WO2020196207A1 - Moteur à combustion interne de type à pré-chambre - Google Patents

Moteur à combustion interne de type à pré-chambre Download PDF

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Publication number
WO2020196207A1
WO2020196207A1 PCT/JP2020/012157 JP2020012157W WO2020196207A1 WO 2020196207 A1 WO2020196207 A1 WO 2020196207A1 JP 2020012157 W JP2020012157 W JP 2020012157W WO 2020196207 A1 WO2020196207 A1 WO 2020196207A1
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WO
WIPO (PCT)
Prior art keywords
chamber
sub
main chamber
injection port
internal combustion
Prior art date
Application number
PCT/JP2020/012157
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English (en)
Japanese (ja)
Inventor
欣也 井上
田中　大
貴之 城田
一成 野中
遼太 朝倉
佳博 菅田
捷 飯塚
晃弘 津田
Original Assignee
三菱自動車工業株式会社
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Priority to JP2021509280A priority Critical patent/JP7226527B2/ja
Publication of WO2020196207A1 publication Critical patent/WO2020196207A1/fr

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    • 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
    • F02B19/00—Engines characterised by precombustion chambers
    • F02B19/08—Engines characterised by precombustion chambers the chamber being of air-swirl type
    • 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
    • F02B19/00—Engines characterised by precombustion chambers
    • F02B19/16—Chamber shapes or constructions not specific to sub-groups F02B19/02 - F02B19/10
    • F02B19/18—Transfer passages between chamber and cylinder
    • 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
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
    • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • This disclosure relates to a sub-chamber internal combustion engine.
  • a sub-chamber type internal combustion engine having a main chamber (main combustion chamber) and a sub-chamber (sub-combustion chamber) provided adjacent to the main chamber has been proposed (for example, Japanese Patent No. 4561522). reference).
  • an air-fuel mixture is formed from the fuel injected into the main chamber.
  • the formed air-fuel mixture is supplied to the sub-chamber via the communication passage, and is ignited by the spark plug in the sub-chamber.
  • a flame is formed.
  • the flame formed in the sub-chamber is jetted into the main chamber through the continuous passage and ignites the air-fuel mixture in the main chamber.
  • the combustion speed of the main chamber is increased. This enables operation with a leaner air-fuel ratio and improves fuel efficiency.
  • the central axis of the first injection port does not collide with the piston crown surface when the piston is located near the compression top dead center, and the cylinder. Orient the inner wall surface. Further, the central axis of the second injection port points to the outer peripheral portion of the bottom surface of the cavity on the crown surface of the piston when the piston is located near the compression top dead center.
  • the injection port faces the inner wall surface of the cylinder. Therefore, the flame collides with the inner wall surface of the cylinder, and the heat of the flame is taken to the inner wall surface of the cylinder. As a result, cooling loss may occur and the combustion rate of the main chamber may slow down.
  • the embodiment of the present disclosure relates to a sub-chamber type internal combustion engine in which the flame injected from the sub-chamber toward the main chamber is suppressed from colliding with the cylinder and the occurrence of cooling loss is reduced.
  • the sub-chamber internal combustion engine includes a main chamber, a sub-chamber, and a continuous passage.
  • the main chamber is defined by a cylinder head, a cylinder, and a piston.
  • the sub chamber protrudes from the cylinder head toward the main chamber and is provided separately from the main chamber.
  • pre-combustion before combustion in the main chamber occurs.
  • the communication passage has an injection port that connects the main chamber and the sub chamber and injects a flame of pre-combustion into the main chamber.
  • the injection port is configured to guide the flame in the direction of rotation of the swirling flow generated in the main chamber.
  • a swirling flow called a swirl or the like is generated by the intake air introduced into the combustion chamber.
  • various techniques for promoting the generation of a swirling flow in order to improve the combustion efficiency are widely known.
  • the injection port is configured to guide the flame in the rotation direction of this swirling flow. As a result, the flame injected into the main chamber from the injection port of the continuous passage is flowed along the rotation direction of the swirling flow. Therefore, it is suppressed that the flame collides with the cylinder, and the occurrence of cooling loss is reduced.
  • the injection port may extend in the direction of rotation of the swirling flow toward the main chamber.
  • the flame injected from the injection port into the main chamber can be guided in the direction of rotation of the swirling flow.
  • the inner diameter of the injection port may increase as it approaches the main chamber.
  • the inner wall surface of the communication passage forming the injection port which is located inside the sub chamber, is more than the inner wall surface located outside the sub chamber. May extend in the direction in which the inner diameter of the
  • the flame injected from the injection port is easily swept by the swirling flow.
  • the penetration of the flame is weakened and the combustion of the main chamber is promoted.
  • the flame rides on the swirling flow and flows toward the adjacent passages. This promotes combustion in the main chamber between the adjacent passageway and the flame injected.
  • the inner wall surface of the communication passage forming the injection port may be formed along the tangent line of the inner circumference of the sub chamber.
  • the air-fuel mixture introduced into the sub-chamber from the connecting passage is guided to the inner circumference of the sub-chamber.
  • the air-fuel mixture tends to form a vortex in the sub-chamber. Therefore, unevenness of the air-fuel mixture in the sub-chamber and variation in the flow of the air-fuel mixture are prevented.
  • the air-fuel mixture in the sub-chamber is easily ignited.
  • the inner diameter of the sub chamber may be increased from the main chamber toward the cylinder head.
  • the flow velocity of the air-fuel mixture introduced into the sub-chamber from the communication passage weakens toward the cylinder head. That is, the flow velocity of the vortex of the air-fuel mixture weakens. This prevents misfires due to the air-fuel mixture flowing too fast.
  • the vertical sectional view which shows the schematic structure of the auxiliary chamber type internal combustion engine by one Embodiment of this disclosure.
  • the cross-sectional view which shows the formation part of the communication passage of the auxiliary chamber type internal combustion engine of FIG.
  • the vertical sectional view which shows the formation part of the communication passage of the auxiliary chamber type internal combustion engine of FIG.
  • the vertical sectional view which shows the schematic structure of the auxiliary chamber by another embodiment of this disclosure.
  • the cylinder axial direction Q indicates the sliding direction of the piston along the cylinder.
  • the cylinder axial direction Q is indicated, and the cylinder head side is "up” and the piston side is "down".
  • the left-right direction L indicates a direction orthogonal to the cylinder axial direction Q and where the intake port and the exhaust port are arranged.
  • the crankshaft direction P indicates a direction in which the cylinders are arranged, orthogonal to the cylinder shaft direction Q.
  • the sub-chamber internal combustion engine 1 has a main chamber 4, a sub-chamber 6, a plurality of communication passages 8 communicating the main chamber 4 and the sub-chamber 6, and ignition provided in the sub-chamber 6. It includes a plug 10, a fuel injection valve 12 provided in the main chamber 4, and a swirling flow generating unit 14.
  • the sub-chamber internal combustion engine 1 is an in-line internal combustion engine in which a plurality of cylinders N including a main chamber 4 and a sub chamber 6 are arranged in series. That is, the main chamber 4, the sub chamber 6, the plurality of communication passages 8, the spark plug 10, the fuel injection valve 12, and the swirling flow generating portion 14 are provided in each cylinder N.
  • the arrangement of the cylinders N is not limited to this, and may be a V type or a horizontally opposed type.
  • the main chamber 4 is a space defined by the cylinder 101a of the cylinder block 101, the cylinder head 102, and the piston 103.
  • the main chamber 4 has a pent roof shape and has two slopes toward the intake port 105 side and the exhaust port 110 side of the cylinder head 102.
  • the main chamber 4 is connected to the intake port 105 via two intake valves 104a and an intake valve 104b driven by an intake cam (not shown).
  • the intake port 105 is connected to an intake passage, a throttle valve, and an air cleaner (not shown).
  • the main chamber 4 has an exhaust port 110, an exhaust passage (not shown), and an exhaust purification catalyst (not shown) via two exhaust valves 109a and 109b driven by an exhaust cam (not shown). (Not shown) is connected.
  • the sub-chamber internal combustion engine 1 outputs power by a crankshaft (not shown) provided in the arrangement direction of the cylinders N.
  • the piston 103 drives the crankshaft via a connecting rod (not shown).
  • the sub chamber 6 is provided at the top of the pent roof shape and is adjacent to the main chamber 4.
  • the sub-chamber 6 is a space defined by the sub-chamber wall 61.
  • the sub chamber 6 projects from the cylinder head 102 toward the main chamber 4 and is separated from the main chamber 4 via the sub chamber wall 61.
  • the sub chamber 6 is provided substantially at the center of the line of intersection (ridge line) of the two slopes of the main chamber 4 having a pent roof shape.
  • the sub chamber 6 may be provided offset from the substantially center of the main chamber 4.
  • the sub chamber 6 has the same center X1 as the main chamber 4.
  • the volume of the sub chamber 6 is smaller than that of the main chamber 4, and the flame of the air-fuel mixture ignited by the spark plug 10 quickly propagates into the sub chamber 6.
  • FIG. 2 is a view of the cross section of the sub chamber 6 in the forming portion of the communication passage 8 as viewed from the piston 103 side.
  • the auxiliary chamber wall 61 has a circular cross section centered on the center X1, and the bottom portion 61a is formed in a hemispherical shape.
  • FIG. 3 is a vertical cross-sectional view of the sub chamber 6 perpendicular to the left-right direction L.
  • the diameter Dr of the inner circumference 61c of the sub chamber wall 61 increases from the main chamber 4 toward the cylinder head 102. That is, the diameter Dr of the inner circumference 61c of the auxiliary chamber wall 61 increases from the lower side to the upper side in the vertical direction (same as the cylinder axial direction Q).
  • a plurality of communication passages 8 are provided at the bottom 61a of the sub chamber wall 61.
  • the communication passage 8 communicates the main chamber 4 and the sub chamber 6 and guides the air-fuel mixture of the main chamber 4 to the sub chamber 6.
  • the air-fuel mixture introduced into the sub chamber 6 ignites in the sub chamber 6 and precombusts.
  • the communication passage 8 has an injection port 8a for injecting a flame precombusted in the sub chamber 6 on the surface of the outer circumference 61b of the sub chamber wall 61.
  • the injection port 8a is formed along the surface of the outer circumference 61b of the sub chamber wall 61.
  • the communication passage 8 has an introduction port 8b for introducing the air-fuel mixture into the sub-chamber 6 on the surface of the inner circumference 61c of the sub-chamber wall 61.
  • the introduction port 8b is formed along the surface of the inner circumference 61c of the auxiliary chamber wall 61.
  • four communication passages 8 are provided.
  • the injection port 8a of the communication passage 8 is configured to guide the flame injected from the injection port 8a in the rotation direction F of the swirling flow SW generated in the main chamber 4 along the outer circumference 61b of the sub chamber wall 61.
  • the injection port 8a extends in the rotation direction F toward the main chamber 4.
  • the flame injected from the injection port 8a is injected along the center line C1 of the injection port 8a.
  • the swirling flow SW flows along the tangent line S1 at the intersection O1 between the center line C1 and the outer circumference 61b.
  • the fact that the injection port 8a extends in the rotation direction F of the swirling flow SW means that the center line C1 (including the extension line of the center line C1) is inclined in the rotation direction F with respect to the perpendicular line R1 at the intersection point O1. That is, the angle formed by the tangent line S1 and the center line C1 is an acute angle A. It is sufficient that at least the injection port 8a extends in the rotation direction F, and the communication passage 8 may extend in the radial direction of the sub chamber 6, for example, except for the injection port 8a.
  • the communication passage 8 is an inner wall surface forming the injection port 8a, and is an inner wall surface 8c located outside the sub chamber 6 (inner wall surface on the side far from the center X1 in the crankshaft direction P or the left-right direction L). And an inner wall surface 8d (an inner wall surface on the side closer to the center X1 in the crankshaft direction P or the left-right direction L) located inside the sub chamber 6.
  • the inner wall surface 8c and the inner wall surface 8d of the communication passage 8 face each other in the rotation direction F of the swirling flow SW, and the inner wall surface 8c located outside the sub-chamber 6 in the communication passage 8 is in the rotation direction F.
  • the inner wall surface 8d located on the upstream side and inside the sub chamber 6 is located on the downstream side in the rotation direction F.
  • the inner wall surface 8c located outside the sub chamber 6 is formed along the tangent line S2 of the inner circumference 61c of the sub chamber wall 61.
  • the inner wall surface 8c is formed from the introduction port 8b to the injection port 8a along the tangent line S2.
  • the communication passage 8 may be formed so as to be inclined in the vertical direction from the main chamber 4 as shown in FIG. 3 and obliquely in the radial direction of the sub chamber 6 as shown in FIG. .. As a result, the lateral vortex rises in the sub-chamber 6.
  • the inner diameter of the injection port 8a of the communication passage 8 increases as it approaches the main chamber 4. More specifically, the inner diameter Da at the injection port 8a of this space is larger than the inner diameter Db at the introduction port 8b of the space formed by the outer inner wall surface 8c and the inner inner wall surface 8d of the communication passage 8. The inner diameter gradually increases from the introduction port 8b to the injection port 8a. Therefore, the area along the outer circumference 61b of the injection port 8a is larger than the area along the inner circumference 61c of the introduction port 8b. As a result, it is possible to prevent the amount of flame injected through the communication passage 8 from being reduced. Further, the inner diameter of the injection port 8a expands in the rotation direction F of the swirling flow SW.
  • the inner wall surface 8d extends (inclines) in the rotation direction F (direction in which the inner diameter of the injection port 8a expands) of the swirling flow SW from the inner wall surface 8c.
  • the flame injected from the injection port 8a points in the direction along the rotation direction F of the swirling flow SW.
  • the flame injected from the injection port 8a is more likely to flow into the swirling flow SW.
  • At least the inner diameter of the injection port 8a may be expanded in the rotation direction F, and the inner diameter of the communication passage 8 excluding the injection port 8a may be constant, for example.
  • the inner wall surface 8d may extend in the rotation direction F from the inner wall surface 8c, and the inner wall surface 8d may be parallel to, for example, the inner wall surface 8c in the communication passage 8 excluding the injection port 8a.
  • the center electrode 10a of the spark plug 10 is arranged at a position overlapping the center X1 of the sub chamber 6.
  • the center line C1 of the communication passage 8 intersects the wall surface of the inner circumference 61c of the sub chamber wall 61 of the sub chamber 6 at the position H. Then, the tip portion 10c of the center electrode 10a of the spark plug 10 is arranged at a position higher than the position H.
  • the fuel injection valve 12 is provided toward the main chamber 4. Further, the fuel injection valve 12 is provided outside the sub chamber 6. In the present embodiment, the fuel injection valve 12 injects fuel directly into the main chamber 4. That is, the sub-chamber internal combustion engine 1 is a direct injection type internal combustion engine. The injection amount and injection timing of the fuel injection valve 12 are controlled. Further, the fuel injection valve 12 is connected to a fuel injection pump (not shown) and a fuel tank. The fuel injection valve 12 is arranged on the intake valve 104 side of the cylinder head 102. In the present embodiment, the air-fuel ratio of the sub-chamber internal combustion engine 1 is set to a value leaner than the stoichiometric air-fuel ratio. That is, the sub-chamber internal combustion engine 1 is operated by lean burn. This improves fuel efficiency.
  • the swirling flow generating unit 14 generates a swirling flow SW that swirls in the rotation direction F in the main chamber 4.
  • the swirling flow generating unit 14 generates the swirling flow SW by changing the lift heights of the intake valve 104a and the intake valve 104b.
  • the swirling flow generating unit 14 may generate the swirling flow SW depending on the shape of the intake port 105.
  • the swirl flow SW is a swirl flow that swirls clockwise when viewed from the piston 103 side with respect to a surface perpendicular to the sliding direction (cylinder axial direction Q) of the piston 103.
  • the swirling flow SW swirls along the inner wall surface of the cylinder 101a and swivels along the outer peripheral 61b of the sub chamber wall 61.
  • the intake valve 104a and the intake valve 104b are opened, the piston 103 is lowered, and the intake air is introduced into the main chamber 4 and the sub-chamber 6. ..
  • a swirling flow SW is generated in the main chamber 4 due to the difference in lift height between the intake valve 104a and the intake valve 104b.
  • the intake air is pressurized by a supercharger (not shown).
  • the pressures in the main chamber 4 and the sub chamber 6 become the same as the pressure of the intake air.
  • fuel injection mainly for supplying fuel to the main chamber 4 is performed by the fuel injection valve 12.
  • the injected fuel mixes with the intake air in the main chamber 4 to form an air-fuel mixture.
  • the air-fuel mixture is supplied to the entire main chamber 4 as the piston 103 is lowered.
  • the intake valve 104a and the intake valve 104b are closed and the piston 103 is raised to compress the air-fuel mixture in the main chamber 4.
  • the air-fuel mixture is introduced from the main chamber 4 to the sub chamber 6 via the communication passage 8.
  • the air-fuel mixture introduced into the sub-chamber 6 becomes an ascending swirling flow (see the arrow in the sub-chamber 6 in FIG. 4) by the communication passage 8.
  • the inner wall surface 8c of the communication passage 8 is formed along the tangent line S2 of the inner circumference 61c of the sub-chamber wall 61.
  • an ascending lateral vortex is generated along the inner circumference 61c in the sub chamber 6, and the spark plug 10 ignites the lateral vortex.
  • the diameter Dr of the inner circumference 61c of the sub chamber wall 61 expands from the main chamber 4 toward the cylinder head 102 (see FIG. 3).
  • the flow velocity of the lateral vortex in the sub chamber 6 is reduced.
  • misfire caused by the flow velocity of the lateral vortex in the sub chamber 6 being too high is prevented.
  • the air-fuel mixture introduced into the sub chamber 6 is ignited and burned by the spark plug 10. As shown in FIG. 5, at this time, the flame G is injected from the injection port 8a. Then, the air-fuel mixture in the main chamber 4 burns, and the pressure rises due to the combustion gas generated by the combustion. As a result, the piston 103 is pushed down and proceeds to the expansion stroke.
  • the injection port 8a of the communication passage 8 extends in the rotation direction F of the swirling flow SW generated in the main chamber 4 along the outer circumference 61b of the sub chamber wall 61, and causes the flame G in the rotation direction F. Guide.
  • the flame G is injected and then flowed by the swirling flow SW in the rotation direction F of the swirling flow SW. Therefore, the flame G is flown toward the adjacent passages 8 like the flame G1 (see the arrow Gn in FIG. 5).
  • the flame G1 spreads in the space V in the main chamber 4 between the flame G and the flame ejected from the adjacent passage 8. In space V, the flame does not reach and combustion tends to be imbalanced.
  • the inner diameter of the communication passage 8 increases from the inner diameter Db at the introduction port 8b to the inner diameter Da at the injection port 8a.
  • the area of the injection port 8a increases.
  • the diameter of the flame injected from the injection port 8a also increases. Therefore, a large flame G1 is ejected into the space V in the main chamber 4 between the flame G injected from the communication passage 8 and the flame G injected from the adjacent communication passage 8.
  • the combustion of the space V is promoted.
  • the diameter of the injection port 8a increases in the rotation direction F of the swirling flow SW. As a result, the flame G is easily swept by the swirling flow SW. Therefore, more flame G is supplied to the space V. As a result, the combustion of the space V is promoted.
  • the exhaust valve 109 opens, the piston 103 rises from the bottom dead center, and the combustion gas (exhaust) in the cylinder is discharged to the exhaust port 110. Then, when the piston 103 reaches top dead center, the intake stroke starts again. When the piston 103 reciprocates twice in this way, four strokes are completed.
  • the injection port 8a of the communication passage 8 is the rotation direction F of the swirling flow SW generated in the main chamber 4 along the outer circumference 61b of the sub-chamber wall 61. Lead the flame G to. As a result, the occurrence of cooling loss of the flame G injected from the sub chamber 6 toward the main chamber 4 is reduced, and the combustion of the main chamber 4 is promoted.
  • the sub-chamber internal combustion engine 1 is a direct injection type internal combustion engine, but the present disclosure is not limited to this.
  • it may be an auxiliary chamber type internal combustion engine provided with an intake port injector provided at the intake port 105.
  • the communication passage 8 may be one or a plurality.
  • the inner diameter of the communication passage 8 increases toward the outer circumference 61b of the sub-chamber wall 61, but the present disclosure is not limited to this.
  • the inner diameter of the communication passage 8 may be constant. That is, the inner diameter Da of the communication passage 8 at the injection port 8a in FIG. 2 and the inner diameter Db of the communication passage 8 at the introduction port 8b may be the same.
  • the communication passage 8 is provided at one position in the protruding direction of the sub chamber 6, but the present disclosure is not limited to this.
  • the first passage 208 and the second passage 209 may be provided at different positions in the protruding direction of the sub chamber 206.
  • the inner diameter of either the first passage 208 or the second passage 209 may be constant.
  • the inner diameter of the other passage may be expanded toward the outer circumference 261b of the sub chamber wall 261.
  • the inner diameter of the second passage 209 may be constant. As a result, the amount of flame injected from the first passage 208 near the tip 210c of the spark plug 210 increases.
  • the bottom 61a has a hemispherical shape, but the present disclosure is not limited to this. As shown in FIG. 6, the shape of the bottom portion 261a may be a truncated cone shape. Further, it may have various shapes such as a conical shape.
  • the swirl flow generation unit 14 generates a swirl flow, but the present disclosure is not limited to this.
  • the swirling flow generating unit 14 may generate a vertical vortex that swirls in one direction along a plane parallel to the cylinder axial direction Q, that is, may generate a tumble flow.
  • the communication passage 8 may be formed along the rotation direction of the tumble flow.
  • the shape of the sub chamber is an example of a shape (hemispherical shape, cylindrical shape, etc.) having a circular cross section due to a plane perpendicular to the cylinder axis direction.
  • the cross section may be an ellipse or a regular polygon. From the viewpoint of flame propagation, a symmetrical shape is preferable, but the shape is not limited to this.
  • Geometric expressions such as "diameter direction", “diameter direction”, and "tangent line” in the present disclosure can be appropriately understood by those skilled in the art even when the cross section is other than circular. That is, even in an embodiment in which the cross section of the sub chamber is other than circular, those skilled in the art will be able to appropriately apply the features of the present disclosure so as to obtain the same effects as those of the present disclosure.
  • a spark-ignition internal combustion engine in which the air-fuel mixture is ignited by a spark plug provided in the sub chamber is taken as an example.
  • Gasoline is used as a fuel in the internal combustion engine of the present disclosure, but the fuel is not limited to this, and other fuels such as alcohol may be used.
  • the features of the present disclosure are not limited to the spark ignition internal combustion engine, and can be applied to a compression ignition internal combustion engine such as a diesel engine. In other words, it is not essential to provide a spark plug or other spark generating means in the sub-chamber, and it is the first normal in one combustion cycle of an internal combustion engine (in the case of a 4-stroke engine, a cycle consisting of intake, compression, combustion, and exhaust).
  • the internal combustion engine is designed so that combustion (pre-combustion) occurs in the sub-chamber. It is well known that even in a compression ignition internal combustion engine, pre-combustion can be generated in the sub-chamber by injecting fuel directly from the injector into the sub-chamber or by setting the compression ratio appropriately. Further, even in the case of a compression ignition internal combustion engine, the fuel is not particularly limited to light oil, and may be gasoline, alcohol, or the like.
  • the sub-chamber internal combustion engine (1) is The main chamber (4) defined by the cylinder (101a), the cylinder head (102), and the piston (103), A sub-chamber (6) that protrudes from the cylinder head (102) toward the main chamber (4) and is provided separately from the main chamber (4) to generate pre-combustion before combustion in the main chamber (4).
  • the injection port (8a) is configured to guide the flame in the rotation direction (F) of the swirling flow (SW) generated in the main chamber (4).
  • the injection port (8a) may extend in the rotation direction (F) toward the main chamber (4).
  • the inner diameter (Da) of the injection port (8a) may be enlarged as it approaches the main chamber (4).
  • the wall surface (8d) may extend in a direction in which the inner diameter (Da) expands from the inner wall surface (8c) located outside the sub chamber (6).
  • the inner wall surface (8c) of the communication passage (8) forming the injection port (8a) is the inner circumference (61c) of the sub chamber (6). ) May be formed along the tangent line (S2).
  • the inner diameter (Dr) of the sub chamber (6) may be expanded from the main chamber (4) toward the cylinder head (102).
  • Sub-chamber internal combustion engine 4 Main chamber 6: Sub-chamber 8: Communication passage 8c: Inner wall surface 14: Swirling flow generator 61: Sub-chamber wall 61b: Outer circumference 61c: Inner circumference 101a: Cylinder 102: Cylinder head 103: Piston Da: Inner diameter Db: Inner diameter Dr: Inner circumference diameter F: Swirling flow rotation direction S2: Inner circumference tangent SW: Swirling flow

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)

Abstract

Moteur à combustion interne de type à pré-chambre comprenant une chambre principale, une pré-chambre et un passage de liaison. La chambre principale est délimitée dans une culasse, un cylindre et des pistons. La pré-chambre fait saillie de la culasse vers la chambre principale et est séparée de la chambre principale. La précombustion se produit dans la pré-chambre avant la combustion dans la chambre principale. Le passage de liaison relie la chambre principale et la pré-chambre et comporte un orifice d'injection qui injecte des flammes de précombustion dans la chambre principale. L'orifice d'injection est conçu de façon à guider les flammes dans le sens de rotation pour générer un écoulement tourbillonnant à l'intérieur de la chambre principale.
PCT/JP2020/012157 2019-03-27 2020-03-18 Moteur à combustion interne de type à pré-chambre WO2020196207A1 (fr)

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JP2019061136 2019-03-27
JP2019-061136 2019-03-27

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