Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
  • F02F1/00—Cylinders; Cylinder heads 
  • F02F1/24—Cylinder heads
  • F02F1/242—Arrangement of spark plugs or injectors
• • 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
  • F02B19/10—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder
  • F02B19/1019—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber
  • F02B19/1023—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber pre-combustion chamber and cylinder being fed with fuel-air mixture(s)
  • F02B19/1028—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber pre-combustion chamber and cylinder being fed with fuel-air mixture(s) pre-combustion chamber and cylinder having both intake ports or valves, e.g. HONDS CVCC
  • F02B19/1061—Engines characterised by precombustion chambers with fuel introduced partly into pre-combustion chamber, and partly into cylinder with only one pre-combustion chamber pre-combustion chamber and cylinder being fed with fuel-air mixture(s) pre-combustion chamber and cylinder having both intake ports or valves, e.g. HONDS CVCC with residual gas chamber, e.g. containing spark plug
• • 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
  • F02B17/00—Engines characterised by means for effecting stratification of charge in cylinders
  • F02B17/005—Engines characterised by means for effecting stratification of charge in cylinders having direct injection in the combustion chamber
• • 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
  • F02B19/12—Engines characterised by precombustion chambers with positive ignition
• • 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
  • F02B23/101—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 the injector being placed on or close to the cylinder centre axis, e.g. with mixture formation using spray guided concepts
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D41/00—Electrical control of supply of combustible mixture or its constituents
  • F02D41/02—Circuit arrangements for generating control signals
  • F02D41/021—Introducing corrections for particular conditions exterior to the engine
  • F02D41/0235—Introducing corrections for particular conditions exterior to the engine in relation with the state of the exhaust gas treating apparatus
  • F02D41/024—Introducing corrections for particular conditions exterior to the engine in relation with the state of the exhaust gas treating apparatus to increase temperature of the exhaust gas treating apparatus
  • F02D41/0255—Introducing corrections for particular conditions exterior to the engine in relation with the state of the exhaust gas treating apparatus to increase temperature of the exhaust gas treating apparatus to accelerate the warming-up of the exhaust gas treating apparatus at engine start
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02P—IGNITION, OTHER THAN COMPRESSION IGNITION, FOR INTERNAL-COMBUSTION ENGINES; TESTING OF IGNITION TIMING IN COMPRESSION-IGNITION ENGINES
  • F02P15/00—Electric spark ignition having characteristics not provided for in, or of interest apart from, groups F02P1/00 - F02P13/00 and combined with layout of ignition circuits
  • F02P15/02—Arrangements having two or more sparking plugs
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02P—IGNITION, OTHER THAN COMPRESSION IGNITION, FOR INTERNAL-COMBUSTION ENGINES; TESTING OF IGNITION TIMING IN COMPRESSION-IGNITION ENGINES
  • F02P5/00—Advancing or retarding ignition; Control therefor
  • F02P5/04—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions
  • F02P5/145—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions using electrical means
  • F02P5/15—Digital data processing
  • F02P5/1502—Digital data processing using one central computing unit
  • F02P5/1504—Digital data processing using one central computing unit with particular means during a transient phase, e.g. acceleration, deceleration, gear change
• • 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
  • F02B2023/085—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition using several spark plugs per 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
  • F02B75/00—Other engines
  • F02B75/12—Other methods of operation
  • F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
• • H—ELECTRICITY
  • H01—ELECTRIC ELEMENTS
  • H01T—SPARK GAPS; OVERVOLTAGE ARRESTERS USING SPARK GAPS; SPARKING PLUGS; CORONA DEVICES; GENERATING IONS TO BE INTRODUCED INTO NON-ENCLOSED GASES
  • H01T13/00—Sparking plugs
  • H01T13/54—Sparking plugs having electrodes arranged in a partly-enclosed ignition chamber
• • 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

• the present invention relates to an internal combustion engine with a spark plug and prechamber spark plug and a method for operating an internal combustion engine.
• prechamber spark plugs comprise a center electrode arranged in a housing and a ground electrode which define an ignition gap between them in which an air-fuel mixture is ignited. This ignited air-fuel mixture is then conducted through openings in a spark plug cap located at the combustion-chamber end of the prechamber spark plug into a combustion chamber of the internal combustion engine, in which the actual combustion of an air-fuel mixture for the piston stroke takes place.
• a spark plug cap located at the combustion-chamber end of the prechamber spark plug into a combustion chamber of the internal combustion engine, in which the actual combustion of an air-fuel mixture for the piston stroke takes place.
• the internal combustion engine according to the invention with the features of claim 1 is characterized by an improved mode of operation, which allows particularly high efficiency with a low knock tendency and reliable operation in any operating conditions. According to the invention, this is achieved by an internal combustion engine which includes at least one cylinder and which includes one spark plug and one prechamber spark plug per cylinder. Furthermore, the internal combustion engine includes four gas exchange openings per cylinder. A first gas exchange opening and a second gas exchange opening are in each case inlet openings, and a third gas exchange opening and a fourth gas exchange opening are respectively outlet openings.
• a “spark plug” is considered to be an ordinary spark plug, in particular one with exposed electrodes, which is set up to ignite a fuel-air mixture between at least two electrodes by means of an electrical ignition spark.
• the spark plug particularly preferably has a straight center electrode and at least one hook-shaped front or top electrode.
• such a spark plug can alternatively also be referred to as a “spark spark plug”.
• a laser device that is set up to ignite the fuel-air mixture by means of laser radiation could also be used as the “spark plug”.
• a “pre-chamber spark plug” is a design with a pre-chamber formed within a spark plug cap, which is in fluid communication with a combustion chamber of the internal combustion engine via through-openings in the spark plug cap. This allows gases to pass from the pre-chamber through the plug cap into the combustion chamber and vice versa.
• the plug cap is preferably arranged on an end of a housing of the prechamber spark plug that is on the combustion chamber side, viewed in the axial direction of the prechamber spark plug.
• the plug cap, housing and prechamber form integral parts of the prechamber spark plug. In particular, the prechamber is thus located within the prechamber spark plug.
• electrodes are used to ignite a fuel-air mixture located therein, with torch jets passing through the openings in the spark plug cap and igniting the fuel-air mixture in the combustion chamber.
• the prechamber spark plug is preferably to be regarded as an integral component which can be fastened in a cylinder head of the internal combustion engine. The fastening is preferably carried out in such a way that in an end position the through-openings in the candle cap are aligned in a predefined manner in order in particular to generate specifically aligned torch jets during operation.
• the prechamber spark plug can be designed in such a way that it can be screwed into a standard thread of the cylinder head, which can accommodate a conventional spark plug.
• the combination of a conventional spark plug and a prechamber spark plug offers the advantage of a particularly flexible, efficient, and reliable mode of operation of the internal combustion engine.
• optimal and reliable ignition of the fuel-air mixture in the combustion chamber can always take place in any operating state, such as cold start, catalytic converter heating phase, partial load, full load, and the like.
• Operation of the internal combustion engine can preferably be designed in such a way that the prechamber spark plug is used as the sole ignition option in the largest possible operating range in order to achieve effective knock reduction and low fuel consumption, particularly at high loads.
• the spark plug can be operated additionally or solely in operating ranges in which operation of the prechamber spark plug is disadvantageous or impossible, for example during a cold start, in order to achieve reliable ignition in these ranges as well.
• the prechamber spark plug can be optimized specifically for the most efficient operation possible, for example for certain operating points of the internal combustion engine, with falling efficiency at other operating points being negligible or acceptable, since at these operating points, for example, alone or the spark plug can also be used for ignition.
• damage to the internal combustion engine for example due to knocking, misfiring or poor combustion, can be avoided due to the always optimally adaptable ignition for a wide variety of operating ranges, thus enabling a particularly long service life for the internal combustion engine.
• the spark plug and/or the prechamber spark plug is/are preferably arranged on a combustion chamber roof of a combustion chamber of the cylinder.
• the combustion chamber roof forms an upper end of the combustion chamber along a stroke direction of a piston.
• the combustion chamber roof is preferably part of a cylinder head of the internal combustion engine.
• the prechamber spark plug and the spark plug preferably protrude into the combustion chamber.
• a plug cap of the prechamber spark plug and electrodes of the spark plug preferably protrude into the combustion chamber.
• the ends of the combustion chamber Prechamber spark plug and the spark plug can also be arranged within a respective candle bore, in which the corresponding prechamber spark plug or spark plug is arranged.
• the prechamber spark plug is arranged closer to a center point of the combustion chamber roof than the spark plug.
• the spark plug is preferably arranged closer to the center point of the combustion chamber roof than the prechamber spark plug in order to achieve particularly effective and uniform ignition by means of the spark plug.
• the prechamber spark plug is located closer to a side wall of the cylinder than the spark plug.
• the prechamber spark plug is preferably designed and arranged in such a way that flare jets generated during ignition by means of the prechamber spark plug are aligned in the direction of a center of the combustion chamber.
• the spark plug is located closer to the side wall of the cylinder than the prechamber spark plug.
• a substantially cylindrical lateral surface of the cylinder which can also be referred to as the running surface of the piston, is regarded as the side wall.
• a reference direction which indicates a relative arrangement of the inlet openings and outlet openings to one another or on the combustion chamber roof, is considered to be on the inlet side or outlet side.
• an inlet-side arrangement of the spark plug to the prechamber spark plug means that the spark plug is arranged further along an axis that extends from the outlet openings to the inlet openings in the direction pointing to the inlet openings than the prechamber spark plug, i.e. the spark plug is closer to the inlet opening than arranged the prechamber spark plug. It is particularly advantageous if the spark plug is arranged on the outlet side of the prechamber spark plug, ie the spark plug is arranged closer to the outlet opening than the prechamber spark plug.
• the prechamber spark plug is arranged closer to the inlet openings than the spark plug.
• the gas exchange openings are arranged in the combustion chamber roof, the combustion chamber roof being divided into four quadrants by two mutually perpendicular sectional planes.
• the combustion chamber roof is divided by the two sectional planes in such a way that one of the four gas exchange openings is located in each of the four quadrants.
• the spark plug and/or the prechamber spark plug is/are arranged, in particular essentially, on one of the two sectional planes.
• the two sectional planes are each located centrally between the gas exchange openings.
• the two cutting planes preferably intersect in a cutting line which is parallel to a piston direction along which a piston of the internal combustion engine is movable.
• the spark plug and/or the prechamber spark plug lies essentially symmetrically between two gas exchange openings.
• the two cutting planes particularly preferably form planes of symmetry of the combustion chamber roof.
• the spark plug and/or the prechamber spark plug is preferably arranged within a central area of the combustion chamber roof.
• the central area lies essentially radially inside the gas exchange openings and in particular surrounds an area around a central point or a roof center of the combustion chamber roof.
• the prechamber spark plug is particularly preferably arranged precisely on a center point of the combustion chamber roof.
• the midpoint area is particularly preferably defined by a circle of maximum size, which is inscribed in the middle between the gas exchange openings.
• This means that the spark plug and/or the pre-chamber spark plug is preferably located centrally on the combustion chamber roof, as a result of which particularly symmetrical, uniform penetration and thus simultaneous ignition within the entire combustion chamber is made possible.
• a particularly uniform penetration of the combustion chamber by the flare jets which achieve the ignition, and thus a uniform and efficient combustion can thereby be made possible.
• the spark plug and/or the pre-chamber spark plug is particularly preferably arranged between two adjacent gas exchange openings and the side wall of the cylinder.
• the spark plug and/or the prechamber spark plug lies radially outside of a center circle on which the center points of the four gas exchange openings lie.
• the spark plug and/or the prechamber spark plug is arranged within a free, radially outer area of the combustion chamber roof.
• four such radially outer and free areas are distributed around the circumference of the combustion chamber roof.
• one of the spark plugs and the prechamber spark plug is arranged within the central area and the other is arranged radially on the outside.
• a distance between the side wall of the cylinder and the spark plug and/or a distance between the side wall of the cylinder and the prechamber spark plug is preferably at most 30%, preferably at most 15%, of a cylinder radius of the cylinder. Due to the lateral arrangement near the side wall is the spark plug and / or The prechamber spark plug is also at a large distance from the center of the combustion chamber, which means that the thermal load is lower than with a central arrangement, for example. This has an advantageous effect on a long service life for the spark plug and/or the prechamber spark plug.
• the internal combustion engine preferably also includes a combustion chamber fuel injector, which is set up to inject, in particular, liquid or gaseous fuel directly into the combustion chamber of the internal combustion engine.
• the combustion chamber fuel injector is preferably arranged on the combustion chamber roof.
• the combustion chamber fuel injector is thus located in the vicinity of the prechamber spark plug and/or the spark plug in order to generate a uniform fuel-air mixture, preferably aligned with the position of the prechamber spark plug and/or spark plug, for homogeneous, uniform ignition.
• the combustion chamber fuel injector is particularly preferably arranged between two adjacent gas exchange openings and the side wall of the cylinder.
• the combustion chamber fuel injector lies radially outside of a center circle on which the center points of the four gas exchange openings lie.
• the combustion chamber fuel injector is arranged within a free, radially outer area of the combustion chamber roof.
• the combustion chamber fuel injector is set up here to inject the fuel towards a center of the combustion chamber in order to obtain uniform distribution and ignition.
• An arrangement of the combustion chamber fuel injector between the two inlet openings and the side wall of the cylinder is particularly advantageous in order to promote optimal, uniform mixture formation before combustion.
• the lateral arrangement results in a greater distance between the combustion chamber fuel injector and the center of the combustion chamber, which can have an advantageous effect on a lower thermal load on the combustion chamber fuel injector in order to enable a long service life.
• a distance between the combustion chamber fuel injector and the side wall of the cylinder is preferably at most 30%, particularly preferably at most 15%, of the cylinder radius.
• the combustion chamber Fuel! njector preferably close to the side wall, i.e. it is not arranged centrally but on the side of the combustion chamber roof.
• the combustion chamber fuel injector is preferably aligned at an angle, so that an injection direction of the fuel to be injected is aligned in the direction of the center of the combustion chamber.
• the lateral arrangement of the combustion chamber fuel injector enables a particularly space-saving arrangement on the combustion chamber roof, which means that more space is available for arranging the spark plug and/or the prechamber spark plug, particularly in the central area of the combustion chamber roof.
• the combustion chamber fuel injector and the prechamber spark plug are particularly preferably arranged on opposite sides of the combustion chamber roof.
• the combustion chamber fuel injector and the spark plug are preferably arranged on opposite sides of the combustion chamber roof.
• an arrangement that is opposite with respect to a center point of the combustion chamber roof is considered to be opposite. This allows a particularly advantageous utilization of the free space available for arranging the components on the combustion chamber roof.
• the combustion chamber fuel injector is preferably arranged within a center region of the combustion chamber roof, with the center region lying radially inside the gas exchange openings.
• the combustion chamber fuel injector is particularly preferably arranged precisely on a center point of the combustion chamber roof.
• a central arrangement of the combustion chamber fuel injector on the combustion chamber roof allows particularly uniform, preferably symmetrical, injection into the combustion chamber in order to enable particularly uniform fuel distribution in the combustion chamber and efficient combustion.
• the prechamber spark plug is particularly preferably arranged closer to the combustion chamber fuel injector than the spark plug.
• Such an arrangement of the combustion chamber fuel injector and the prechamber spark plug close to one another has a particularly advantageous effect on efficient and reliable operation of the prechamber spark plug.
• the proximity between the combustion chamber fuel injector and the prechamber spark plug results in improved scavenging and mixture supply to the prechamber of the prechamber spark plug.
• the spark plug is arranged closer to the combustion chamber fuel injector than the pre-chamber spark plug. In this case, a particularly good mixture supply can be provided in the area of the spark plug.
• Such an arrangement of the combustion chamber fuel injector and the spark plug close to one another allows, for example, a particularly robust operation of the internal combustion engine during catalyst heating.
• the combustion chamber fuel injector and the prechamber spark plug are preferably arranged at a distance of at most 50%, in particular at most 30%, preferably at most 10%, of a cylinder radius of the cylinder.
• the combustion chamber fuel injector and the spark plug are preferably arranged at a distance of at most 50%, in particular at most 30%, preferably at most 10%, of the cylinder radius of the cylinder.
• An injection direction, ie a direction along which the fuel is essentially injected, of the combustion chamber fuel injector is particularly preferably aligned in the direction of the prechamber spark plug, in particular towards a plug cap of the prechamber spark plug.
• the direction of injection is preferably aligned essentially in the direction of the spark plug.
• the internal combustion engine also includes an intake manifold fuel injector, which is set up for injecting fuel into an intake manifold of the internal combustion engine.
• the internal combustion engine comprises two intake manifolds, each with an intake manifold fuel injector, each intake manifold opening into the combustion chamber at one of the two inlet openings.
• the internal combustion engine can also include exactly one intake manifold fuel injector, which is set up for injecting fuel into both intake manifolds.
• the internal combustion engine can include exactly one intake manifold fuel injector, which is set up to inject fuel into a common intake manifold section, with the intake manifold section divides into the two intake manifolds in the direction of the combustion chamber.
• the intake manifold fuel injector is advantageously an alternative to a direct-injecting one arranged on the combustion chamber Combustion chamber fuel injector provided.
• the intake manifold fuel injector is advantageously an alternative to a direct-injecting one arranged on the combustion chamber Combustion chamber fuel injector provided.
• the invention relates to a method for operating an internal combustion engine which has at least one cylinder and four gas exchange openings per cylinder, a spark plug and a prechamber spark plug.
• the spark plug and/or the pre-chamber spark plug is operated in order to ignite a fuel-air mixture within the combustion chamber of the cylinder. This means that during operation of the internal combustion engine, simultaneous operation of both the prechamber spark plug and the spark plug, or alternatively operation of the spark plug or the prechamber spark plug alone, can take place in order to ignite the fuel-air mixture in the combustion chamber of the cylinder. This allows a particularly flexible and efficient operation of the internal combustion engine.
• the prechamber spark plug is preferably operated alone during operation of the internal combustion engine under high load, in particular while the spark plug is inactive. Operation at a torque of at least 20%, preferably at least 50%, particularly preferably at least 80%, of a nominal torque of the internal combustion engine is preferably regarded as a high load.
• This torque threshold can preferably be dependent on a speed of the internal combustion engine, or other key figures, such as a lambda number, control times of valves, an engine temperature, or the like.
• the spark plug is operated alone during low load operation of the internal combustion engine, particularly while the prechamber spark plug is inactive. Operation at a torque of less than 80%, preferably less than 50%, particularly preferably less than 20%, of a nominal torque of the internal combustion engine is preferably regarded as a low load. This can reliable ignition by means of the spark plug can be enabled even at low loads.
• the spark plug is particularly preferably operated during a catalytic converter heating phase, in particular after a cold start of the internal combustion engine.
• the spark plug is preferably operated on its own, in particular while the prechamber spark plug is inactive.
• the spark plug is preferably operated alone at low engine temperatures of the internal combustion engine, preferably at engine temperatures of a maximum of 323 K, in particular a maximum of 303 K, particularly preferably a maximum of 293 K.
• a temperature of a coolant of the internal combustion engine can be determined as the engine temperature, for example, in order to make a particularly simple determination to obtain.
• a combined operation of the spark plug and the prechamber spark plug can also take place simultaneously.
• spark plug is operated while the internal combustion engine is burning up again, in particular after overrun phases, ie after the internal combustion engine is being towed by the vehicle, and preferably at very low loads.
• a combined operation of the spark plug and the prechamber spark plug can also take place simultaneously during such a reburning of the internal combustion engine.
• the spark plug can be operated alone within this partial operating range, that is to say while the prechamber spark plug is inactive.
• the lambda number is particularly preferably at least 1.05 within at least one partial operating range of the internal combustion engine.
• the internal combustion engine is operated within the partial operating range with a lean fuel/air mixture.
• the prechamber spark plug and/or spark plug is preferably operated during lean operation.
• Figure 1 is a sectional view of an internal combustion engine according to a first embodiment of the invention
• FIG. 2 simplified schematic detailed views of various preferred configurations of the internal combustion engine of FIG.
• FIG. 3 simplified schematic detailed views of further preferred configurations of the internal combustion engine of FIG.
• Figure 4 is a sectional view of an internal combustion engine according to a second embodiment of the invention
• Figure 5 shows simplified schematic detail views of various preferred configurations of the internal combustion engine of Figure 4.
• FIG. 1 shows a simplified sectional view of an internal combustion engine 1 according to a first exemplary embodiment of the invention.
• the internal combustion engine 1 comprises a plurality of cylinders 10, only one of the cylinders 10 being shown in FIG.
• the cylinder 10 has a combustion chamber 5 which is delimited by a combustion chamber roof 50 at its upper end.
• the combustion chamber roof 50 is formed by a cylinder head 15 of the internal combustion engine 1 .
• the combustion chamber roof 50 is preferably conical or designed to taper towards the top, with a roof tip forming in particular in the center point 54 (cf. FIG. 2) of the combustion chamber roof 50 .
• the center point 54 lies in the middle, in particular on a central axis 12, of the preferably circular cylinder 10.
• the internal combustion engine 1 comprises four gas exchange openings 4 per cylinder 10 (cf. also FIG. 2).
• a first and a second gas exchange opening 4 each form an inlet opening 41 through which fresh air can flow into the combustion chamber 5 .
• a third and a fourth gas exchange opening 4 each form an outlet opening 42 through which exhaust gases can flow out of the combustion chamber 5 after combustion.
• the internal combustion engine 1 includes a combustion chamber fuel injector 6 per cylinder 10 , which is set up to inject liquid or gaseous fuel directly into the combustion chamber 5 .
• the combustion chamber fuel injector 6 protrudes slightly into the combustion chamber 5 .
• the combustion chamber fuel injector 6 can also be arranged retracted within an injector bore 60 in which it is arranged.
• the internal combustion engine 1 includes a spark plug 2 and a prechamber spark plug 3 per cylinder 10.
• the spark plug 2 is a conventional spark plug that is set up to ignite a fuel/air mixture in the combustion chamber 5 by means of an electric spark.
• the spark plug 2 can have a center electrode 21 and a lateral, hook-shaped front electrode 22, which in particular forms the ground electrode.
• the ignition spark can be generated between the two electrodes 21 , 22 .
• the spark plug 2 can be arranged in a bore 20 inside the cylinder head 15, with the bore 20 opening into the combustion chamber 5.
• the spark plug 2 can also protrude into the combustion chamber 5 .
• the prechamber spark plug 3 has a plug cap 32 which is arranged on an axial end of a housing 34 of the prechamber spark plug 3 .
• the plug cap 32 forms a prechamber 35 within the prechamber spark plug 3, the prechamber 35 being connected to the combustion chamber 5 via through-openings (not shown) which penetrate the plug cap 32.
• a fuel-air mixture within the prechamber 35 can be ignited by means of electrodes 31, so that several, preferably four, torch jets 30 (cf. Figure 2, Figure 3 or Figure 5; shown schematically as club-shaped jets emanating from the prechamber spark plug 3) pass through the passage openings ), in particular in the form of flames, spread into the combustion chamber 5 in order to ignite the fuel-air mixture there.
• the prechamber spark plug 3 is screwed into a bore 33 in the cylinder head 15 .
• the prechamber spark plug 3 is screwed in in such a way that the plug cap 32 protrudes into the combustion chamber 5 .
• the prechamber spark plug 3 is optimized for operating the internal combustion engine 1 under high load and while the internal combustion engine 1 is being operated with a stoichiometric or lean fuel/air mixture. Due to the special ignition method of the prechamber spark plug 3, the fuel-air mixture can be ignited reliably and with a low knocking tendency of the internal combustion engine 1. As a result, a particularly fuel-efficient operation of the internal combustion engine 1 can be made possible without the risk of damage from knocking.
• the spark plug 2 is operated in particular after a cold start, during a catalytic converter heating operation and at low loads in order to also in these Operating areas to allow reliable ignition of the fuel-air mixture in the combustion chamber 5.
• FIGS. 2 and 3 several preferred variants for arrangements of combustion chamber fuel injector 6, spark plug 2 and prechamber spark plug 3 on combustion chamber roof 50 are shown in a simplified, schematic manner, which are described below.
• the piston direction is parallel to the central axis 12 of the cylinder 10.
• all four gas exchange openings 4 have an identical cross section.
• the inlet openings 41 and the outlet openings 42 could also have different cross sections.
• the inlet openings 41 could each have larger cross sections than the outlet openings 42 .
• the outlet openings 42 could each have larger cross sections than the inlet openings 41 .
• the gas exchange openings 4 are each circular and inscribed in the combustion chamber roof 50 in such a way that a maximum overall cross section is available for the gas exchange. Alternatively, the gas exchange openings 4 could also be smaller.
• the components arranged on the combustion chamber roof 50 - spark plug 2, prechamber spark plug 3 and combustion chamber fuel injector 6 - are each essentially on one of the two sectional planes 51, 52, since this is where the greatest space is available for these components .
• FIG. 2 shows variants of arrangements of the components in the combustion chamber roof 50 with a central position of the combustion chamber fuel injector 6.
• the central position is an arrangement within a central region 53, which surrounds a central point 54 of the combustion chamber roof 50 and lies essentially radially inside the gas exchange openings 4, is considered. Due to the central location of the combustion chamber fuel injector 6, a particularly uniform distribution of the injected fuel spray in the combustion chamber 5 can be achieved.
• the combustion chamber fuel injector 6 is on the inlet side of the center 54, that is, closer to the two inlet openings 41 than to the outlet openings 42.
• the combustion chamber fuel injector 6 is located completely within the two inlet-side quadrants 55 , 58.
• there is space for another component within the central area 53 namely the spark plug 2 or the prechamber spark plug 3.
• combustion chamber roof 50 has four side areas 59, which are each arranged between two adjacent gas exchange openings 4 and a side wall 11 of the cylinder 10, and within which components can be arranged.
• Figure 2(a) shows an arrangement with the pre-chamber spark plug 3 within the central area 53.
• the fuel-air mixture can be ignited as centrally as possible by means of the pre-chamber spark plug 3, which means that the torch jets 30 and thus particularly evenly penetrate the combustion chamber 5 a particularly uniform ignition in the combustion chamber 5 can be achieved.
• a distance 36 between the prechamber spark plug 3 and the combustion chamber fuel injector 6 can be kept to a minimum, which has an advantageous effect on flushing and supplying the mixture to the prechamber 35 .
• FIG. 2(a) Due to the proximity of the combustion chamber fuel injector 6 and the prechamber spark plug 3, the arrangement of FIG. 2(a) also offers a particularly efficient mode of operation of the internal combustion engine 1 when operating the prechamber spark plug 3, since the spray generated can be ignited in a particularly targeted and reliable manner by the flare jets 30.
• effective scavenging of prechamber 35 of prechamber spark plug 3 and optimum mixture supply can be achieved, which has a particularly advantageous effect on robust and effective operation of prechamber spark plug 3.
• the spark plug 2 is arranged laterally, close to the side wall 11 of the cylinder 10.
• the spark plug 2 is arranged in the side area 59 on the inlet side, which lies in the two quadrants 55, 58 on the inlet side, i.e. close to the two inlet openings 41.
• FIG. 2(b) shows an arrangement which essentially corresponds to the arrangement in FIG. This allows, for example, the combustion chamber fuel injector 6 to be aligned more towards the outlet openings 42 in order to bring the fuel spray close to the candle 3 and the spark plug 2.
• FIG. 2(c) shows an arrangement similar to FIG. 2(a), with the positions of spark plug 2 and prechamber spark plug 3 being reversed. That is, the spark plug 2 is arranged in the center area 53 close to the combustion chamber fuel injector 6 and the pre-chamber spark plug 3 is arranged close to the side wall 11 on the inlet side. Due to the central arrangement of the spark plug 2 close to the center point 54 and close to the combustion chamber fuel injector 6, a particularly robust and efficient operation of the internal combustion engine can be achieved during ignition by means of the spark plug 2, preferably at low loads and/or during a catalyst heating phase.
• the prechamber spark plug 3 is designed and arranged in such a way that the torch jets 30 are aligned in the direction of the center of the combustion chamber roof. As a result, particularly fuel-efficient operation can be made possible even when the prechamber spark plug 3 is operated alone, for example in medium or high load ranges of the internal combustion engine 1 .
• the lateral arrangement of the prechamber spark plug 3 offers the advantage due to the distance to the center of the combustion chamber 5 that lower temperatures act on the plug cap 32 and thus a lower load and a longer service life of the prechamber spark plug 3 can be made possible.
• Figure 2(d) shows an arrangement which essentially corresponds to the arrangement of Figure 2(c), with the difference that the prechamber spark plug 3 is arranged in the outlet-side side area 59, i.e. on the outlet side of the spark plug 2 and combustion chamber fuel injector 6 .
• the flare jets 30 that the prechamber spark plug 3 generates are aligned in the direction of the inlet openings 41 .
• FIG. 2(e) shows an arrangement similar to FIGS. 2(a) and (b) with a central prechamber spark plug 3, the spark plug 2 being arranged in a side region 59 lying on the second sectional plane 52.
• the side area 59 is in one of the two intake-side quadrants 55, 58 and one of the two exhaust-side quadrants 56, 57.
• This makes it possible to provide a particularly advantageous installation position for the spark plug 2 in the cylinder head 15, since the one with the intake openings 41 and exhaust openings 42 Connected intake manifolds and exhaust manifolds often point away from each other within the cylinder head 15.
• the spark plug 2 can also be arranged in the left-hand side area 59 of the quadrants 57 and 58.
• FIG. 3 shows variants in which the combustion chamber fuel injector 6 is arranged laterally on the combustion chamber roof 50, namely in the side region 59 on the inlet side.
• the combustion chamber fuel injector 6 is arranged at a small distance 61 from the side wall 11 . Due to the lateral arrangement of the combustion chamber fuel injector 6, the center area 53 of the Combustion chamber roof 50 around the center point 54 has plenty of space for the spark plug 2 and the prechamber spark plug 3, so that both of these can be arranged as centrally as possible for improved, uniform ignition.
• An injection direction of the combustion chamber fuel injector 6 is aligned in the direction of the center of the combustion chamber in order to achieve the most uniform possible distribution of the fuel spray in the combustion chamber 5 .
• FIG. 3(a) shows a variant in which spark plug 2 is arranged on the inlet side of prechamber spark plug 3
• FIG. 3(b) shows a variant in which spark plug 2 is arranged on the outlet side of prechamber spark plug 3.
• FIG. 3(c) and FIG. 3(d) also show variants in which the spark plug 2 is arranged centrally and the prechamber spark plug 3 is arranged laterally on the combustion chamber roof 50. This is particularly advantageous when there is not enough space for both the spark plug 2 and the pre-chamber spark plug 3 in the center region 53 .
• the spark plug 2 is arranged exactly in the center 54 of the combustion chamber roof 50, which enables a particularly robust operation of the internal combustion engine 1 when the spark plug 2 is in operation, for example during a catalytic converter heating phase.
• the prechamber spark plug 3 is arranged in the left-hand side area 59, which lies between the side wall 11 and one of the inlet openings 41 and one of the outlet openings 42, respectively.
• Figure 3(d) also shows a variant in which the prechamber spark plug 3 is arranged in the side area 59 on the outlet side, i.e. close to the two outlet openings 42. It should be noted that, as an alternative to the variants shown in FIG. 3(c) and in FIG. 3(d), an arrangement of the prechamber spark plug 3 in each of the other side regions 59 is also possible.
• FIG. 1 a variant is shown in FIG.
• the spark plug 2 is arranged in the right-hand side area 59 , ie between the side wall 11 , one of the two inlet openings 41 and one of the two outlet openings 42 .
• an arrangement of the spark plug in any other of the side areas 59 is also possible.
• FIG. 4 shows a sectional view of an internal combustion engine 1 according to a second exemplary embodiment of the invention.
• the second exemplary embodiment essentially corresponds to the first exemplary embodiment in FIGS. 1 to 3, with the difference that instead of a combustion chamber fuel injector 6 which is arranged in the combustion chamber roof 50 and injects directly, an intake manifold fuel injector 7 is provided.
• the intake manifold fuel injector 7 is arranged in the cylinder head 15 and on an intake manifold 70 and set up to inject liquid or gaseous fuel into the intake manifold 70 .
• the intake manifold 7 opens into the combustion chamber 5 at the intake opening 41 and thus conducts the fuel-air mixture into the combustion chamber 5.
• one intake manifold 70 is provided for each intake opening 41, with one intake manifold fuel injector 7 is provided (not shown).
• Figure 5 shows variants of the arrangements of spark plug 2 and prechamber spark plug 3 on combustion chamber roof 50 of internal combustion engine 1 of the second exemplary embodiment of Figure 4. Since no fuel injector is arranged on combustion chamber roof 50 in the second exemplary embodiment, there is advantageously more space for spark plug 2 and the prechamber spark plug 3 available.
• the arrangements in FIG. 5 are similar to FIG. 3, resulting in essentially the same advantages.
• the spark plug 2 and the prechamber spark plug 3 can both be arranged in the central area 53 .
• FIG. 5(c) and FIG. 5(d) also show variants with a central spark plug 2, which is arranged exactly in the center 54 of the combustion chamber roof 50.
• the prechamber spark plug 3 is arranged in the left side area 59, and in Figure 5(d) in the side area 59 on the exhaust side.
• FIG. 5(e) also shows a variant with a central prechamber spark plug 3 arranged precisely in the center 54.
• the spark plug 2 is arranged in the right-hand side area 59 .
• spark plug 2 or prechamber spark plug 3 can also be arranged in any of the four side areas 59 as an alternative to the positions shown in FIG. 5(c) to FIG. 5(e).
• distances to which reference is made are to be regarded as minimum distances. That means, for example, a “distance between prechamber spark plug and combustion chamber fuel injector” is regarded as the minimum distance of an outer circumference of the spark plug, in particular essentially in a plane of the combustion chamber roof, to the outer circumference of the combustion chamber fuel injector.

Landscapes

• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Theoretical Computer Science (AREA)
• Signal Processing (AREA)
• Combustion Methods Of Internal-Combustion Engines (AREA)
• Ignition Installations For Internal Combustion Engines (AREA)
• Fuel-Injection Apparatus (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=80461941

Family Applications (1)

Country Status (7)

Families Citing this family (1)

Family Cites Families (8)

• 2021
  • 2021-02-26 DE DE102021104627.0A patent/DE102021104627A1/de active Pending
• 2022
  • 2022-02-16 EP EP22706291.6A patent/EP4298325A1/de active Pending
  • 2022-02-16 US US18/546,559 patent/US20240229734A9/en active Pending
  • 2022-02-16 JP JP2023548793A patent/JP2024507169A/ja active Pending
  • 2022-02-16 WO PCT/EP2022/053790 patent/WO2022179910A1/de active Application Filing
  • 2022-02-16 CN CN202280017157.8A patent/CN116888353A/zh active Pending
  • 2022-02-16 KR KR1020237032642A patent/KR20230145612A/ko unknown

Also Published As

Similar Documents

Legal Events