Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
  • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
  • F02D19/0602—Control of components of the fuel supply system
  • F02D19/0613—Switch-over from one fuel to another
  • F02D19/0615—Switch-over from one fuel to another being initiated by automatic means, e.g. based on engine or vehicle operating conditions
• • 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
  • F02B3/00—Engines characterised by air compression and subsequent fuel addition
  • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
  • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
  • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
  • F02D19/0602—Control of components of the fuel supply system
  • F02D19/0613—Switch-over from one fuel to another
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
  • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
  • F02D19/0639—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels
  • F02D19/0642—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed characterised by the type of fuels at least one fuel being gaseous, the other fuels being gaseous or liquid at standard conditions
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02D—CONTROLLING COMBUSTION ENGINES
  • F02D19/00—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
  • F02D19/06—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed
  • F02D19/08—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels
  • F02D19/10—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels peculiar to compression-ignition engines in which the main fuel is gaseous
  • F02D19/105—Controlling engines characterised by their use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures peculiar to engines working with pluralities of fuels, e.g. alternatively with light and heavy fuel oil, other than engines indifferent to the fuel consumed simultaneously using pluralities of fuels peculiar to compression-ignition engines in which the main fuel is gaseous operating in a special mode, e.g. in a liquid fuel only mode for starting
• • 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
• • 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
  • F02D41/008—Controlling each cylinder individually
• • 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
  • F02D41/30—Controlling fuel injection
  • F02D41/3094—Controlling fuel injection the fuel injection being effected by at least two different injectors, e.g. one in the intake manifold and one in the cylinder
• • 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
  • F02D2200/04—Engine intake system parameters
  • F02D2200/0406—Intake manifold pressure
• • 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
  • Y02T10/30—Use of alternative fuels, e.g. biofuels

Definitions

• the invention relates to a method for operating a dual-fuel internal combustion engine with a gas mixer, a suction line and an engine with a number of cylinders and with an injection system, wherein the dual-fuel internal combustion engine in a first operating condition in diesel mode with diesel and in a second operating state is operated in gas mode with gas as fuel.
• the invention further relates to a control for the dual-fuel internal combustion engine according to the preamble of claim 19 and a dual-fuel internal combustion engine according to the preamble of claim 21.
• the dual-fuel internal combustion engine preferably has in the intake but not necessarily further Charging and a bypass range to bypass the charge.
• This type of dual-fuel internal combustion engines are also referred to as multi-fuel internal combustion engines and can be operated in addition to the preferred fuel choice of diesel and gas with a variety of other fuels.
• a dual-fuel internal combustion engine is operated depending on the availability of a fuel with one or the other fuel.
• a dual-fuel internal combustion engine in Zündstrahl aus according to the diesel method with external mixture formation of a gas mixture and preferably a diesel jet are operated.
• engines of the dual-fuel internal combustion engine are regularly built on the basis of a diesel engine design and are among the latest technologies, especially in the field of environmentally sound applications of large engines.
• the aforementioned type of internal combustion engine may in particular also comprise a so-called high-pressure gas engine with internal mixture formation, which can deliver a comparatively high specific cylinder power by means of gas injection in ranges of above 200 bar in conjunction with a diesel jet.
• the priming motor can also handle liquid fuel such as diesel or other liquefied fuel such as liquefied natural gas (LNG) or liquefied natural gas (LTG).
• LNG liquefied natural gas
• LTG liquefied natural gas
• a dual-fuel internal combustion engine may therefore preferably have a gas-diesel engine for forming a gas-diesel internal combustion engine.
• a central mixture formation for example by means of a gas mixer, for the gas operation.
• a gas operation is in the foreground, in which a mixture formation takes place in a cylinder-specific manner, preferably directly in front of a cylinder.
• Each cylinder may be assigned a separate gas injector valve, which is controlled individually for each cylinder.
• the control can be done in coordination with the cycle of a number of cylinders.
• a priming jet of liquid fuel can preferably be used to ignite the fuel gas mixture in the cylinder; In principle, spark-ignited gas operation can also be provided.
• a dual-fuel internal combustion engine may preferably have an injection system, which can preferably be controlled electronically and for different gas qualities, such as biogas or natural gas, in liquid form or for the use of oils such as vegetable oils or the like as a liquid fuel.
• gas qualities such as biogas or natural gas
• oils such as vegetable oils or the like as a liquid fuel.
• common-rail injection systems but possibly also pump-nozzle injection systems with electronic control, have proved their worth here.
• the ignition medium in the gas mode can be added to the actual gaseous fuel of the charge mixture as explained in the cylinder at high compression or can be added to the intake duct.
• the dual-fuel engines operating in gas mode, in particular ignition-jet mode, according to the diesel process with external mixture formation (ie mixture formation outside the cylinder) are more flexible overall in fuel use and still have lower emissions.
• EP 2 069 627 B1 shows a dual-fuel internal combustion engine of general type with a proportioning system for adapting a flow of liquefied gas and diesel, wherein excess fuel mixtures are collected and recycled to a mixing chamber for further combustion in a combustion chamber of the engine.
• US 6,131,552 generally discloses a fuel control system which can control the delivery of gas to a mixing chamber in response to a measured operating condition of the engine.
• an air effort is a measure of the supplied to an internal combustion engine gaseous fresh charge charge air in a charge mixture
• the air consumption also allows a statement about the quality of the intake system and process.
• the actual air expenditure regularly represents the ratio of the actual mass of fresh air in a charge mixture supplied to the engine or a cylinder thereof during a working cycle.
• This real mixture mass is related to the theoretical fresh charge mass, determined from the geometric displacement and the theoretical charge density Ambient conditions (with naturally aspirated engines) or with supercharged engines, the state of the fresh charge behind the compressor or behind the intercooler is taken into account here.
• Fresh charge supplied to the cylinder exerts a number of factors, such as the valve timing or the opening area of the valves. In principle, this can be determined from a module for determining the engine charge, to which an intake route model is deposited. In fact, however, the fresh charge supplied to the engine in a charge mixture only corresponds to the theoretical one in exceptional cases.
• the air consumption is not a constant number for an engine, but is highly dependent on the speed and the present geometric relationships of intake and combustion chamber; To cope with this dependency z. B. find a suitable map.
• Ansaugfflenmodelle However, in engine regulators basically only in general internal combustion engines, such as. B. from EP 1 398 490 A2, known.
• the storage behavior of the intake also referred to as intake manifold, via the filling and emptying method is modeled.
• the suction tube is treated as a pressure vessel, the is continuously filled with air by a throttle and from which the engine sucked through its suction behavior according to the power stroke via the inlet valve air.
• the mixture formation can take place before the compressor of the exhaust gas turbocharging and / or cylinder-individually before a cylinder as explained.
• the intake path between the compressor outlet and the combustion chamber inlet consists of partially large volumes, which are therefore significant charge fluid masses, ie. H. in particular mixture masses or even only charge air masses, store or release. This is especially true when it comes to load and / or speed changes of the engine to pressure and / or temperature changes in the individual sub-volumes.
• a fuel supply to a dual-fuel internal combustion engine especially in the transient operating range of the internal combustion engine and variable fuel qualities, and / or a reliable indication of state parameters of a charging fluid in the intake is quite complex.
• dual-fuel internal combustion engines in particular for the formation of a Zündstrahlmotors that the operation in the low load range can be problematic.
• the invention begins, whose object is to provide a method and a device by means of which an improved operation of an internal combustion engine is achieved as a dual-fuel internal combustion engine, in particular for a low load range.
• a low-load range problem of a fuel composition is to be solved in an improved manner, in particular under Avoidance of torque jumps of a motor in further transient operation.
• a transition is to be made available between a diesel operation and a gas operation, preferably from a diesel operation to a gas operation.
• the object of the invention is also to address at least one of the problems described above. At least an alternative solution should be proposed.
• the engine is operated in a first operating state in diesel mode with diesel or other liquid fuel and in a second operating state in gas mode with gas (BG) as fuel in a charge mixture.
• BG gas
• switching between the diesel operation and the gas operation is effected at a switching range which is determined in particular by a switching operating parameter, in particular a predetermined one.
• a predetermined switching range may be determined by predetermined values of a switching operating parameter, i. H. a switching value for an operating parameter of the internal combustion engine, be set.
• a predetermined value of a switching operation parameter may be a DESIRED value or ACTUAL value or a virtual value.
• it may be a switching point; that is, exactly one value of the switching operating parameter (s).
• the invention is based on the consideration that there are several fundamental challenges for increasing the load in the gas engine, in particular in the ignition jet gas engine, from the no-load or low-load range; but which are solved with the concept of the invention in a superior manner.
• the invention is based on the consideration that at low engine loads very low (intake air) pressures would have to be driven in front of a cylinder, as long as the setpoint (gas) ) Combustion air ratios should not exceed a certain value (eg 2 ... 2.5) in order to achieve an improvement in the emission range.
• a certain value eg 2 ... 2.5
• the invention is based on the consideration that without throttling the intake air at low engine loads in gas operation, especially in Zündstrahl strict, very large (gas) combustion air conditions would have to be driven, in which then a secure ignition, in particular a reliable ignition with would be achievable, but the gas would no longer burn completely as fuel in a charge mixture and therefore would cause high HC emissions.
• the invention therefore provides to make an increase in the diesel injection amount in pure diesel mode.
• the problems described above do not occur.
• the change from a pure diesel operation into the gas operation, in particular ignition jet operation can be problematic, especially in the start-up or other transient operating range.
• This also applies in principle to the reverse transition from gas operation, in particular ignition jet operation, to diesel operation. There may be torque jumps when switching from gas fuel to liquid fuel, especially diesel fuel, or vice versa, does not meet the loads and other operating requirements of the engine.
• the concept of the invention advantageously uses the transition between a diesel operation and a gas operation, in particular in a range of small engine loads.
• the diesel operation (DB) and the gas operation (ZB) are switched over at a changeover range determined by switching operating parameters, in particular predetermined.
• the switching relates to such from the diesel operation in the Zündstrahl congress and opposite to a Zündstrahl gas engine.
• the concept forms the basis that the transition is a more uniform and preferably also with changing load requirements and possibly avoiding excessive emissions can be achieved.
• the switchability of both diesel (ignition jet) injection and gas metering is performed individually for each cylinder.
• a cylinder-specific gas metering proves a Ansaugsharenmodell (as in the conventional gas engine with a mixture formation before compressor) as less necessary; although this may be advantageous for reliable indication of state parameters of a charging fluid in the intake
• an internal combustion engine may include an intake passage and an engine having a number of cylinders.
• the intake section could have a gas mixer.
• an injection system which is advantageously designed as a common-rail injection system, has proved to be advantageous for providing an ignition jet.
• the internal combustion engine preferably has a charge with a charging heat exchanger and with a bypass path for bypassing the charge, wherein the charge has a compressor.
• a bypass section of the intake section can also be provided as part of an intake system in order to bypass the charge.
• a charge can be one or two stages, preferably provided with a Abgasriick entry.
• the compressor may be designed as a one or two-stage compressor, in particular in the context of a turbocharger.
• An advantageous development is based on the consideration that an advantageous transient operation of a dual-fuel internal combustion engine, especially when switching between gas operation and diesel operation, possibly taking into account a state pressure of the charge mixture in the intake, in particular taking into account a throttling of the charge mixture, ie the Charge air or the fuel mixture, should take place.
• the further development has recognized that it may be necessary to specify a changeover operating parameter at least in the form of a state pressure of the charge mixture in the intake route.
• the development has also recognized that it is in principle possible to set the switching range based on a state pressure of the charge mixture in the intake, in particular a receiver pressure immediately in front of a cylinder of the engine, in particular to predetermine. It turns out that a change of operating modes, ie. H. a change between gas operation and diesel operation or generally between gas operation and liquid operation of the dual-fuel internal combustion engine, according to the concept of development depending on a state pressure of the charge mixture in the intake, in particular the boost pressure and / or the receiver pressure
• At least one of the switching operating parameters provides a state pressure of the charge mixture in the intake section is a cylinder of the engine, in particular a desired value of a state pressure of the charge mixture is.
• the actual value of a state pressure of the charge mixture can also be used. If necessary. It is also possible to use an averaged ACTUAL or DESIRED value. In certain cases, it may also prove appropriate to use a virtual value of a state pressure of the charge mixture.
• the value of the state pressure may be a minimum value of the state pressure in a certain period of time or otherwise determined.
• the state pressure or other switching operating parameters are determined virtually, for example, simulated and / or calculated; in particular in real time and / or simultaneously for a first and a second operating state.
• the first operating state is a diesel operation with diesel.
• the second operating state can be a gas operation with gas as fuel, in particular in the ignition jet mode.
• diesel mode-according to a preferred development ie primarily for small loads-a pressure or other operating parameter calculation, in particular a DESIRED pressure calculation for a pressure in front of a cylinder during ignition-jet operation, should run in parallel with a pressure or other operating-parameter calculation in diesel operation.
• a pressure or other operating-parameter calculation in diesel operation it can be advantageously achieved that when the (target) pressure necessary for the ignition jet operation has reached the current (actual pressure) (in particular without throttling the intake air in diesel operation) or a pressure specified as minimum (in particular with throttling in diesel operation ), is switched from the diesel operation to the ignition jet operation or other gas operation. Similarly, this may apply to the reverse direction.
• a Umschalt istsparameters in the form of a state pressure of the intake manifold, throttles and in particular actuators thereof, to influence the state pressure such as a throttle valve, a throttle valve or other throttle organs provide.
• any means for reducing the pressure is considered as a throttle member of the intake path; to this end, in addition to an engine throttle, it may also include a compressor bypass throttle.
• a motor throttle and a valve a flap or a throttle or a variable turbine geometry of a compressor.
• An angle of attack ⁇ between fully open and fully closed position is generally used here to describe a throttle position; It can also be used in combination several throttle organs of the aforementioned type.
• an engine throttle may be provided upstream of the receiver volume and / or a compressor bypass throttle in the bypass path. It can, in particular depending on a desired and / or actual state pressure of the intake line, a throttling of the intake, in particular for throttling the engine and / or the bypass route are made.
• An optional throttling in diesel operation would be advantageous only when reaching the minimum pressure, in order not to have permanent consumption disadvantages in diesel operation, since throttling usually also brings any consumption disadvantage.
• the primary goal of the optional throttling would thus be, in particular, the enlargement of the operating map area in which ignition-firing operation would be possible. It also shows that, in particular, throttling in the diesel mode before a switching operation can lead to a comparatively smooth switching operation without torque jump and / or under reduced HC emission.
• a throttle body, in particular of the aforementioned type according to a development in the diesel engine in the direction of the closed position moves, which leads to a switching operation for reducing the state pressure, especially when switching from diesel operation to a Zündstrahlconce.
• throttling in diesel mode can also be restricted to the switching process for switching to gas operation.
• a reduction of a compression pressure (in the drawing p2) after the compressor and / or a suction pressure (pl in the drawing) can be used in front of the compressor.
• the throttle body takes advantage of a Part of the load control of the motor For example, after the switching operation, the throttle organ can be opened further.
• a first switching point from diesel operation to gas operation is a different value than a second switching point from a gas operation to diesel operation.
• a hysteresis for the switching range can be defined according to the concept. This leads to a comparatively soft switching capacity of the dual-fuel internal combustion engine, in which torque jumps are avoided in an improved manner.
• DB diesel operation
• ZS ignition jet operation
• ZB gas operation
• the first switching point is from diesel operation to gas operation with a higher value above a value for the second switching point from a gas operation to diesel operation. It turns out that it is fundamentally advantageous to carry out a first switching point from diesel operation to gas operation when the engine is throttled, in particular by means of an engine throttle, and / or with a throttled intake route, in particular by means of a compressor bypass throttle and / or intake throttle.
• an engine throttle arranged directly upstream of the receiver volume can preferably be moved in the direction of a closed position before switching over.
• different switching points can be specified as limits of the switching range, at least by means of determining the state pressure of the intake path for switching over.
• the pressure before a cylinder should be lower for a downshift from ignition jet operation (ZB) to diesel operation (DB) than in the case of reverse switching.
• ZB ignition jet operation
• DB diesel operation
• ZS ignition jet operation
• ZB gas operation
• DB diesel operation
• a switching operating parameter of a state pressure of the intake section to be switched on the condition that the state pressure of the Diesel operation is equal to or above the state pressure, in particular nominal state pressure, the gas operation.
• an advantageous condition is that a virtually determined value and / or actual value of the state pressure in diesel mode is equal to or above a virtually determined and / or set value of the state pressure of the gas operation.
• a change of the operating mode is advantageously carried out when a setpoint for the pressure before cylinder is exceeded during the transition from diesel to ignition jet operation, or falls below a setpoint for the pressure before cylinder during the transition from Zündstrahl- to diesel operation.
• a shift in the switching thresholds for the change in the ignition jet operation toward lower loads can be achieved by an at least short-term throttling of the pressure upstream of the cylinder in diesel operation.
• a switching of the operating mode from diesel to ignition jet operation takes place in particular if the setpoint pressure for the ignition jet operation corresponds to the current charge air pressure in front of the cylinder.
• the dual-fuel internal combustion engine can be controlled and / or adjusted from a throttled actual state of the diesel operation to a desired state of the gas operation to be triggered; in particular in addition due to the formulated according to this development condition for a switching area.
• hysteresis can be defined by specifying a limit value for a difference between actual value and nominal value of a state pressure for the switching range, preferably depending on the reversing direction for the ignition jet operation when switching to ignition jet operation or for diesel operation when switching to diesel operation ,
• a number of cylinders upstream of the cylinders to a receiver volume which, for example, can take into account, in particular, the volume of a manifold or a mixing section or the like after an engine throttle.
• the dual-fuel internal combustion engine with a charge in the intake path of an intake system, in particular with a charge comprising a charging heat exchanger.
• a charge comprising a charging heat exchanger.
• assign the charge heat exchanger in the intake a heat exchanger volume, which can consider, for example, especially the volume of the charge heat exchanger or other volumes of the intake before a throttle engine.
• the state pressure is determined in front of a cylinder of the engine, preferably as a receiver pressure in a receiver volume.
• a receiver volume is to be understood in general as any type of volume which is upstream of the cylinder in the upstream direction and downstream of a supercharging and / or a bypass line in the downstream direction, in particular an engine throttle.
• a receiver volume may be the volume of a manifold or any other expansion of the space of the charge path.
• a volume of a receiver is to be understood as meaning a volume which exceeds the usual volumes of a charging path; It is shown in the context of the development that the specification of the receiver pressure in the receiver volume is particularly significant for the reliable control of the dual-fuel internal combustion engine, because an increasing uncertainty in the state of the fuel gas mixture is linked with increasing size of a receiver volume. A regulation of the receiver pressure in the receiver volume thus eliminates imponderables that exist in stationary assumptions about a charging path.
• each cylinder of the engine has proved to be advantageous for each cylinder of the engine to be switched individually between the diesel mode and the gas mode at a switching range determined by a switchover operating parameter, in particular a predetermined one.
• a switchover operating parameter in particular a predetermined one.
• the further development is based on the knowledge that a changeover, in particular in a start region of a working cycle of a cylinder, is advantageous; inasmuch as an individual change-over of the entire engine has to follow the sequential sequence of the starting ranges of the working cycles of the number of cylinders.
• cylinder-individual can be switched from one cycle to the next and at the beginning of each cycle for each cylinder in turn (in firing order).
• a switching range is not necessarily limited to a one-dimensional range or a single point of a condition pressure of the intake stroke, but may rather include a map of variable and / or fixed switching points.
• a variable and fixed switching operating parameter is to be understood as a desired value of the same, which is variably selectable and then fixed.
• the variable and / or fixed switching points of the switching range can be defined by variable and / or fixed switching operating parameters, comprising at least one state pressure or, advantageously, in particular to form a hysteresis region, a state pressure range.
• Further switching operation parameters may advantageously be selected from the group of operating parameters comprising: engine speed, maximum combustion air ratio, proportion of a liquid fuel, in particular diesel fuel mass to the total fuel mass in Zündstrahlconce, an at least required or useful state pressure of the intake in diesel mode, in particular the receiver pressure in the receiver volume.
• a state pressure can also serve as the basis for a complex-formed state pressure variable; this can be, for example, a first state pressure in the form of a nominal state pressure and / or a second state pressure in the form of an actual state pressure.
• a state pressure variable may be formed as a combination of the first and second state pressure, possibly taking into account further state pressures of the intake path or of the intake system, for example a combination of a receiver pressure and a boost pressure (in the drawings p5 and p3).
• a switching operating parameter can be formed on the basis of a difference of the first and second state pressure of the intake section, in particular a difference between a setpoint and actual value of the same state pressure and / or a difference between a state pressure before and after a throttle element.
• the difference of a state pressure before and after an engine throttle, in particular receiver pressure and boost pressure (in the drawings p5 and p3) can be taken into account as first and second state pressure.
• first and second state pressure are taken into account as first and second state pressure.
• a control performance of a scheme can be significantly improved.
• a scheme can be interpreted more flexibly, for example, by a difference of First and second state pressure of a setpoint and actual value, a hysteresis for the switching range is defined.
• the state pressure is determined virtually, for example, simulated and / or calculated.
• a suitable calculation model of the charging system in particular comprising the intake route, can be used. It has been found in a particularly preferred development that the calculation model should include at least two computational volumes, which make up the largest volume ranges of the charging path. This relates in particular to the computing volume of a receiver volume such as a manifold on the engine and / or the computing volume of a charge heat exchanger. Taking into account these comparatively large volumes eliminates dynamic and beyond the stationary area adjusting gas mixture conditions in a receiver volume and / or charge heat exchanger volume can be considered.
• the first operating state is a pure diesel operation only with diesel.
• a virtually determined operating parameter of the first operating state can be determined in a control mode provided for the first operating state by means of a map arrangement assigned to the pure diesel operation. This applies in particular to a virtually determined state pressure, be it as setpoint or actual state pressure, in particular in the receiver volume (p5). This also applies, if necessary, to virtual certain other operating parameters such as temperature and expansion volume (eg a temperature T5 in the receiver volume V5 assigned to the receiver pressure p5).
• the second operating state can be a pure gas operation with gas as fuel.
• a Zündstrahl foi according to the diesel method with external mixture formation of a gas-air mixture to understand a diesel jet.
• a virtually determined operating parameter of the second operating state can be determined, ie simulated and / or calculated.
• the operating parameter is in a control mode provided for the second operating state determined by means of a pure gas operation associated map array.
• a gas state of the receiver volume and / or the charge heat exchanger volume p5, T5, V5 or p3, T3, V3 can be determined for the pure gas operation.
• the aforementioned first and / or second variant may make the measurement of an operating parameter, in particular a condition pressure in the intake path, in particular receiver volume and / or charge heat exchanger volume (possibly costly or impossible or possibly unsafe) unnecessary. It can also be the proper determination and use of a target and / or actual value of an operating parameter allows, in particular a state pressure in addition to or as an alternative to a measured value.
• a target and / or actual value of an operating parameter allows, in particular a state pressure in addition to or as an alternative to a measured value.
• it is provided to virtually determine the gas operation and the diesel operation in parallel and / or in real time in addition to the real operation of the dual-fuel internal combustion engine, in particular to calculate and / or simulate the intake route on the basis of the computing model.
• the calculation model discussed within the scope of an aforementioned development can advantageously be used with a calculation volume of the receiver volume and / or the charge heat exchanger in order to enable reliable predictions of the virtual operating states of a dual-fuel internal combustion engine in pure diesel operation or in pure gas operation
• the operating state comprises at least one first, in particular virtually determined, operating parameter of the first operating state and / or the second operating state comprises at least one second, in particular, virtually determined operating parameter of the second operating state.
• the first and / or second operating parameter is a state pressure of the intake path, in particular a state pressure immediately before a cylinder of the engine, in particular a receiver pressure in the receiver volume of the engine.
• the first and the second operating parameters are available in parallel and / or in real time.
• a state pressure of the intake such that a combustion air ratio (here LAMBDA GAS value) of the gas mixture below a threshold value, for. B. less than 2.5, in particular less than 2.0.
• a combustion air ratio here LAMBDA GAS value
• Fig. 1 is a diagram of a dual-fuel internal combustion engine with an intake with a
• FIG. 2 shows in a diagram for engine speed and engine torque exemplary registered operating state ranges of a diesel operation (DB) and a gas operation (ZB), in particular Zündstrahl ists (ZS), the Zündstrahl ist presently for a LAMBDA GAS value in the range between 1.5 .. 2 and the diesel operation for a LAMBDA diesel value in the range between 3 .. 7 takes place; the values in brackets correspond to alternative modes of operation (ie diesel instead of gas at the top and gas instead of diesel at the bottom);
• Fig. 3 in view (A) is a schematic and in the context of a module 200 for a
• FIG. 4 shows a transient curve of an engine torque Md SOLL as a desired value over time and the associated receiver pressure p5 in the diesel mode (DB) for the receiver volume 81, FIG.
• Fig. 5 is a schematic representation of a structure for a regulator part 300 of a regulator for the
• FIG. 6 is a schematic diagram of a structure for a regulator part 400 of a regulator for the
• FIG. 7 shows a module 420 for the regulator part 400 of a regulator for the gas operation, in particular
• FIG. 1 shows a multi-fuel internal combustion engine, also referred to as a dual-fuel internal combustion engine 100, with an engine 10, an injection system 20, and an intake system with a branched intake passage 30.
• a turbocharger 50 and a charging heat exchanger 60 here in the form of a charge air cooler, and a bypass 70 arranged.
• the engine is provided with a cylinder-specific gas metering 40 for fuel gas BG.
• the injection system 20 is designed to portion liquid fuel such as diesel or other liquefied or liquid fuel to this in a diesel operation as a liquid fuel or in a gas or Zündstrahl operation as ignition at the beginning of a cycle of a cylinder Ai, Bi inject; this at very high injection pressures.
• charge air LL is sucked from the environment.
• the charging fluid or mixture also referred to as fuel gas / air mixture in gas operation with central gas mixing via a gas mixer
• the charging fluid or mixture -in the following short-term mixture G ⁇ with mass flow rate m (') _ G is combined with the intake pressure pl and at an intake temperature Tl, which in the substantially corresponds to the ambient temperature, supplied via a compressor section 32 to a compressor 51 of the turbocharger 50 and there compressed to a compression pressure p2 at a compression temperature T2.
• the compressor 51 is driven by a turbine 52 and sits with this on a common loader axle 53; the turbine 52 of the exhaust system 90 in turn is driven by the engine 10 leaving exhaust AG in the exhaust line 90.
• the mass flow m (') _ G of the mixture G heated as a result of the compression to the compression temperature T2 is fed to a cooling section 31 of the intake section 30 and conducted there in a charging heat exchanger 60 via a cooler structure 61; in the heat exchanger volume 62 symbolically represented here, a heat exchange with a cooling medium takes place in the cooler structure 61, so that the mixture G is cooled.
• the fuel gas mixture leaves the heat exchanger volume of size V3 in cooled form at a charging temperature T3 and a boost pressure p3 in the direction of a charging path 33 for supplying the mixture G to the engine 10.
• a Ansaugstartnmodell the state of the mixture G before the compressor 51 comparatively generally by means of State variables for pressure and temperature indicated, here suction temperature Tl and suction pressure pl in front of the compressor 51, and after the compressor 51 at increased compression pressure p2 and increased compression temperature T2 with the state variables p2, T2 after the compressor 51 are described by means of a suitable compressor model; this, for example, according to a gas state equation, such. B. for an ideal or real gas.
• a heat exchanger volume V3 or a receiver volume V5 is assigned in Ansaugreheatnmodell. Accordingly, this assumes the fuel gas mixture G in the heat exchanger volume V3, the state variables p3, T3, this as a result of cooling and an increase in volume with decreasing charge pressure and charging temperature p3, T3.
• the state of the mixture G in the bypass 70 is basically also determined in accordance with the state variables pl, Tl input or p3, T3 output of the bypass 70 or vice versa in the case of a backflow through the bypass 90; d. H. a bypass gas mixture G BP in the bypass section 71 of the bypass 70 adjusts itself in dependence on the prevailing pressure conditions and the position of the compressor bypass throttle 72 -here according to the setting angle aVBP of the compressor bypass flap.
• the bypass line 71 can be used, in particular, for returning excess mixture G upstream of the compressor 51, in order to feed it again in a compressed state for combustion in the cylinders Ai, Bi of the engine 10.
• the engine throttle 82 in the present case is formed via first and second engine throttle valves 82 B, 82 A, which are respectively associated with the first and second receiver volumes 81 B, 8 LA, the first and second engine throttle valves 82. B, 82.A are independently adjustable; in the following though summarily described under the motor throttle 82.
• the receiver volume 81 is to be understood as the sum of the first and second receiver volumes 81.A and 81B.
• the mixture G in the volume V5 of the receiver volume 81 assumes the gas states indicated by p5 and T5; depending on the B-side or A-side mass flow rate m (') _ DK, B or m (') _ DK, A depending on the position of the engine throttle 82. B and 82.A.
• receiver pressure p5 in the receiver volume V5 or for the control variables based on the receiver pressure p5-such as an actual receiver pressure p5_IST or a target receiver pressure p5_SOLL or a simulated receiver pressure p5 ⁇ a central role to determine a switching range for Dual-fuel internal combustion engine 100 result; Namely, on the one hand in a diesel operation-without admixture of gas BG on the cylinder-individual gas metering 40- or in a gas operation with the addition of gas BG via the cylinder-individual gas metering 40 and a firing via the injection system 20th
• Boundary conditions for a simulation of the dual-fuel internal combustion engine and for the online determination of the virtual values of p5 and p3 in diesel operation on the one hand and the gas operation on the other hand may be beyond u. a .:
• z For example, to describe the states of a charge air, in a Ansaugumblenmodell, as described with reference to FIG. 1, at least two large volumes are summarized to summarize the volume of the intake, namely the receiver volume 80 and the charge heat exchanger volume 62.
• the intake 30 can within the Ansaugumblenmodells based on the filling and emptying method, as it is known in principle, modeled.
• the state changes in the volumes can be regarded as quasi-isothermal in the present case. This simplifies the system by limiting it to mass conservation as opposed to the adiabatic approach and, in particular, simplifies a simultaneous calculation of the internal combustion engine or the intake path of the same in real time.
• FIG. 2 shows, in a coordinate system about the engine speed nMOT and the engine torque Md, two different operating ranges, namely once for the diesel operation DB and once for the ignition jet operation ZB, which are defined by preferred combustion air ratios LAMBDA.
• the limits result by establishing, in particular by emission standards, recommended ranges of combustion air conditions. These are indicated by ranges of corresponding LAMBDA values LAMBDA BG (fuel gas) and LAMBDA_ DL (diesel).
• LAMBDA BG fuel gas
• LAMBDA_ DL diesel
• the preferred Diesel operation DB at low load is preferably LAMBDA-DL between 3 .. 7 (LAMBDA-BG between 1.5 and 2).
• the emissions -HC emissions, particulate emissions or the like (NOx, CO, CO 2) of the dual-fuel internal combustion engine 100 are comparatively small and, moreover, a transition of the operation mode as much as possible can be made without torque jumps.
• a transition between operating points A, B or a transition between operating points A ', B' could be solved by the fact that in the diesel operation DB-especially in the low load range, the regularly in the starting range of the internal combustion engine present- the charge air LL fuel gas BG in possibly very small amounts is added.
• an ignition jet operation with LAMBDA ZB values below 2.5, but in any case LAMBDA ZB below 2, preferably in the range between 1.5 and 2, is desirable.
• a first varied approach to make an operating state transition possible without torque jump and / or low emissions can basically be to provide the internal combustion engine with an injection system, which is designed to implement the Zündstrahlvons and also capable of a continuous injection or multiple injection (multi -point injection, MPI) in any case as an option to a single injection (single-point injection, SPI) implement.
• MPI multi -point injection
• SPI single-point injection
• a fuel injection to form a firing be made, for example, a diesel injection or other liquid fuel injection.
• a certain part number of cylinders for example two cylinders A1, A2 or A3, A4 or A5, A6 or ⁇ , A8-- can also be combined into one subgroup and one injection provided for each subgroup instead of one individual Cylinder.
• a priming injection can be carried out sequentially, ie a sequential sequence of injections for a number of cylinders individually one after the other or for a number of groups of cylinders are carried out one after the other.
• the sequence of injections is such that is injected for each cylinder at the beginning or in a start region of a working cycle. This procedure results in a better control of the LAMBDA value over a combustion cycle of the entire engine or an individual working cycle of the respective cylinder.
• a multiple injection per cylinder can be carried out.
• such or similar approach may be advantageous over simultaneous injection for all cylinders or against central injection on one manifold for all cylinders.
• the multiple injection proves to be useful in particular as a direct injection into the cylinder chamber in combination with the common rail system of an injection system 10 shown in Fig. 1.
• the engine of the dual-fuel internal combustion engine is throttled in the event of an operating state transition which is in the vicinity of a switching region.
• a throttle member in an intake section 30, in particular here an engine throttle 82 in a charging path 33 is preferred.
• a first and / or second motor throttle 82.A, 82.B in a first and / or second charging path 33.A, 33. B moved in the direction of a closed position.
• a hysteresis condition 202 shown in FIG. 3A can be checked and switched in step 203.
• a hysteresis condition 202 may be embodied as a hysteresis condition 202.1 of FIG. 3B for a switching operation from the diesel operation DB to the ignition operation ZB or as a hysteresis condition 202.1 of FIG. 3C from the ignition operation ZB to the diesel operation DB.
• the hysteresis condition 202.1 indicates an acceptable threshold range kl for which the actual receiver pressure p5_IST is below the target pressure P5_SOLL, eg in the receiver volume 81, which is favorable for an ignition jet operation.
• the hysteresis condition 202.2 indicates an acceptable threshold range k2, for which the actual receiver pressure p5_IST lies below the nominal pressure of a receiver pressure p5_SOLL, DB in the receiver volume 81 which is favorable for a diesel operation.
• step 203 of the controller module 200 a changeover of the operating mode from the diesel operation DB (0) to the ignition jet operation ZB (1) is thus initiated.
• step 203 of the controller module 200 a return to the diesel operation DB (1) from the ignition jet operation ZB (0) can be initiated if the hysteresis condition 202.2 is fulfilled, namely in the case where the receiver pressure p5 in the receiver volume 81 in the ignition jet operation ZB or in the vicinity of a favorable for the diesel operation DB receiver pressure p5 in the receiver volume 81;
• the difference between p5_IST and p5_SOLL, DB is below a threshold k2.
• FIG. 4 is a timing of an additional throttling of the engine 10, preferably with the engine throttle 82, in particular the first and / or second engine throttle 82.A, 82. B when starting a transition from the diesel operation DB in the ignition jet operation
• the engine torque Md SOLL as the desired value for times t_DB in the diesel operation DB and for times t_ZB in the ignition jet operation
• a ramp is driven with increasing motor torque Md.
• a switchover between diesel operation DB to ignition jet operation ZS (generally gas operation ZB) takes place at a predetermined p5_SOLL, DB, but only at a comparatively high receiver pressure p5> and at a comparatively late time t '+ ⁇ t.
• the receiver pressure p5_IST, DB in the receiver volume 81 is reduced by throttling-here, for example, by specifying a lowered desired value p5_SOLL, db-an actual value of p5 drops over time; this can lead to a switchover to the ignition jet operation at a comparatively early point in time t 'and at an already comparatively small receiver pressure p5 ⁇ .
• the range of Zündstrahl ists ZB, as shown in Fig. 2 is thus increased over the map area, as it would exist without throttling addition.
• a receiver pressure p5_IST in the receiver volume 81 can be lowered, in particular p5_IST can be lowered below p5_SOLL, eg as a threshold value or below p5_SOLL, DB, depending on whether in the first case in the ignition jet mode ZB or in the second case in the diesel mode DB should be switched.
• p5 is referred to as Switchover operating parameters are used to keep DB values in preferred ranges even in the case of switching processes LAMBDA_SOLL, ZB values of the gas, ie in gas mode ZB or LAMBDA_SOLL, DB values in diesel mode DB.
• LAMBDA_SOLL eg on p5_SOLL, ZB is explained in detail starting from FIG. 2 with regard to the gas operation with reference to the controller structure of FIG. 6.
• FIG. 5 schematically shows the structure of a control module 300 for the first operating state of a diesel operation DB.
• the control module 300 essentially has a first controlled system or control unit 310 for controlling a diesel injection mass m (') _ DB in diesel operation.
• a second controlled system or control unit 320 is designed to control an angle of attack of a compressor bypass throttle 72 and / or a turbine bypass throttle, in this case in particular with corresponding actuating angles aTBP or aVBP of throttle valves.
• a third controlled system or regulating unit 330 is designed to control a setting angle aDK of an engine throttle valve DK; The latter is used in particular for implementing a throttling when starting a changeover from the diesel operation DB to the gas operation ZB according to FIG. 4B.
• the control unit for displaying the first controlled system 310 in the control module 300 for the diesel operation DB uses a map 311, plotted over engine speed nMOT and engine torque Md, for an efficiency level eta DB in diesel operation.
• the map 311 supplies the degree of efficiency eta DB, and the latter determines, via a functional relationship 312, the fuel mass m (') _ DB to be injected, which is denoted here by 313.
• the control unit for displaying the second controlled system 320 in the control module 300 for diesel operation uses a map 321 for the boost pressure p3 in the heat exchanger volume 62, or generally for a state pressure after the compressor 51, which is specified as the desired value p3_SOLL, DB in diesel mode DB ,
• the control unit for displaying the third controlled system 330 in the control module 300 for the diesel operation includes a map 331, which is provided in the present case, especially for low-emission and jump-free implementation of a change of operation from diesel operation in the Zündstrahl sou.
• the third controlled system 330 supports a conversion of an operating state change between ⁇ ', B' as shown in Fig. 2.
• the map 331 the specification of a Recei ver horre p5 in a receiver volume 81 as a target value in diesel mode p5_SOLL, DB in response to an ambient temperature TO and a temperature of the engine cooling water TJV1KW.
• a plot could be made on the charge air temperature T5 and TJvlKW.
• An adjustment of a desired and actual value of p5 in a PID controller 332 supplies a control variable for setting the adjustment angle aDK of the motor throttle 82, which is denoted 333 here.
• the engine throttle 82 may be moved toward a closed position to choke the engine 10 to prepare for a largely jump-free transition to the gas operation ZB.
• a hysteresis condition 202 and measures for engine throttling according to the control unit of the third controlled system 330 a low-emission and non-jumper mode switching is possible.
• FIG. 6 shows a control module 400 for implementing a control for the gas operation, in particular the ignition jet operation ZB.
• This provides at least one controlled system 430 and a further controlled system 420 shown in FIG.
• an additional controlled system 410 and a further auxiliary controlled system 440 are coupled to the controlled system 430.
• the first controlled system 430 converted by means of a control unit, it utilizes a first characteristic field 431.1 and a second characteristic field 431.2, the first characteristic field outputting an efficiency level eta ZB in ignition jet operation as a function of engine speed nMOT and engine torque Md.
• the second characteristic field 431.2 likewise supplies a gas and / or diesel quantity regulation specification x_DL as a function of engine speed nMOT and engine torque Md.
• both characteristics fields 431.1 and 431.2 deliver, via a functional relationship, a mass flow rate of gas for cylinder-specific injection upstream of the cylinder.
• a receiver pressure p5 in the receiver volume 81 can be determined as the desired value in the firing mode ZB, ie p5_SOLL, ZB.
• a manipulated variable can be output at a PID controller 413 as the setting angle of the throttle valve aDK, here designated 434.
• the functional relationship 412 of the controlled system 410 is influenced by the amount of air stored in the receiver volume 81 as a function of the engine speed nMOT and the receiver pressure p5.
• the air consumption is defined in the additional control path 410 as the actual mass flow rate of charge air in relation to a theoretical charge air value.
• the air consumption results from the map 411 from the receiver pressure p5 and a certain engine speed nMOT. Apart from a mass flow rate of gas, which can be set on the cylinder-specific gas metering valves 40, the air expenditure thus enters into the functional relationship 432 for determining the desired value of the receiver pressure p5 in the receiver volume 81.
• a LAMBDA_SOLL, ZB gas value as a function of an engine speed nMOT and a motor torque Md via a map 441 is specified via a further additional control path 440.
• the LAMBDA SOLL, ZB gas value results as a value below 2.5, in particular below 2.
• This is also the control unit for representing the functional relationship 432 supplied.
• the air outlay and, likewise, the gas value LAMBDA SOLL, for example, from the characteristic map 441 are applied to the arithmetic unit for representing a further functional relationship 412. From this, the mass flow rate of gas for the gas solenoid valves is determined as output variable.
• the fuel mass to be injected can be determined taking into account the second characteristic field 431.2; this is denoted here as m (') _ DB with 414.
• the counterpart of the second controlled system 320 for diesel operation DB is shown as a further controlled system 420 in the ignition jet operation ZB, namely the further controlled system 420 for representing an angle of attack ⁇ of a turbine bypass TBP and / or a compressor bypass VBP.
• the basis for this time is a map of a differential pressure Ap_SOLL, DK at the throttle valve as a target value, plotted against the engine rotational speed nMOT and the engine torque Md.
• the differential pressure Ap_SOLL, DK results as pressure downstream of the compressor 51, which is referred to here as boost pressure p3.
• the nominal value of ⁇ is to be understood as meaning the difference between the nominal value of the boost pressure and the receiver pressure p5.
• control variable aVBP or aTBP which is designated here as 423, can be determined via a control unit in the form of a PID controller 422.

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• Engineering & Computer Science (AREA)
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• General Engineering & Computer Science (AREA)
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• Output Control And Ontrol Of Special Type Engine (AREA)
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• 2013
  • 2013-07-08 DE DE102013213349.9A patent/DE102013213349B4/de not_active Expired - Fee Related
• 2014
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