-sectional area of the tumble channel 72 is smaller than the channel cross-sectional area of the main channel 74, that is, the channel cross-sectional area of the main channel 74 is larger than the channel cross-sectional area of the tumble channel 72.
- the partition part 70 may be provided so that the cross-sectional area of the tumble flow channel 72 is larger than the cross-sectional area of the main flow channel 74, or they may be substantially the same.
- the lower portion of the intake passage 60 partitioned by the partition portion 70 serves as the tumble passage 72, and the upper portion thereof serves as the main passage 74, but in this specification they are not limited to their vertical arrangement.
- the terms “upper” and “lower” for the intake passages 60, 60d and the like refer to the direction from the crankshaft 12 to the cylinder head 24 or the cylinder head cover 26 in the direction of the cylinder axis C.
- the “upward” direction, the direction opposite to this "upward” direction, that is, the direction from the cylinder head 24 side to the crankshaft 12 side is called the “downward” or “downward” direction. It doesn't mean “below”.
- the “up” or “up” direction corresponds to the first direction
- the "down” or “down” direction corresponds to the second direction.
- a tumble control valve 75 is further provided upstream of the partition 70 and downstream of the throttle valve 62c. As shown in FIG. 1, a tumble control valve 75 is arranged at an upstream end portion 70u of the partition portion 70 formed in the inlet pipe 58. As shown in FIG. The tumble control valve 75 has a tumble valve shaft 75a and a tumble valve body 75b that is fixed to the tumble valve shaft 75a and rotates together. The tumble valve body 75b is formed in a plate-like semi-disk that closes the opening of the main flow path 74 near the upstream end 70u of the partition section 70 in the inlet pipe 58. As shown in FIG. A tumble valve shaft 75a is attached to one linear end of the tumble valve body 75b.
- the tumble valve shaft 75a is rotatably supported on the inlet pipe 58 so as to be parallel to the plane of the partition portion 70 in the width direction of the intake passage 60, more specifically, parallel to the throttle valve shaft 62b. and is appropriately rotated by an actuator (not shown). As the tumble valve shaft 75a rotates, the tumble valve body 75b also rotates, the opening degree of the main flow path 74 is changed, and as the amount of intake air flowing through the main flow path 74 is adjusted, the intake air amount of the tumble flow path 72 also increases. adjusted.
- the tumble control valve 75 is provided so as to be continuous with the upstream end 70u of the partition 70, but is arranged with a gap from the upstream end 70u of the partition 70. good too.
- the tumble control valve 75 can also be called an intake control valve, a tumble valve, or a TCV.
- the tumble control valve 75 and the throttle valve 62c are electronically controlled as described below, but are not limited to being electronically controlled. It may be a valve controlled by
- the internal combustion engine 10 is provided with fuel injection valves 76 and 78 .
- One fuel injection valve (hereinafter referred to as the first fuel injection valve) 76 is provided upstream of the upstream end 70u of the partition 70, and is located upstream of the upstream end 70u of the intake passage 60. It is arranged to inject fuel into the part.
- the other fuel injection valve (hereinafter referred to as the second fuel injection valve) 78 is provided to inject fuel into the intake port 38 .
- the second fuel injection valve 78 is provided on the main flow path 74 side.
- the second fuel injection valve 78 is provided so as to face the main flow path 74, and is provided in the inlet pipe 58 here.
- the second fuel injection valve 78 is provided to inject fuel from the main flow path 74 side and supply the fuel to the combustion chamber 32 via the intake port 38 .
- the second fuel injection valve 78 is attached to the upper wall of the member defining the intake passage 60.
- the present disclosure does not limit the number of fuel injection valves to two, and may be one, for example. Only 78 can be provided.
- the resonator 77 is connected to the intake passage 60 via the communicating pipe 77a.
- the communication pipe 77a is provided so as to communicate the resonator 77 with the intake passage 60 on the downstream side of the intermediate portion 70m of the partition portion 70 in the intake flow direction.
- the communication pipe 77a is positioned so as to communicate with the intake port 38 defined in the cylinder head 24, particularly to communicate with the downstream portion 74d of the main flow passage 74 and its downstream side. Therefore, the downstream outlet portion 77c of the communicating passage 77b connecting the resonator 77 of the communicating pipe 77a to the intake passage 60 opens to the intake port 38 defined by the cylinder head 24. As shown in FIG.
- the communication passage 77b is defined by the communication pipe 77a that connects the resonator 77 and the cylinder head 24, but is not limited to this, and may be configured as part of the resonator 77 or part of the cylinder head 24.
- a downstream portion 74d of the main flow path 74 is a portion of the main flow path 74 downstream of the intermediate portion 70m of the partition portion 70.
- the intermediate portion 70m of the partition portion 70 is a portion located in the middle of the length of the partition portion 70 extending in the intake air flow direction. For example, when the partition 70 includes only the partition main body 92, it is a portion located in the middle of the length in the intake air flow direction.
- An ECU (electronic control unit) 80 that controls the internal combustion engine 10 has a configuration as a so-called computer, and includes an intake control section 82, a fuel injection control section 84 and an ignition control section 85.
- the ECU 80 analyzes the operating state of the internal combustion engine 10 based on the outputs from various sensors such as an engine rotation speed sensor and an engine load sensor, and controls the operation of the throttle valve 62c by the intake control unit 82, and performs tumble control. For example, it controls the operation of the valve 75 . Further, the ECU 80 controls each operation of the fuel injection valves 76 and 78 by the fuel injection control section 84 based on the analyzed operating state of the internal combustion engine 10 . Further, the ECU 80 controls the operation of the spark plug 54 by the ignition control section 85 based on the analyzed operating state of the internal combustion engine 10 .
- the ECU 80 stores programs and various data for these controls.
- FIG. 7 shows a cross-sectional view of the three-dimensional model M along the line VII-VII in FIG. 6, and FIG. 8 shows a cross-sectional view of mainly the intake system of the three-dimensional model M along the line VIII-VIII in FIG. 9 shows a cross-sectional view of mainly the intake system of the three-dimensional model M along line IX-IX in FIG. 6, and FIG. 1 shows a cross-sectional view of an intake system;
- FIG. 11 is a perspective view of the three-dimensional model M shown in FIG. 12 shows a cross-sectional view of the three-dimensional model M at a position along line XII-XII in FIG.
- the three-dimensional model M includes an intake port 38 from the downstream end of the inlet pipe 58 and an exhaust port 40.
- the outer surface 79 of the intake system in the three-dimensional model M corresponds to the inner surface 58s of the inlet pipe 58, the inner surface 63s of the insulator 63, and the inner wall surface 24s of the cylinder head 24, which are members that define the downstream side of the intake passage 60. It has portions, some of which correspond to the surface 70s of the partition 70, and some of which correspond to the surface 90s of the offset portion 90, which will be described later.
- the tumble flow path 72 and the main flow path 74 overlap vertically in the cylinder axis C direction.
- the downstream end 72d of the tumble channel 72 is narrower in the horizontal direction than the main channel 74, and is biased to the right.
- a portion 72d of the tumble flow path 72 defined by the inner wall surface 24s of the cylinder head 24 is biased to the right with respect to the intake valve port 34, as shown in FIG.
- the partition 70 has an offset portion 90 provided on the downstream side of the partition 70.
- the offset portion 90 is narrower than the upstream end portion (upstream end) 70u of the partition portion 70 in the lateral direction (LH-RH direction) intersecting with the cylinder axis C, that is, the width direction.
- the offset portion 90 extends from one side to the other side of the valve axis of the intake valve 44 when the intake passage 60 faces the intake valve 44 in the direction in which the intake air flows from the upstream side to the downstream side, ie, the intake air flow direction. It is the narrow portion of the partition 70 in the width direction that can be defined as the direction. As shown in FIG.
- the width W1 in the width direction of the upstream end portion located on the upstream end portion 70u side of the partition portion 70 in the portion defined by the cylinder head 24 is larger than the width W1 in the width direction.
- the width W2 in the width direction of the downstream end portion 72d is clearly narrow.
- the deviation portion 90 is biased in one direction in the left-right direction, that is, in the width direction.
- the downstream end portion 72d of the tumble flow path 72 is partitioned so as to deviate to the right RH side (see FIGS. 10 and 12). Therefore, the offset portion 90 on the downstream side of the partition portion 70, which at least partially partitions the offset downstream end portion 72d of the tumble flow path 72, is offset to the right RH side here. Therefore, in FIG. 1, the cylinder axis C extends parallel to the plane of the paper, and the width direction extends substantially perpendicular to the plane of the paper. Therefore, it is indicated by a two-dot dashed line instead of a solid line. In this way, on the downstream side in the intake air flow direction, the tumble flow passage 72 is designed to be biased in the width direction, and along with this, the deviated portions 90 are partitioned to be biased to the same side in the width direction.
- FIG. 8 the relationship between the partition section 70 and the offset section 90 on the downstream side thereof, the tumble flow path 72 and the main flow path 74 will be further described with reference to FIGS. 8 to 10.
- FIG. 8 the relationship between the partition section 70 and the offset section 90 on the downstream side thereof, the tumble flow path 72 and the main flow path 74 will be further described with reference to FIGS. 8 to 10.
- the tumble channel 72 and the main channel 74 are completely separated.
- the width of the tumble channel 72 and the width of the main channel 74 are substantially the same.
- the partition part 70 extends to the inner wall surface 24s of the cylinder head 24 at both ends in the width direction between the tumble flow path 72 and the main flow path 74, and is connected to the upstream side of the deviation part 90.
- a body portion 92 extends.
- the surfaces 70s of the partition 70 and the surfaces 92s of the partition main body 92 thereof are denoted by reference numerals.
- the tumble channel 72 and the main channel 74 are completely separated, but the width of the tumble channel 72 is narrower than the width of the main channel 74.
- the partition portion 70 extends to the inner wall surface 24s of the cylinder head 24 at both ends in the width direction between the tumble flow passage 72 and the main flow passage 74, and extends from the partition body portion 92 to the offset portion 90.
- the reference numerals are given to the portions corresponding to the surface 70s of the partition portion 70. As shown in FIG.
- the tumble flow path 72 and the main flow path 74 are partially connected at the cut point in FIG. 10 (the line XX in FIG. 6). Further, in this cut plane, the surface 70s of the partition 70 extends in the width direction and also in the vertical direction, and is biased to the right. As a result, the partition 70 transitions from the main partition 92 to the offset portion 90, and the intake port 38 has enough cylinder space in the intake port 38 to the extent that the offset portion 90 does not completely separate the tumble flow path 72 and the main flow path 74. It can be seen that it extends leftward from the right part of the inner wall surface 24s of the head 24 .
- the tumble flow path 72 and the main flow path 74 are partitioned so that the main flow path 74 and the tumble flow path 72 communicate with each other in the region where the deviated portion 90 extends in the intake air flow direction.
- the offset portion 90 connected to the partition body portion 92 extends downstream of the partition body portion 92 of the partition portion 70 so that a part of the partition body portion 92 extends in the intake air flow direction. It is formed to extend downstream.
- the surfaces 70s of the partitioning portion 70 and the surfaces 90s of the deviating portion 90 thereof are denoted by reference numerals.
- the tumble flow path 72 and the main flow path 74 are partitioned so that the main flow path 74 extends downward to the sides of the deviation portion 90 in the region where the deviation portion 90 extends in the intake flow direction. there is This downward expansion of the main flow path 74 is performed in a direction opposite to the direction in which the offset 90 is biased, here on the left LH side of the offset 90 .
- the downward expansion of the main flow path 74 and the resulting fusion of the main flow path 74 and the tumble flow path 72 are more pronounced toward the downstream side of the deviation portion 90 .
- the wall surface 24w is a part of the inner wall surface 24s of the cylinder head 24 here, is positioned just below the second direction side of the main flow passage 74, and extends in the direction of the cylinder axis C as shown in FIGS. It has a directional length and extends in the intake flow direction. Therefore, when the inner wall surface 24s is extended in the direction of the cylinder axis, the elongated inner wall surface 24s crosses the main flow path 74. As shown in FIG.
- the wall surface 24w extends to the left LH side of the downstream end portion 72d of the tumble flow path 72 to form a partition, and biases the tumble flow path 72 to the right RH side.
- the wall surface 24w serves as a deflection section DP configured to deflect the intake air from the tumble flow path 72 to one side of the virtual plane IS, that is, to the right RH side.
- the mounting portion 78s of the second fuel injection valve 78 is located on the left LH side of the intake passage 60, as is clear from FIGS.
- the second fuel injection valve 78 is provided at a position biased in the direction opposite to the direction in which the biased portion 90 is biased. Therefore, the second fuel injector 78 can inject fuel in a direction different from the direction in which the deviated portion 90 is biased, and more preferably in the opposite direction.
- the second fuel injection valve 78 is provided on the upper side, that is, on the main flow path 74 side, and injects fuel from the main flow path 74 side.
- FIGS. 13A and 13B schematically show sprayed fuel SF injected from the second fuel injection valve 78 provided at a position biased toward the left LH side.
- 10 schematically shows part of the sprayed fuel SF injected from the second fuel injection valve 78. As shown in FIG.
- the fuel SF injected from the second fuel injection valve 78 is not blocked by the partition 70, and at least part of it, here in particular at least the majority of it, more preferably its All flow first through the main flow path 74, then flow into the junction (downstream junction) 72f between the main flow path 74 and the tumble flow path 72, and then directly reach the intake valve port 34 and enter the combustion chamber 32.
- the arrangement of the second fuel injection valve 78 and the shape of the partition portion 70 including the offset portion 90 are designed to enable such fuel injection.
- divider body 92 of divider 70 partially terminates downstream thereof to allow confluence of main channel 74 and tumble channel 72, and along surface 90s of offset 90 preferably
- the partition main body portion 92 of the partition portion 70 and the offset portion 90 downstream thereof are arranged so that the fuel SF injected from the second fuel injection valve 78 reaches the intake valve port 34 without touching the offset portion 90. designed (see, for example, FIG. 10).
- the second fuel injection valve 78 which is provided to inject the fuel SF from the main flow path 74 side toward the combustion chamber 32, injects fuel in the direction opposite to the direction in which the deviated portion 90 is deviated. It is designed to Therefore, the partition 70, particularly its offset 90, can be extended further downstream in the intake air flow direction.
- the deflection portion DP which is the wall surface 24w, defines the tumble flow path 72 so that the deflection portion 90 is biased toward the downstream side in the biased direction. Therefore, the deviated portion 90 of the partition portion 70 that is extended further downstream in the direction of flow of the intake air can give stronger directivity to the intake air from the tumble flow path 72 .
- the partition portion 70 completely separates the main flow path 74 and the tumble flow path 72 with the partition body portion 92 on the upstream side, and has the offset portion 90 on the downstream side to It is designed to characterize the flow from the tumble channel 72 further downstream while realizing connection with the tumble channel 72 .
- the second fuel injection valve 78 is biased in the direction opposite to the direction in which the biased portion 90 is biased, here it is disposed on the opposite side in the width direction, and injects fuel in a direction different from that of the biased portion 90. , and fuel can be introduced substantially directly into the combustion chamber 32 via the intake valve port 34 . In other words, it is possible to ensure a good supply of fuel to the combustion chamber.
- the offset portion 90 which is the downstream portion of the partition portion 70, can be extended further downstream. Therefore, the flow from the tumble channel 72 can be given a stronger directivity. This directivity is directed between the intake valve port 34 and the head portion of the intake valve 44 when the valve is open so as to form a stronger tumble flow in the combustion chamber 32 . Therefore, the intake air from the tumble flow path 72 can more preferably form a tumble flow in the combustion chamber 32 .
- the tumble flow path 72 communicates with the main flow path 74 downstream of the downstream edge portion of the partition portion 70, that is, the downstream edge portion 90d of the deviation portion 90, and forms a single intake passage leading to the combustion chamber 32.
- the tumble channel 72 and the main channel 74 are defined. This allows the intake air from the tumble passage 72 to be introduced into the combustion chamber 32 along with the intake air from the main passage 74, and the intake air from the single intake passage, the single intake port 38, to deliver fuel to the combustion chamber 32. and the formation of tumble flow can occur.
- this configuration can suppress an increase in the number of parts, and is excellent in terms of cost.
- the wall surface 24w allows the intake air from the tumble flow path 72 to be biased to one side of the imaginary plane IS, that is, to the right RH side, and flow into the combustion chamber 32.
- the intake air from this tumble passage 72 has a strong directivity so as to form a strong tumble flow as described above, flows into the combustion chamber 32, and extends to the exhaust side of the wall surfaces defining the combustion chamber 32. It collides with the part of the ceiling surface 24t and the part of the cylinder bore 22b. Due to this collision, the wall surface can generate a lateral force component in the longitudinal direction of the tumble flow. Therefore, in addition to the vertical force component of the tumble flow, the intake air from the tumble flow path 72 can also have the horizontal force component of the swirl flow, that is, the circumferential direction of the cylinder.
- the spark plug 54 provided in the combustion chamber 32 is positioned on one side of the imaginary plane IS, that is, on the side to which the intake air from the tumble flow path 72 is biased. Therefore, it is possible to suitably ignite the fuel contained in the intake air from the tumble flow path 72, that is, the air-fuel mixture.
- FIG. 14 shows a schematic diagram of the combustion chamber 32 of the internal combustion engine 10 and its surroundings viewed from above in the cylinder axis C direction. 14 shows the contour of the circular opening edge 24e of the cylinder bore 22b or the ceiling surface 24t of the combustion chamber 32, the relative arrangement of the intake valve port 34, the exhaust valve port 36 and the spark plug 54.
- FIG. The imaginary plane IS defined to pass through the central portion 34a of the intake valve port 34 and the central portion 36a of the exhaust valve port 36 passes through the cylinder axis C and the valve stem of the intake valve 44 in FIG. Overlaps the 44s axis (valve axis).
- the intake air from the tumble flow path 72 enters the combustion chamber 32 biased to the right RH side in the width direction perpendicular to the imaginary plane IS, as indicated by arrow T in FIG.
- the downstream end portion 72d of the tumble flow path 72 has a substantially constant width, so the arrow T of the intake air from the tumble flow path 72 is shown substantially parallel to the imaginary plane IS.
- the arrow T mainly passes through the right side, which is one side of the imaginary plane IS, and advances toward the wall surface 32W on the exhaust valve port 36 side of the combustion chamber 32, and can collide with it.
- the wall surface 32W against which the flow of the arrow T collides is mainly the wall on the right RH side of the imaginary plane IS, and as shown in FIG.
- the impact force F of the flow of the arrow T on the wall surface 32W can be divided into an orthogonal component Fa orthogonal to the wall surface 32W and a tangential component Fb along the wall surface 32W.
- the orthogonal component Fa is a component that produces a vertical eddy current in the direction of the cylinder axis C, that is, a tumble flow.
- the tangential component Fb is a component that produces a swirl flow that rotates along the circumferential direction of the cylinder from the right side, which is one side of the virtual plane IS, toward the left side, which is the other side. That is, the flow of arrow T forms a flow in combustion chamber 32 so as to generate a tumble flow and a swirl flow.
- the flow from the tumble flow path 72 has a different center of vortex than when the tumble flow is simply formed in the combustion chamber 32, so that the tumble flow can be generated in the combustion chamber 32 and the virtual plane A swirl-like flow from the right RH side, which is one side of the IS, to the left LH side can also be generated.
- the wall surface 32W with which the intake air from the tumble flow path 72 collides is, for example, the ceiling surface 24t portion or the cylinder bore 22b portion extending toward the exhaust side among the wall surfaces defining and forming the combustion chamber 32 as described above.
- the ceiling surface 24t is formed into a concave curved surface. Therefore, the ceiling surface 24t can suitably generate the force of the tangential component Fb by the intake air from the tumble flow path 72.
- the ceiling surface 24t is formed in a substantially hemispherical shape and is a smooth concave curved surface, so that such a force is generated in the intake air from the tumble flow passage 72, and a swirl-like flow is more preferably generated. can contribute to the development of
- the arrow T1 in FIG. 14 indicates the flow when the intake air flows into the combustion chamber 32 while being directed more to the right.
- the wall surface 24w may be designed in consideration of the degree of force of the tangential component that is generated, such as the bias of the tumble flow path 72, the inclination of the tumble flow path 72 with respect to the combustion chamber 32, and the like.
- the spark plug 54 is positioned on the side of the imaginary plane IS where the intake air from the tumble flow path 72 is biased. Therefore, since the intake air from the tumble flow path 72 contains fuel and substantially forms an air-fuel mixture, the air-fuel mixture introduced into the combustion chamber 32 is preferably ignited by the ignition plug 54 . Then, since the flow from the right RH side, which is one side of the virtual plane IS, to the left LH side is formed as described above, flame propagation in the combustion chamber 32 can be favorably caused.
- the resonator 77 is connected to the intake passage 60, particularly to the intake passage 60d on the downstream side of the throttle valve 62c, as described above.
- the resonator 77 is provided so as to communicate with the intake passage 60d obliquely rather than perpendicularly to the direction of intake air flow. It is
- the communication pipe 77a is connected to the cylinder head 24 so as to be obliquely inserted from the upper side to the lower side. Therefore, the axis 77d (FIGS.
- a communication passage 77b that connects the resonator 77 to the intake passage 60 is provided at a position biased toward the left LH side, like the second fuel injection valve 78.
- the communication path 77b directly communicates with the main flow path 74 and the downstream junction 72f.
- the communicating portion of the communication passage 77b with the intake passage 60 is positioned in the vicinity of the mounting portion 78s of the second fuel injection valve 78, immediately downstream of the mounting portion 78s.
- the axial line 77d of the downstream outlet portion 77c of the communication passage 77b connecting the resonator 77 to the intake passage 66 is made substantially parallel to the fuel injection direction of the second fuel injection valve 78. As shown in FIG.
- the communication passage 77b of the resonator 77 is It is provided with respect to the intake passage 60 so that the intake air from the resonator 77 can be directed directly to the combustion chamber 32 .
- the directivity of the intake air from this resonator 77 is directed between the intake valve port 34 and the head portion of the intake valve 44 when the valve is open so as to form a stronger swirl flow in the combustion chamber 32. .
- FIG. 15 shows the three-dimensional model of FIG. 5, schematically shows the intake valve 44, and schematically shows the flow direction of the intake air from the resonator 77, that is, the axis 77d.
- FIG. 16 schematically shows a view of the intake valve port 34 side from the upstream side in the intake air flow direction. , and the direction of flow of intake air from the resonator 77, that is, the axis 77d.
- the communication path 77b is arranged so that the intake air from the resonator 77 directly passes between the head portion of the intake valve 44 and the intake valve port 34 when the valve is open, and is directed toward the combustion chamber 32.
- the axis 77d extends to the combustion chamber 32 by directly passing between the head portion 44a of the intake valve 44 and the intake valve port 34 when the valve is open.
- the direction of the axis 77d of the communication passage 77b is the direction of the axis 77d of the communication passage 77b, as shown in FIG. It is defined to cross the valve stem 44s of the intake valve 44 upstream of the valve stem 44s.
- the axis 77d of the communication passage 77b is not limited to intersecting the valve stem 44s upstream of the valve stem 44s of the intake valve 44. It can also be defined to intersect the valve stem 44s downstream of the valve stem 44s.
- the axis 77d of the communication passage 77b is the back of the head portion 44a of the intake valve 44 (toward the combustion chamber) when the intake valve 44 is open in the intake stroke.
- the imaginary cylindrical body IC (FIG. 15) that can be defined between the intake valve port 34 and the side facing the air outlet 77b, it passes through the imaginary wall surface on the side opposite to the outlet portion 77c of the communicating passage 77b.
- the axis 77d of the communicating passage 77b extends substantially parallel to the surface of the head portion 44a.
- the resonator 77 Since the resonator 77 is connected to the intake passage 60d via the communication passage 77b as described above, when the air from the resonator 77 flows toward the combustion chamber 32, the air is biased to the right side of the intake valve port 34. It can flow into the combustion chamber 32 . Since the axis 77d of the downstream outlet 77c of the communication passage 77b obliquely intersects the intake air flow direction at the connection point to the intake passages 60 and 60d, as described above, the intake air from the resonator 77 is biased. greater than the intake bias from the tumble flow path 72. 14, the intake air from the tumble flow path 72 flows into the combustion chamber 32 biasedly as indicated by arrow T in FIG. It can flow into the combustion chamber 32 even more. Therefore, the intake air from the resonator 77 can generate a swirl flow or a vortex flow close to it.
- FIG. 17 in these intake devices, a tumble control valve 75 is attached to the upper passage portion of the intake passage, the upper side being the main passage 74 and the lower side being the tumble passage 72 .
- a and B indicate the positions of various locations representing changes in pressure within the intake system shown in FIG. Point A is located downstream of the throttle valve 62c and upstream of the upstream end 70u of the partition section 70 separating the tumble flow path 72 and the main flow path 74, and point B is the tumble flow. Located on Road 72.
- FIG. 18 shows crank angles in one cycle when the throttle valve 62c is slowly opened for an intake system in which the resonator 77 is connected downstream of the throttle valve 62c and an intake system in which the resonator 77 is not connected downstream of the throttle valve 62c.
- the pressure data at each location are shown with the crank angle on the horizontal axis and the pressure on the vertical axis.
- An intake passage area in the intake device from the downstream of the throttle valve 62c to the intake valve 44 is defined as a throttle valve downstream intake area, and this volume is defined as a throttle valve downstream intake volume.
- These definitions also include areas and volumes within resonator 77 when resonator 77 is connected.
- the intake volume downstream of the throttle valve is not large. , air is taken in from the atmosphere upstream of the throttle valve 62c through the opening of the throttle valve 62c.
- the opening of the throttle valve 62c is small, the volume of air that increases as the piston 28 descends cannot be charged in time, and the internal pressure of the intake port rapidly becomes negative (at crank angle 380 in FIG. 18). between about 540 degrees).
- the pressure in the intake port suddenly becomes negative in this way, as the piston 28 descends, the air in the intake area downstream of the throttle valve expands and is drawn in, weakening the flow and forming a tumble flow in the cylinder.
- the eddy current becomes weaker.
- FIG. 19 is an operation map of the throttle valve 62c and the tumble control valve 75.
- the horizontal axis represents the engine rotation speed Ne, and the vertical axis represents the output of the internal combustion engine 10.
- the opening range of the control valve 75 is shown. Both the areas ⁇ 1 and ⁇ 2 are areas in which the tumble control valve 75 is closed as indicated by broken lines in FIG. 1, and the area ⁇ is an area in which the tumble control valve 75 is opened as indicated by solid lines in FIG.
- the region ⁇ 1 is a region in which the throttle valve 62c is gradually opened and corresponds to a low load region, and the region ⁇ 2 is a region in which the throttle valve 62c is opened to a predetermined opening degree larger than the opening degree in the region ⁇ 1, Corresponds to the medium load range.
- the tumble control valve 75 is either fully open or fully closed. However, the tumble control valve 75 may be controlled to take an opening degree between fully open and fully closed.
- the mapped data of FIG. 19 is stored in the storage section of the ECU
- the horizontal axis represents the opening of the throttle valve 62c, that is, the throttle opening TH
- the vertical axis represents the intake air flow rate into the combustion chamber 32. and the inspiratory flow rate.
- the thin line indicates the intake air flow rate from the resonator 77 and the thick line indicates the intake air flow rate from the tumble flow path 72 .
- 20A indicates the sum of the intake flow rate from the tumble flow path 72 and the intake flow rate from the resonator 77.
- the graph of FIG. 20B shows the strength correlation between the vortex flow such as the tumble flow caused by the intake air from the tumble flow path 72 and the vortex flow such as the swirl flow caused by the intake air from the resonator 77
- the horizontal axis is the graph of FIG. 20A.
- the vertical axis indicates the strength of the vortex.
- 20A and 20B is the throttle opening degree when the tumble control valve 75 is closed. This is the opening degree at the boundary of the area (corresponding to area ⁇ 2 in FIG. 19).
- the throttle valve 62c When the tumble control valve 75 is in the closed state and the throttle opening TH is relatively small such as gradually opening, that is, when the operating state of the internal combustion engine is in the low load region, that is, the region ⁇ 1, the throttle valve 62c is closed as described above.
- the amount of intake air in the tumble flow path 72 which is the intake flow path portion on the downstream side of the air intake, is small.
- the intake stroke in addition to the intake air flowing through the tumble flow path 72, the intake air inside the resonator 77 is also drawn into the combustion chamber 32 as described above.
- the intake air flowing through the tumble flow passage 72 is in addition, the intake air inside the resonator 77 is also positively drawn into the combustion chamber 32 .
- the intake air from the resonator 77 is directed as described above and is strongly directed to the right side of the combustion chamber 32 and taken in.
- a strong swirl flow or tumble flow with a strong swirl component is generated in the combustion chamber 32 (“swirl” line in FIG. 20B). Therefore, the combustion of the air-fuel mixture in the combustion chamber can be promoted.
- the resonator 77 provided as described above can improve intake of air when the throttle opening is relatively small.
- the tumble control valve 75 when the tumble control valve 75 is in the closed state and the throttle opening TH gradually increases, for example, when the operating state of the internal combustion engine is in the middle load region, that is, the region ⁇ 2, the tumble flow downstream from the throttle valve 62c
- the intake air flowing into the passage 72 can cover the intake air in the intake stroke, and the degree to which the intake air in the resonator 77 is drawn into the combustion chamber 32 is reduced.
- the intake air flowing into the tumble flow path 72 is mainly It is drawn into combustion chamber 32 .
- This allows a tumble flow to be generated in the combustion chamber 32 by the intake air through the tumble passage 72 ("tumble" line in FIG. 20B). Therefore, even when the tumble control valve 75 is in the closed state and the throttle opening TH is relatively large, the intake air can be preferably drawn.
- the resonator 77 is provided so as to communicate with the intake passage on the downstream side of the intermediate portion 70m of the partition portion 70 in the intake flow direction. Therefore, when the throttle valve 62c is throttled, that is, when the throttle valve 62c is relatively small, such as when the internal combustion engine is operating in a low-load region, the intake air from the resonator flows into the intake passage on the downstream side of the partition 70. can be done. Therefore, the inflow of intake air from the intake passage to the combustion chamber 32 can be improved.
- the axis 70d of the downstream outlet 70c of the communicating passage 70b connecting the resonator 77 to the intake passage 60 is designed to face the combustion chamber 32 as described above. Therefore, the air flowing from the resonator can be easily guided to the combustion chamber 32, so that a vortex such as a swirl flow can be more positively generated in the combustion chamber 32.
- the resonator 77 is directly connected to the cylinder head 24 defining the ceiling surface 24t of the combustion chamber 32 via a communication passage 77b. Therefore, the air flowing in from the resonator 77 can be guided more directly into the combustion chamber 32 .
- the tumble control valve 75 is closed. , the swirl flow and/or tumble flow can promote better mixing of the fuel and promote its combustion.
- spark plug 54 is positioned in the direction of this fuel injection. Therefore, the combustion of fuel in the combustion chamber 32 can be caused more favorably.
- the downstream side of the intermediate portion 70m of the partition portion 70 in the intake air flow direction is communicated with the intake passage 60, particularly with the downstream portion of the main flow passage 74.
- a resonator 77 was provided. This makes it possible to effectively introduce the intake air from the resonator 77 into the combustion chamber 32 when the throttle valve 62c is throttled during operation of the internal combustion engine 10 in the low load region ⁇ 1.
- the axis 77d of the downstream outlet 77c of the communicating passage 77b connecting the intake air of the resonator 77 to the intake passage 60 is designed to face the combustion chamber 32 side.
- the intake air from the resonator 77 is more directly directed to the combustion chamber 32, and a swirl flow or a tumble flow having a swirl component is actively generated in the combustion chamber 32.
- the communication passage 77b preferably communicates with the downstream side of the main flow passage 74 rather than the downstream portion thereof. It is preferable that the tumble channel 72 and the main channel 74 communicate with the downstream junction 72f.
- a notch portion 77e may be further provided at the downstream outlet portion 77c of the communicating passage 77b that connects the resonator 77 to the intake passage 60.
- the internal combustion engine 10 was a two-valve internal combustion engine having only one intake valve and one exhaust valve per cylinder. However, the internal combustion engine to which the present invention is applied has three or more valves per cylinder. may have Moreover, although the internal combustion engine 10 is provided with the tumble control valve 75, the present invention can also be applied to an internal combustion engine in which the tumble control valve 75 is not provided.
Abstract
Description
スロットル弁の下流側の吸気通路を複数の流路に分割するように吸気流れ方向に延在する仕切部と、
前記吸気流れ方向において前記仕切部の中間部よりも下流側において前記吸気通路に連通するように設けられたレゾネータと
を備えた
ことを特徴とする内燃機関の吸気装置
を提供する。
24w…壁部、32…燃焼室、34…吸気弁口、36…排気弁口、38…吸気ポート
40…排気ポート、44…吸気弁、46…排気弁、54…点火プラグ、60…吸気通路
62…スロットルボディ、62c…スロットル弁、70…仕切部
72…タンブル流路(第1吸気流路)、74…主流路(第2吸気流路)
75…タンブル制御弁、76…第1燃料噴射弁、77…レゾネータ、77b…連通路
78…第2燃料噴射弁、90…偏位部、92…仕切本体部
DP…偏向部、M…立体モデル、S…吸気装置
Claims (10)
- スロットル弁(62c)の下流側の吸気通路(60d)を複数の流路に分割するように吸気流れ方向に延在する仕切部(70)と、
前記吸気流れ方向において前記仕切部(70)の中間部(70m)よりも下流側において前記吸気通路(60d)に連通するように設けられたレゾネータ(77)と
を備えた
ことを特徴とする内燃機関の吸気装置(S)。 - 前記レゾネータ(77)を前記吸気通路(60d)につなぐ連通路(70b)における下流側出口部(77c)の軸線(77d)は前記燃焼室(32)側を向くように設計されている
ことを特徴とする請求項1に記載の内燃機関の吸気装置(S)。 - 前記レゾネータ(77)は、前記燃焼室(32)の天井面(24t)を区画形成する前記内燃機関のシリンダヘッド(24)に連通路(77b)を介して直接的に繋げられている
ことを特徴とする請求項1又は請求項2に記載の内燃機関の吸気装置(S)。 - 前記内燃機関のシリンダ軸線(C)の方向においてクランク軸(12)側からシリンダヘッド(24)側の方向を第1方向と定義するとき、
前記仕切部(70)は、前記吸気通路(60d)を、前記第1方向において順に並ぶ第1吸気流路(72)と前記第2吸気流路(74)とに分けるように設けられている
ことを特徴とする請求項1から請求項3のいずれか一項に記載の内燃機関の吸気装置(S)。 - 前記レゾネータ(77)を前記吸気通路(60d)につなぐ連通路(77b)は、前記第2吸気流路(74)の下流側部分(74d)又は前記第1吸気流路(72)と前記第2吸気流路(74)との下流側合流部(72f)に連通する
ことを特徴とする請求項4に記載の内燃機関の吸気装置(S)。 - 前記燃焼室(32)に臨むとともに吸気弁(44)によって開閉される吸気弁口(34)の中心部と、前記燃焼室(32)に臨むとともに排気弁(46)によって開閉される排気弁口(36)の中心部とを通過するとともに前記シリンダ軸線(C)に平行に延びる仮想面(IS)を定めるとき、
前記第1吸気流路(72)から前記燃焼室(32)への吸気を前記仮想面(IS)の一方側に偏らせるように構成された偏向部(DP)が更に設けられている
ことを特徴する請求項4又は5に記載の内燃機関の吸気装置(S)。 - 前記第2吸気流路(74)の流路断面積は前記第1吸気流路(72)の流路断面積よりも大きく、燃料噴射弁(78)は、前記第2吸気流路(74)側に設けられている
ことを特徴する請求項4から請求項6のいずれか一項に記載の内燃機関の吸気装置(S)。 - 前記燃料噴射弁(78)の燃料噴射方向は、前記レゾネータ(77)を前記吸気通路(60d)につなぐ連通路(77b)における下流側出口部(77c)の軸線(77d)と略平行である
ことを特徴とする請求項7に記載の内燃機関の吸気装置(S)。 - 前記第2吸気流路(74)を開閉するタンブル制御弁(75)が前記仕切部(70)の上流端(70u)又は該上流端(70u)よりも上流側に更に設けられている
ことを特徴とする請求項4から請求項8に記載の内燃機関の吸気装置(S)。 - 前記レゾネータ(77)を前記吸気通路(60d)につなぐ連通路(77b)における下流側出口部(77c)に切欠部(77e)が更に設けられている
請求項1から請求項9のいずれか一項に記載の内燃機関の吸気装置(S)。
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2023550912A JPWO2023053346A1 (ja) | 2021-09-30 | 2021-09-30 | |
PCT/JP2021/036152 WO2023053346A1 (ja) | 2021-09-30 | 2021-09-30 | 内燃機関の吸気装置 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2021/036152 WO2023053346A1 (ja) | 2021-09-30 | 2021-09-30 | 内燃機関の吸気装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2023053346A1 true WO2023053346A1 (ja) | 2023-04-06 |
Family
ID=85781610
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2021/036152 WO2023053346A1 (ja) | 2021-09-30 | 2021-09-30 | 内燃機関の吸気装置 |
Country Status (2)
Country | Link |
---|---|
JP (1) | JPWO2023053346A1 (ja) |
WO (1) | WO2023053346A1 (ja) |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5627025A (en) * | 1979-08-10 | 1981-03-16 | Honda Motor Co Ltd | Suction device in internal-combustion engine |
EP0439848A1 (en) * | 1990-02-01 | 1991-08-07 | Volvo Car B.V. | Short circuit primary turbulence system for a combustion engine |
JPH08338253A (ja) * | 1995-06-14 | 1996-12-24 | Suzuki Motor Corp | エンジンの吸気装置 |
JPH11166417A (ja) * | 1997-09-30 | 1999-06-22 | Yamaha Motor Co Ltd | エンジンの吸気装置 |
JPH11218029A (ja) * | 1998-02-02 | 1999-08-10 | Yamaha Motor Co Ltd | エンジンの吸気装置 |
JP2003262165A (ja) * | 2002-03-07 | 2003-09-19 | Hitachi Ltd | 多気筒用内燃機関の吸気管 |
JP2017089527A (ja) * | 2015-11-12 | 2017-05-25 | アイシン精機株式会社 | インテークマニホールド |
WO2019009347A1 (ja) * | 2017-07-05 | 2019-01-10 | 本田技研工業株式会社 | シリンダヘッド |
JP6714764B2 (ja) * | 2017-03-10 | 2020-06-24 | 本田技研工業株式会社 | 内燃機関の吸気構造 |
-
2021
- 2021-09-30 WO PCT/JP2021/036152 patent/WO2023053346A1/ja active Application Filing
- 2021-09-30 JP JP2023550912A patent/JPWO2023053346A1/ja active Pending
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5627025A (en) * | 1979-08-10 | 1981-03-16 | Honda Motor Co Ltd | Suction device in internal-combustion engine |
EP0439848A1 (en) * | 1990-02-01 | 1991-08-07 | Volvo Car B.V. | Short circuit primary turbulence system for a combustion engine |
JPH08338253A (ja) * | 1995-06-14 | 1996-12-24 | Suzuki Motor Corp | エンジンの吸気装置 |
JPH11166417A (ja) * | 1997-09-30 | 1999-06-22 | Yamaha Motor Co Ltd | エンジンの吸気装置 |
JPH11218029A (ja) * | 1998-02-02 | 1999-08-10 | Yamaha Motor Co Ltd | エンジンの吸気装置 |
JP2003262165A (ja) * | 2002-03-07 | 2003-09-19 | Hitachi Ltd | 多気筒用内燃機関の吸気管 |
JP2017089527A (ja) * | 2015-11-12 | 2017-05-25 | アイシン精機株式会社 | インテークマニホールド |
JP6714764B2 (ja) * | 2017-03-10 | 2020-06-24 | 本田技研工業株式会社 | 内燃機関の吸気構造 |
WO2019009347A1 (ja) * | 2017-07-05 | 2019-01-10 | 本田技研工業株式会社 | シリンダヘッド |
Also Published As
Publication number | Publication date |
---|---|
JPWO2023053346A1 (ja) | 2023-04-06 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP4728195B2 (ja) | エンジンの吸気制御装置 | |
US7802555B2 (en) | Intake control device for an engine | |
JP5925878B2 (ja) | 内燃機関の吸気装置 | |
JPH076394B2 (ja) | シリンダ吸気ポ−ト付き内燃機関 | |
EP2101055B1 (en) | Engine with intake control device | |
US20100037853A1 (en) | Intake system for an internal combustion engine | |
JP4044195B2 (ja) | エンジンの吸気装置 | |
WO2023053346A1 (ja) | 内燃機関の吸気装置 | |
EP3650671B1 (en) | Internal combustion engine intake structure | |
US7137380B1 (en) | Internal combustion engine with ignition plug and vehicle provided with the same | |
WO2022176862A1 (ja) | 内燃機関の吸気構造 | |
JPH0745817B2 (ja) | 直噴式多気筒ディーゼル機関 | |
WO2023188249A1 (ja) | 内燃機関の吸気構造 | |
JP7411142B2 (ja) | 内燃機関 | |
JP3971010B2 (ja) | エンジンの吸気装置 | |
US20100037840A1 (en) | Internal combustion engine | |
WO2022176860A1 (ja) | 内燃機関の吸気構造 | |
JP4044196B2 (ja) | エンジンの吸気装置 | |
KR20010041124A (ko) | 내연기관 | |
WO2022210120A1 (ja) | 内燃機関の吸気構造 | |
JPH09317476A (ja) | 筒内燃料噴射式エンジン | |
JP3030413B2 (ja) | 筒内噴射型内燃機関 | |
WO2023188310A1 (ja) | 内燃機関の吸気構造 | |
WO2024070901A1 (ja) | 内燃機関の吸気構造 | |
JP6958430B2 (ja) | 内燃機関 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 21959386 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2023550912 Country of ref document: JP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 112024000055804 Country of ref document: IT |
|
REG | Reference to national code |
Ref country code: BR Ref legal event code: B01A Ref document number: 112024005141 Country of ref document: BR |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2401001958 Country of ref document: TH |