• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Method for operating an internal combustion engine (2) provided with at least one purged prechamber (1), wherein the at least one prechamber (1) is connected to a main combustion chamber (3) of the internal combustion engine (2) and wherein - during one of the firing in the main combustion chamber (3 ) immediately preceding the compression phase - after ignition in the prechamber (1) in a first overflow (4) gas from the prechamber (1) in the main combustion chamber (3) flows, wherein after the first overflow phase (4) an at least two-phase, incompressible medium (M) - preferably water - is introduced into the pre-chamber (1).
    公开号:AT511821A4
    申请号:T217/2012
    申请日:2012-02-21
    公开日:2013-03-15
    发明作者:Herbert Schaumberger；Hubert Dipl Ing Dr Techn Winter；Wolfgang Fimml
    申请人:Ge Jenbacher Gmbh & Co Ohg；
    IPC主号:
    专利说明:

    / 1680 70798 30 / hn 1
    The invention relates to a method for operating a provided with at least one purged combustion chamber internal combustion engine, wherein the at least one prechamber is connected to a main combustion chamber of the internal combustion engine and wherein - during a flame in the main combustion chamber immediately preceding compression phase - after ignition in the pre-chamber in a first Overflow phase Gas from the antechamber into the main combustion chamber overflowed.
    In Otto engine operated internal combustion engines, especially in gas engines, in which a propellant gas-air mixture is ignited, one uses the lean concept for larger combustion chamber volumes. This means that a relatively large excess of air is present, whereby at maximum power density and high efficiency of the engine pollutant emissions and the thermal load of the components are kept as low as possible. The ignition and combustion of very lean fuel-air mixtures represents a significant challenge for the development and operation of modern high-performance gas engines.
    From a certain size of the gas engines (usually about six liters displacement), it is necessary to use boosters to go through the correspondingly large flame paths in the combustion chambers of the cylinder in the shortest possible time. As such booster usually serve pre-chambers, wherein the highly compressed at the end of the compression stroke fuel-air mixture is ignited in a partitioned from the main combustion chamber of the cylinder relatively small side room. In this case, a main combustion chamber is bounded by the working piston, the Zyiinderiaufbuchse and the cylinder head floor, the side chamber (the antechamber) is connected by one or more overflow holes with the main combustion chamber. Frequently, such prechambers are purged or filled with propellant gas during the charge cycle phase to fatten the fuel-air mixture and thus improve the combustion and combustion properties. For this purpose, a small amount of propellant gas is diverted from the propellant gas supply to the main combustion chamber and a suitable, with a
    4BW £ check valve provided feed introduced into the antechamber. This amount of propellant flushes during the charge cycle the antechamber and is therefore often referred to as purge gas. During the compression phase, the very lean fuel-air mixture of the main combustion chamber flows through the overflow holes in the antechamber and mixes there with the purge gas. The ratio of fuel to air in the mixture is given in the form of the excess air coefficient λ. An excess air ratio of λ = 1 means that the amount of air present in the mixture exactly corresponds to the amount required to allow complete combustion of the fuel. The combustion takes place stoichiometrically in such a case. Large gas engines are usually operated lean at full load at a λ of about 1.9 to 2.0, that is, the amount of air in the mixture corresponds to about twice the stoichiometric amount of air. By flushing the antechamber with propellant results after mixing with the propellant gas-air mixture from the main combustion chamber, a mean λ in the antechamber of about 0.8 to 0.9. This results in optimal conditions of ignition and, due to the energy density, intensive ignition torches emerging into the main combustion chamber, which lead to a rapid burning through of the fuel-air mixture in the main combustion chamber. At such λ values, however, the combustion takes place at the maximum temperature level, so that the wall temperatures in the prechamber region are correspondingly high. On the one hand, this results in a correspondingly high thermal load on the pre-chamber and the components arranged therein (for example spark plug, valves) and, on the other hand, undesirably high nitrogen oxide emissions.
    From JP 07-127453 it is already known to inject water into an antechamber in order to reduce the nitrogen oxide emissions by the associated temperature reduction. The disadvantage here is that the water is injected before or during the ignition in the antechamber, whereby the performance of the prechamber is reduced as ZündVerstärker. 4% no
    The object of the invention is to provide an improved method for operating an internal combustion engine, in which the nitrogen oxides formed in the pre-chamber and formed by the prechamber are reduced. In addition, in particular, the performance of the pre-chamber as a booster should not be reduced.
    This object is achieved in that after the first overflow at least two-phase, incompressible medium-preferably water - is introduced into the pre-chamber.
    Since the formation of nitrogen oxides takes place to a good extent after the actual combustion, it is an object of the invention to lower the temperature of the burned gas. Therefore, after the ignition in the pre-chamber and possibly before the ignition in the main combustion chamber in the same combustion cycle, an at least two-phase medium, preferably in its liquid state, is introduced into the prechamber.
    Preferably, the medium is water injected into the prechamber. Due to the evaporation of the medium or of the water in the prechamber, the contents of the prechamber are cooled, resulting in less nitrogen oxides.
    The fact that the medium is introduced into the prechamber only after the first overflow phase, the performance of the prechamber is not impaired as ignition amplifier, i. The ignition in the pre-chamber and also in the main combustion chamber can take place at the conventional high temperatures and thus also with the conventional ignition energy. The fact that the medium is introduced only after the ignition in the pre-chamber, beyond only relatively small amounts of the medium are necessary to achieve a corresponding cooling and thus a corresponding reduction of nitrogen oxide emissions.
    OFF 4
    According to a preferred embodiment, it can be provided that the medium is introduced into the pre-chamber before reaching the maximum pressure in the main combustion chamber. The maximum pressure in the main combustion chamber is reached after exceeding the top dead center of a main combustion chamber limiting piston. Due to the prevailing pressure conditions in the prechamber and in the main combustion chamber during the time window between the first overflow phase and the achievement of the maximum pressure in the main combustion chamber, the introduction of the medium into the prechamber in this time window is particularly advantageous. During this time window, by the compression by means of cylinders in the main combustion chamber at least temporarily back-flowing gas is pushed from the main combustion chamber into the prechamber. It is therefore particularly favorable when gas flowing back from the main combustion chamber flows back into the prechamber in at least one second overflow phase, the medium being introduced at least temporarily during the at least one second overflow phase.
    In a structurally advantageous embodiment, it may be provided that the prechamber is connected to the main combustion chamber via an overflow channel, wherein the medium is introduced via at least one injection channel which opens into the overflow channel. As a result, the prevailing Druckverhäitnisse be exploited advantageous and automatically in each second overflow during the introduction of the medium this is automatically pushed into the antechamber.
    Combustion processes in an internal combustion engine are often controlled as a function of the crankshaft position or depending on the crank angle. Accordingly, it can be provided in an advantageous embodiment of the proposed method that the medium is introduced in a crank angle range of about 15 degrees crank angle before a top dead center of the main combustion chamber bounding piston to about 10 degrees Kurbelwinkei after the top dead center of the main combustion chamber bounding piston.
    According to a particularly preferred embodiment, it can be provided that the medium is introduced at a pressure of at least 100 bar, preferably about 200 bar, / 888 5. At high loads, cylinder pressures of about 30 bar to 70 bar may prevail in the combustion chambers (main combustion chamber and prechamber). By a correspondingly high injection pressure can be ensured that the medium can be introduced into the prechamber despite these high cylinder pressures.
    Further details and advantages of the present invention will be explained with reference to the following description of the figures. It shows or show:
    Fig. 1 Pressure curves in the prechamber and main combustion chamber one
    Internal combustion engine depending on the crank angle in the region of top dead center of a main combustion chamber bounding piston,
    2 shows an antechamber with a proposed water injection and FIG. 3 shows an enlarged view of a detail region of FIG. 2.
    Fig. 1 shows two diagrams. The upper diagram shows the course of a differential pressure ApVH as a function of the crank angle KW. The differential pressure ΔρνΗ is to be regarded as the difference between the pressure pv in the prechamber and the pressure ph in the main combustion chamber. The illustrated crank angle range KW extends over a complete compression stroke and a complete expansion stroke of a spark-ignition engine operated spark ignited gas engine, starting at bottom dead center BDC of a main combustion chamber 3 limiting piston 7 (-180 degrees crank angle KW) and also ending in bottom dead center BDC of the piston 7 ( +180 degrees crank angle KW). Plotted dashed is also the top dead center 6 (TDC) of the main combustion chamber 3 limiting piston 7 (0 degrees crank angle KW).
    The lower diagram of FIG. 1 shows the absolute pressure curves of the antechamber pressure pv and of the pressure ph in the main combustion chamber. During the area designated by the reference numeral 4 (first overflow phase 4), the ignition takes place in the prechamber 1 (eg by a spark of a spark plug), whereby the pressure pv in the prechamber 1 increases more strongly than in the compression by means of the expanding gas Piston 7 also stagnant pressure pH
    At the 6 in the main combustion chamber 3. As the differential pressure curve Δρνπ can be seen, prevails during this crank angle range 4 (first overflow 4) overpressure in the prechamber 1 with respect to the main combustion chamber 3. This causes the ignited fuel-air mixture and the resulting ignition flares of the Prechamber 1 is pressed via one or more overflow channels 8 in the main combustion chamber 3 (see Fig. 2).
    In the proposed method, after this first overflow phase 4, an at least two-phase, incompressible medium M-preferably water-is introduced into the prechamber 1 in order to cool the contents of the prechamber 1 and, accordingly, to reduce the formation of nitrogen oxides. By the prevailing pressure conditions pv, Ph in the pre-chamber 1 and the main combustion chamber 3 forms or form after the first Überströmphase 4 one or more second Überströmphasen 5, while or pushed back which G flowing back from the main combustion chamber 3 in the pre-chamber 1 becomes. These second overflow phases 5 are in particular suitable for introducing the medium M or the water into the prechamber 1, since in these second overflow phases 5 the flow of the backflowing gas G takes place in the direction of the prechamber 1. At the latest after reaching the maximum pressure Pmax in the main combustion chamber 3, however, the pressure ratios pv, Ph are such that no backflow takes place into the prechamber 1. Therefore, the most favorable range for introducing the medium M or water into the pre-chamber 1 after the end of the first overflow phase 4 and before reaching the maximum pressure Pmaxim main combustion chamber 3. This favorable injection range is marked in Fig. 1 with a dashed rectangle and provided with the reference numeral 10.
    It should be noted that the diagrams shown in FIG. 1 show the corresponding pressure curves without the proposed introduction of an at least two-phase medium M into the prechamber 1. If, according to the proposed method, a medium M or water is introduced or injected in a second overflow phase 5, the evaporation of the medium M in the prechamber 1 and the associated cooling of the prechamber contents causes the pressure pv in the tank to drop
    / IMS 7
    Prechamber 1, whereby an additional pressure gradient in the direction of the prechamber 1 is formed. The resulting pressure ratios pv, Ph thus favoring the introduction of the medium M in the antechamber 1 in addition.
    2 shows an antechamber 1 of an internal combustion engine 2. In this example, the prechamber 1 is connected via an overflow channel 8 to a main combustion chamber 3 of the internal combustion engine 2, resulting in an overall connected volume comprising the prechamber volume and the main combustion chamber volume without a valve arranged therebetween. The main combustion chamber 3 is bounded laterally in this illustration by a Zyiinderiaufbuchse 11, above the bottom of a cylinder head 12 and below by the end face of the piston 7. In the overflow channel 8 opens an injection channel 9, through which a medium M-preferably water - can be introduced or injected according to the proposed method in the pre-chamber 1. In addition, this injection channel 9 can generally also be regarded as a cooling channel for the pre-chamber 1.
    FIG. 3 shows the region of FIG. 2 marked with a circle in an enlarged view. In this illustration, the considered prechamber 1 of the internal combustion engine 2 is in a second overflow phase 5 (see FIG. 1). In this case, due to the prevailing pressure conditions pv, Ph in the prechamber 1 and in the main combustion chamber 3, backflowing gas G is pushed from the main combustion chamber 3 into the prechamber 1. During such a second overflow phase 5, the medium M or water is advantageously introduced via the injection channel 9 into the overflow channel 8, as a result of which it subsequently reaches the prechamber 1 and can there lead to a cooling of the prechamber contents. Preferably, the medium M or the water at a pressure of at least 100 bar, preferably about 200 bar, injected. In general, about 2 mm3 to about 5 mm3 of medium M or water can be introduced per combustion cycle and prechamber 1.
    At the confluence of the injection channel 9 in the overflow 8 may also be arranged a retention valve, which opens, for example, only at a pressure difference of about 10 bar to 20 bar between the pressure in the injection channel 9 «β «ν 8 and the pressure in the overflow 8 to introduce the medium M or the water in the overflow 8. It can also be provided that a nozzle is arranged at the junction of the injection channel 9 in the overflow 8, through which the medium M or the water can be injected into the overflow 8. By introducing the medium M or of the water into the overflow channel 8, the introduction of burned gases from the main combustion chamber 3 into the prechamber 1 can additionally be reduced. As a result of the evaporation of the medium M, an evaporation cushion can form in the overflow channel 8 which, as a barrier, opposes the backflowing gas from the main combustion chamber 3. This leads to a further reduction of nitrogen oxide formation.
    Innsbruck, on February 20, 2012
    权利要求:
    Claims (7)
    [1]
    4m 70798 30/30 1 Claims 1. A method for operating an internal combustion engine (2) provided with at least one purged prechamber (1), the at least one prechamber (1) being connected to a main combustion chamber (3) of the internal combustion engine (2) and wherein - during a flame in the main combustion chamber (3) immediately preceding compression phase - after ignition in the prechamber (1) in a first Überströmphase (4) gas flows from the prechamber (1) in the main combustion chamber (3), characterized in that after the first overflow phase (4) an at least two-phase, incompressible medium (M) - preferably water - is introduced into the prechamber (1).
    [2]
    2. The method according to claim 1, characterized in that the medium (M) is injected into the pre-chamber (1).
    [3]
    3. The method according to claim 1 or 2, characterized in that the medium (M) before reaching the maximum pressure pmax in the main combustion chamber (3) is introduced into the prechamber (1).
    [4]
    4. The method according to any one of claims 1 to 3, characterized in that in at least a second overflow phase (5) back-flowing gas (G) from the main combustion chamber (3) flows back into the pre-chamber (1), wherein the medium (M) at least temporarily during the at least one second overflow phase (5) is introduced.
    [5]
    5. The method according to any one of claims 1 to 4, characterized in that the medium (M) in a crank angle range of about 15 degrees crank angle (KW) before a top dead center (6) of the main combustion chamber (3) limiting piston (7) to about 10 degrees crank angle (KW) after top dead center (6) of the main combustion chamber (3) limiting piston (7) is introduced. 2
    [6]
    6. The method according to any one of claims 1 to 5, characterized in that the pre-chamber (1) with the main combustion chamber (3) via an overflow channel (8) is connected, wherein the medium (M) via at least one in the overflow channel (8). merging injection channel (9) is introduced.
    [7]
    7. The method according to any one of claims 1 to 6, characterized in that the medium (M) with a pressure of at least 100 bar, preferably about 200 bar, is introduced. Innsbruck, on February 20, 2012
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    引用文献:
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    法律状态:
    2021-10-15| MM01| Lapse because of not paying annual fees|Effective date: 20210221 |
    优先权:
    申请号 | 申请日 | 专利标题
    ATA217/2012A|AT511821B1|2012-02-21|2012-02-21|Method for operating an internal combustion engine provided with at least one purged prechamber|ATA217/2012A| AT511821B1|2012-02-21|2012-02-21|Method for operating an internal combustion engine provided with at least one purged prechamber|
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    US13/771,540| US9644527B2|2012-02-21|2013-02-20|Method of operating a combustion engine provided with at least one flushed prechamber|
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