EP3850205A1 - Procédé pour faire fonctionner un moteur à combustion interne - Google Patents

Procédé pour faire fonctionner un moteur à combustion interne

Info

Publication number
EP3850205A1
EP3850205A1 EP19765707.5A EP19765707A EP3850205A1 EP 3850205 A1 EP3850205 A1 EP 3850205A1 EP 19765707 A EP19765707 A EP 19765707A EP 3850205 A1 EP3850205 A1 EP 3850205A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
exhaust
internal combustion
combustion engine
stroke
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP19765707.5A
Other languages
German (de)
English (en)
Inventor
Thomas Malischewski
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
MAN Truck and Bus SE
Original Assignee
MAN Truck and Bus SE
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by MAN Truck and Bus SE filed Critical MAN Truck and Bus SE
Publication of EP3850205A1 publication Critical patent/EP3850205A1/fr
Pending legal-status Critical Current

Links

Classifications

    • 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
    • F02D41/0002—Controlling intake air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0203—Variable control of intake and exhaust valves
    • F02D13/0207—Variable control of intake and exhaust valves changing valve lift or valve lift and timing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0223—Variable control of the intake valves only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0261—Controlling the valve overlap
    • 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
    • F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D41/0047—Controlling exhaust gas recirculation [EGR]
    • F02D41/006—Controlling exhaust gas recirculation [EGR] using internal EGR
    • 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
    • F02D41/0245—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 by increasing temperature of the exhaust gas leaving the engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0273—Multiple actuations of a valve within an engine cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D2013/0292—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation in the start-up phase, e.g. for warming-up cold engine or catalyst
    • 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
    • F02D41/0002—Controlling intake air
    • F02D2041/001—Controlling intake air for engines with variable valve actuation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/08—Exhaust gas treatment apparatus parameters
    • F02D2200/0802—Temperature of the exhaust gas treatment apparatus
    • 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
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • 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
    • 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
    • Y02T10/40—Engine management systems

Definitions

  • the invention relates to a method for operating an internal combustion engine.
  • the residual gas rate can be influenced in the low load via the valve overlap.
  • this deepens the valve pockets in the piston, which in turn are relevant to consumption.
  • AT 005 783 U1 discloses that the intake valve is opened briefly during the exhaust cycle.
  • US 2009/0194080 A1 relates to a method for purging residual combustion gas from an internal combustion engine with direct injection, in particular a diesel engine.
  • a method for purging residual combustion gas from an internal combustion engine with direct injection in particular a diesel engine.
  • the invention is based on the object of providing a method in which the exhaust gas temperature can be raised under low load.
  • the invention relates to a method for operating an internal combustion engine (z. B. four-stroke internal combustion engine and / or multi-cylinder internal combustion engine).
  • the method involves generating a pressure pulse (eg significant and / or sudden and / or time-limited and / or one-time pressure increase, eg a cyclical pressure pulsation, for example) an exhaust line of the internal combustion engine.
  • the method comprises supplying exhaust gas (eg residual exhaust gas) from a combustion chamber of a cylinder during an exhaust stroke of the cylinder into an inlet channel of the cylinder by spreading the pressure pulse from the exhaust gas line into the combustion chamber of the cylinder.
  • the method comprises supplying the exhaust gas from the inlet channel of the cylinder into the combustion chamber of the cylinder during an intake stroke of the cylinder.
  • the process enables the exhaust gas temperature to be increased in the low load by means of internal residual gas control (residual exhaust gas control) without negatively influencing the full load performance of the internal combustion engine.
  • This increases the possible nitrogen oxide conversion rates of an SCR catalytic converter.
  • the method uses the pressure pulsations in the exhaust system to convey residual gas from the combustion chamber into an intake tract of the internal combustion engine.
  • the residual gas is then flushed back into the combustion chamber of the cylinder in the intake stroke, whereby the mass of fresh air in the combustion chamber of the cylinder is reduced by the mass of the residual gas. Due to the reduced air and therefore also exhaust gas mass flow, the exhaust gas temperature rises with the engine torque remaining unchanged, without negatively influencing the engine's gas exchange work.
  • the pressure pulse in the exhaust line is generated by opening an exhaust valve of a further cylinder of the internal combustion engine during an exhaust stroke of the further cylinder.
  • the further cylinder is operated out of phase with the cylinder, preferably out of phase by approximately -120 ° KW (eg in the case of a six-cylinder internal combustion engine) and / or by -720 ° KW / number of cylinders of the internal combustion engine.
  • the pressure pulse can expediently be conducted, for example, via an exhaust gas turbine, e.g. B. from an exhaust manifold via the exhaust gas turbine to another exhaust manifold.
  • an exhaust gas turbine e.g. B. from an exhaust manifold via the exhaust gas turbine to another exhaust manifold.
  • the exhaust line can be single-flow, i.e. H. with an exhaust manifold, or multi-flow, d. H. be equipped with several exhaust manifolds.
  • the supply of exhaust gas from the combustion chamber of the cylinder is only brought about by an increase in a cylinder pressure in the combustion chamber of the cylinder by the pressure pulse.
  • the cylinder pressure can preferably be increased via a boost pressure in the inlet channel of the cylinder and / or the internal combustion engine.
  • the pressure pulse propagates through an (e.g. already previously) opened exhaust valve of the cylinder, preferably during an exhaust stroke of the cylinder, from the exhaust gas line into the combustion chamber of the cylinder.
  • exhaust gas is fed from the combustion chamber of the cylinder into the inlet channel of the cylinder by the pressure pulse by opening an inlet valve of the cylinder, preferably during an exhaust stroke of the cylinder and / or during the pressure pulse.
  • the exhaust gas is fed from the inlet channel of the cylinder into the combustion chamber of the cylinder during an intake stroke of the cylinder by opening an inlet valve of the cylinder.
  • the inlet valve of the cylinder only opens when the pressure pulse propagates into the combustion chamber of the cylinder.
  • the inlet valve of the cylinder only opens when the cylinder pressure in the combustion chamber of the cylinder increases due to the pressure pulse via a boost pressure in the inlet channel of the cylinder and / or the internal combustion engine.
  • the inlet valve of the cylinder closes if or before the cylinder pressure in the combustion chamber of the cylinder again drops below a boost pressure in the inlet channel of the cylinder and / or the internal combustion engine.
  • the inlet valve of the cylinder opens at the beginning of the outlet stroke of the further cylinder and / or the inlet valve of the cylinder opens when the outlet valve of the further cylinder opens.
  • the intake valve of the cylinder opens in the exhaust stroke of the cylinder and / or closes before the end of the exhaust stroke of the cylinder.
  • the inlet valve of the cylinder is in a range between 100 ° KW after UT (bottom dead center of a piston movement of a piston which is assigned to the cylinder) in the working cycle of the cylinder and 150 ° KW nach UT (bottom dead center of the piston movement of the Piston, which is assigned to the cylinder) open in the exhaust stroke of the cylinder.
  • the inlet valve of the cylinder opens at approximately or after 100 ° KW after UT (bottom dead center of a piston movement of a piston that the cylinder is assigned) in the exhaust stroke of the cylinder, and / or the inlet valve of the cylinder closes at approximately or before 150 ° CA after UT (bottom dead center of a piston movement of a piston which is assigned to the cylinder) in the exhaust stroke of the cylinder.
  • the intake valve of the cylinder is open for approximately or less than 50 ° KW in the exhaust stroke of the cylinder.
  • a maximum stroke of the intake valve of the cylinder during the exhaust stroke of the cylinder is smaller than a maximum stroke of the intake valve of the cylinder during an intake stroke of the cylinder.
  • a maximum stroke of the intake valve of the cylinder during the exhaust stroke of the cylinder is less than 1/3 or less than 1/4 of a maximum stroke of the intake valve of the cylinder during an intake stroke of the cylinder.
  • a maximum stroke of the intake valve of the cylinder during the exhaust stroke of the cylinder is less than 3 mm, preferably between 1 mm and 2 mm.
  • a maximum stroke of the intake valve of the cylinder during the intake stroke of the cylinder can be around 10 mm.
  • a valve control curve of the intake valve of the cylinder is invariable and / or a valve control curve of the intake valve of the cylinder is brought about by a non-switchable and / or rigid cam of a camshaft of the internal combustion engine.
  • an actuating device preferably a valve
  • a valve is rigid and / or non-switchable for actuating the inlet valve of the cylinder.
  • a valve control curve of the intake valve of the cylinder is under low load of the internal combustion engine, such as under medium load and / or under full load of the internal combustion engine.
  • the method further comprises operating the internal combustion engine under low load during the generation of the pressure pulse, the supply of exhaust gas from the combustion chamber and / or the supply of the exhaust gas from the inlet duct.
  • the method furthermore operates the internal combustion engine in a range up to 30%, up to 35% and / or up to 40% load (partial load or% of a nominal load of the internal combustion engine) and / or in a low speed range, preferably as between 800 U / min and 1400 U / min, during the generation of the pressure pulse, the Supplying exhaust gas from the combustion chamber and / or supplying the exhaust gas from the inlet duct.
  • load partial load or% of a nominal load of the internal combustion engine
  • a low speed range preferably as between 800 U / min and 1400 U / min
  • the method for increasing an exhaust gas temperature in the exhaust line is carried out, preferably for increasing a conversion rate of an SCR catalytic converter in the exhaust line.
  • the internal combustion engine has a plurality of cylinders (for example 4, 6, 8, 10, 12 or more) and the method is used for each cylinder of the internal combustion engine.
  • the invention also relates to an internal combustion engine or a commercial vehicle (eg bus or lorry) with an internal combustion engine, which is designed to carry out a method as herein.
  • a commercial vehicle eg bus or lorry
  • FIG. 1 shows a schematic internal combustion engine that is suitable for carrying out a method according to the present disclosure
  • Figure 2 is a diagram showing various pressure values over a crankshaft angle
  • Figure 3 is a diagram showing various pressure values and valve control curves over a
  • crankshaft angle of an internal combustion engine Shows crankshaft angle of an internal combustion engine according to the present disclosure.
  • Figure 4 is a schematic flow diagram for an exemplary method according to the present disclosure.
  • FIG. 1 shows an internal combustion engine 10.
  • the internal combustion engine 10 is designed as a multi-cylinder internal combustion engine, preferably as a six-cylinder in-line engine. However, the internal combustion engine can also have more or fewer cylinders and / or another arrangement of cylinders.
  • the internal combustion engine 10 is preferably designed as a four-stroke internal combustion engine.
  • the internal combustion engine 10 can preferably be designed as a diesel internal combustion engine.
  • the internal combustion engine 10 can expediently be comprised in a motor vehicle, preferably a commercial vehicle (for example a truck or bus).
  • the exemplary internal combustion engine 10 has a first to sixth cylinder 12.
  • the cylinders 12 are operated out of phase with one another by 120 ° crankshaft angle (KW).
  • the fifth cylinder of the plurality of cylinders 12 may be out of phase with the first cylinder of the plurality of cylinders 12 by -120 ° KW, etc.
  • the exhaust stroke begins in the fifth cylinder 12
  • the first cylinder of the plurality of cylinders is located 12 already in the middle of the exhaust stroke.
  • the internal combustion engine 10 has a different number of cylinders, the cylinders are accordingly differently offset from one another in phases, for example -720 ° KW / number of cylinders.
  • the cylinders 12 each have at least one inlet duct 14, a combustion chamber 16 and at least one outlet duct 18.
  • the inlet channels 14 and the outlet channels 16 can be arranged, for example, in a cylinder head of the internal combustion engine 10.
  • the cylinders 12 also each have at least one intake valve 20 and at least one exhaust valve 22, preferably two intake valves 20 and two exhaust valves 22 per cylinder 12.
  • the intake valves 20 can be used to establish a fluid connection between the intake channels 14 and the respective combustion chamber 16 of the cylinders 12 are manufactured.
  • Using the exhaust valves 22, a fluid connection can be established between the combustion chambers 16 and the respective exhaust channels.
  • the intake valves 20 and exhaust Valves 22 can be arranged in a cylinder head of internal combustion engine 10.
  • the inlet valves 20 and the outlet valves 22 can be designed as poppet valves.
  • the internal combustion engine 10 has an exhaust line 24.
  • the exhaust line 24 is configured, for example, as a double flow, as shown, with a first exhaust manifold 26 and a second exhaust manifold 28.
  • the first exhaust manifold 26 connects the exhaust ports 18 of the first three cylinders of the plurality of cylinders 12 to an exhaust gas turbine 30 of an exhaust gas turbocharger.
  • the first exhaust manifold 26 supplies exhaust gas from the first three cylinders of the plurality of cylinders 12 to the exhaust gas turbine 30.
  • the second exhaust manifold 28 connects the other three cylinders of the plurality of cylinders 12 to the exhaust turbine 30 to supply exhaust gas to the exhaust turbine 30.
  • the exhaust line 24 can also have more or less exhaust gas flows or exhaust manifolds.
  • Those cylinders of the plurality of cylinders 12, the outlet channels 18 of which are connected directly to a common exhaust gas manifold 26 or 28, can in particular be operated out of phase by 240 ° KW.
  • An exhaust gas aftertreatment device 32 can be arranged downstream of the exhaust gas turbine 30.
  • SCR selective catalytic reduction
  • a nitrogen oxide conversion rate of the SCR catalyst device 34 can be temperature-dependent. Especially at low exhaust gas temperatures, e.g. For example, when starting the engine or during low-load operation of the internal combustion engine 10, an exhaust gas temperature may be too low for a desired nitrogen oxide conversion rate.
  • the method disclosed herein and an internal combustion engine that executes the method disclosed herein are able to raise an exhaust gas temperature during low-load operation using a pressure pulse in the exhaust system and by means of a double intake valve lift.
  • FIG. 2 shows different pressure profiles during an operating cycle of the internal combustion engine 10 in relation to one of the several cylinders 12 (hereinafter the “cylinder 12 in question”) for a low-load operating point.
  • the dash-dotted curve A corresponds to an exemplary pressure curve in the inlet channel 14 of the cylinder 12 in question.
  • the dotted curve B corresponds to an exemplary pressure curve in the respective outlet channel 18 of the cylinder 12 in question.
  • the solid curve C corresponds to an exemplary pressure curve of a cylinder pressure in the ver combustion chamber 16 of the cylinder 12 in question.
  • Curve A shows that the pressure in the inlet duct 14 of the cylinder 12 under consideration is essentially constant.
  • the pressure drops slightly when the intake valve 20 of the cylinder 12 under consideration is open in the intake stroke. In the intake stroke, charge air flows into the combustion chamber 16 of the cylinder 12 under consideration.
  • the pressure in the intake port 14 is essentially constant, with slight fluctuations, which are caused, for example, by opening and closing other intake valves 20 of other cylinders 12.
  • the pressure in the inlet duct 14 can be between 1.3 bar and 1.4 bar when the internal combustion engine 10 is operated under low load, as is shown by way of example.
  • Curve B shows that a pressure in the outlet channel 18 of the cylinder 12 under consideration fluctuates comparatively strongly during a cycle.
  • the outlet valve 22 of the cylinder 12 under consideration opens at the end of the expansion stroke, the pressure rises sharply and is gradually reduced, corresponding to a cylinder pressure curve C in this area.
  • there are further pressure pulsations in the outlet channel 18 of the cylinder 12 under consideration namely every 120 ° KW.
  • the pressure positions are caused by the opening of the exhaust valves 22 of the other cylinders 12.
  • the high pressure pulses during the compression stroke and the intake stroke are caused by those cylinders 12 which are connected to the same exhaust manifold 26 or 28 as the one under consideration Cylinder 12.
  • Curve C shows that a cylinder pressure is greatly increased during the expansion stroke.
  • a region D that the cylinder pressure increases again in the second half of the push-out cycle (exhaust cycle).
  • the reason for the increase is in the effect of the pressure pulse in the exhaust port 18 of the cylinder 12 under consideration (see curve B).
  • This pressure pulse is brought about by the opening of the outlet valve 22 of a cylinder of the several cylinders 12 which is operated in a phase-shifted manner by -120 ° KW.
  • This cylinder which is operated with a phase shift of -120 ° KW, begins its exhaust stroke in this period at the beginning of the period in which exhaust gas is pushed out through the opened exhaust valve 22.
  • the increase in cylinder pressure caused by the pressure pulse in the exhaust line 24 in the cylinder 12 under consideration can have an effect such that the cylinder pressure (curve C) rises higher than the charge air pressure (curve A) due to the pressure pulse (curve B).
  • the cylinder pressure of the cylinder 12 under consideration is higher than the boost pressure in a range of approximately 280 ° KW and 330 ° KW during the push-out cycle.
  • This knowledge can be used to convey residual gas, caused by the pressure pulse, from the combustion chamber 16 of the cylinder 12 in question into the inlet channel 14 of the cylinder 12 in question. It is proposed to open the intake valve 20 of the cylinder 12 under consideration during this phase in the exhaust stroke, in addition to the standard intake stroke during the intake stroke, as supplemented in FIG. 3.
  • FIG. 3 also shows a valve control curve of the exhaust valve 22 of the cylinder 12 in question as a dotted curve E and a valve control curve of the inlet valve 20 of the cylinder 12 in question as a dash-dotted curve F.
  • Curve E shows that the exhaust valve 22 of the cylinder 12 under consideration is open during the exhaust stroke.
  • Curve 11 shows that the intake valve 20 of the cylinder 12 under consideration performs a double stroke.
  • the intake valve 20 opens for the first time in the exhaust cycle, specifically while the pressure pulse increases the cylinder pressure in the combustion chamber 16 of the cylinder 12 under consideration via the boost pressure in the intake duct 14. Residual gas then flows through the opened inlet valve 20 into the inlet channel 14 of the cylinder 12 in question.
  • the inlet valve 20 of the cylinder 12 in question then closes before the cylinder pressure in the combustion chamber 16 of the cylinder in question falls below the boost pressure again.
  • the inlet valve 20 of the cylinder 12 under consideration then opens again normally in the intake stroke. Residual gas is flushed back from the inlet duct 14 into the combustion chamber 16 of the cylinder 21 under consideration in the intake stroke. At the same time, the fresh air mass in the combustion chamber 16 of the is reduced io
  • the residual gas purge can be used to bring about an increase in the exhaust gas temperature in the exhaust line 24 under low load of the internal combustion engine 10 in order to increase a nitrogen oxide conversion rate of the SCR catalytic converter device 34.
  • the amount of residual gas in the low-load range can be preset via the stroke length and stroke height of the inlet valve 20 during the exhaust stroke. It is possible that the additional stroke of the inlet valve 20 has an effect on the maximum possible nominal power of the internal combustion engine. Series engines generally have a clearly negative purge gradient in nominal power, i.e. that is, the exhaust gas back pressure is significantly higher than the boost pressure. This also leads to increased residual gas rates in the nominal output. Therefore, the stroke size and stroke length of the additional stroke of the intake valve 20 must be designed correctly in order not to reduce the nominal output.
  • a maximum stroke of the inlet valve 20 of the cylinder 12 in question it is proposed that this be less than 1/3 or less than 1/4 of a maximum stroke of the inlet valve 20 of the cylinder 12 in question during the intake stroke of the cylinder 12 in question during an intake stroke of the cylinder in question 12, e.g. B. around 1 mm to 2 mm, as shown.
  • the advantageous design of the additional stroke of the inlet valve 20 in the exhaust stroke means that the additional stroke can be carried out both under partial load and under full load without having a significantly negative effect under full load. This means that there is no need to provide a switchable system for selectively connecting the additional stroke of the inlet valve 20. Instead, it is sufficient if the inlet valve 20 is actuated by a robust, rigid, non-switchable cam of a camshaft, or generally driven by a rigid, non-switchable valve, which effects the same valve control curve for all load ranges.
  • the valve control curve of the intake valve 20 under the light load of the internal combustion engine 10 is identical to that under the medium load and under the full load of the internal combustion engine 10.
  • a pressure pulse is generated in the exhaust line 24 of the internal combustion engine 10.
  • the pressure pulse in the exhaust line 24 can be brought about by opening the exhaust valve 22 of one of the plurality of cylinders 12 during an exhaust stroke of this cylinder, as described with reference to FIGS. 2 and 3.
  • step S12 the pressure pulse spreads in the exhaust line 24.
  • the pressure pulse penetrates one of the several cylinders 12 into its combustion chamber 16 through an exhaust valve 22 which is already open in the exhaust stroke and increases the cylinder pressure there.
  • the cylinder pressure is increased via the boost pressure in the inlet duct 14 of the same cylinder 12 (see area D in FIGS. 2 and 3).
  • step S14 exhaust gas or residual gas is fed from the combustion chamber 16 into the inlet duct 14.
  • the supply is made possible by the additional stroke of the intake valve 20 of the cylinder during the exhaust stroke (see FIG. 3).
  • the inlet valve 20 is only opened after the cylinder pressure has been increased above the boost pressure.
  • the intake valve 20 is closed before the cylinder pressure falls below the boost pressure.
  • a method step S16 the exhaust gas is flushed back from the intake duct 14 into the combustion chamber of the cylinder 12 during the intake stroke.
  • this may increase an exhaust gas temperature in the low load to increase a nitrogen oxide conversion rate of the SCR catalyst device.
  • a different cylinder operated out of phase causes the pressure pulse in the exhaust line 24.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

L'invention concerne un procédé pour faire fonctionner un moteur à combustion interne (10). Le procédé comprend la production d'une impulsion de pression dans une ligne d'échappement (24) du moteur à combustion interne (10). Le procédé comprend l'amenée de gaz d'échappement à partir d'une chambre de combustion (16) d'un cylindre (12), pendant un temps d'échappement du cylindre (12), dans un canal d'admission (14) du cylindre (12), à la suite d'une propagation de l'impulsion de pression de la ligne d'échappement (24) dans la chambre de combustion (16) du cylindre (12). Le procédé comprend une amenée des gaz d'échappement du canal d'admission (14) du cylindre (12) dans la chambre de combustion (16) du cylindre (12) pendant une course d'admission du cylindre (12). Le procédé permet, au moyen d'une commande interne de gaz résiduaires (commande de gaz d'échappement résiduaires), de relever la température des gaz d'échappement dans la charge réduite, sans influer de manière négative sur la performance en pleine charge du moteur à combustion interne (10).
EP19765707.5A 2018-09-13 2019-09-06 Procédé pour faire fonctionner un moteur à combustion interne Pending EP3850205A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018122342.0A DE102018122342A1 (de) 2018-09-13 2018-09-13 Verfahren zum Betreiben einer Brennkraftmaschine
PCT/EP2019/073794 WO2020053081A1 (fr) 2018-09-13 2019-09-06 Procédé pour faire fonctionner un moteur à combustion interne

Publications (1)

Publication Number Publication Date
EP3850205A1 true EP3850205A1 (fr) 2021-07-21

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EP19765707.5A Pending EP3850205A1 (fr) 2018-09-13 2019-09-06 Procédé pour faire fonctionner un moteur à combustion interne

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Country Link
US (1) US11732660B2 (fr)
EP (1) EP3850205A1 (fr)
CN (1) CN112689705A (fr)
BR (1) BR112021004456A2 (fr)
DE (1) DE102018122342A1 (fr)
WO (1) WO2020053081A1 (fr)

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* Cited by examiner, † Cited by third party
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DE102022114816A1 (de) 2022-06-13 2023-12-14 Man Truck & Bus Se Brennkraftmaschine mit Stellglied zum Thermomanagement

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Publication number Publication date
US20210189979A1 (en) 2021-06-24
DE102018122342A1 (de) 2020-03-19
WO2020053081A1 (fr) 2020-03-19
CN112689705A (zh) 2021-04-20
BR112021004456A2 (pt) 2021-05-25
US11732660B2 (en) 2023-08-22

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