WO2017017754A1 - パワートレインシステム - Google Patents
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- WO2017017754A1 WO2017017754A1 PCT/JP2015/071214 JP2015071214W WO2017017754A1 WO 2017017754 A1 WO2017017754 A1 WO 2017017754A1 JP 2015071214 W JP2015071214 W JP 2015071214W WO 2017017754 A1 WO2017017754 A1 WO 2017017754A1
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- 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]
- F02D41/005—Controlling exhaust gas recirculation [EGR] according to engine operating conditions
- F02D41/0052—Feedback control of engine parameters, e.g. for control of air/fuel ratio or intake air amount
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- 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]
- F02D41/005—Controlling exhaust gas recirculation [EGR] according to engine operating conditions
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- 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
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/35—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with means for cleaning or treating the recirculated gases, e.g. catalysts, condensate traps, particle filters or heaters
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- 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
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/36—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with means for adding fluids other than exhaust gas to the recirculation passage; with reformers
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- 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
- F02D2200/021—Engine temperature
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- 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
- F02D2200/0414—Air temperature
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- 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
- F02D2200/0418—Air humidity
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- 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
- F02D2200/06—Fuel or fuel supply system parameters
- F02D2200/0606—Fuel temperature
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- 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
- F02D2200/06—Fuel or fuel supply system parameters
- F02D2200/0611—Fuel type, fuel composition or fuel quality
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- 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
- F02D2200/06—Fuel or fuel supply system parameters
- F02D2200/0614—Actual fuel mass or fuel injection amount
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- 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
- F02D2200/10—Parameters related to the engine output, e.g. engine torque or engine speed
- F02D2200/1002—Output torque
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- 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
- F02D2200/10—Parameters related to the engine output, e.g. engine torque or engine speed
- F02D2200/101—Engine speed
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- 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
- F02M2026/001—Arrangements; Control features; Details
- F02M2026/009—EGR combined with means to change air/fuel ratio, ignition timing, charge swirl in the cylinder
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- 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
- F02M26/45—Sensors specially adapted for EGR systems
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- 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 present invention relates to a powertrain system using a spark ignition type internal combustion engine, and more particularly to a powertrain system having an exhaust gas recirculation function for recirculating a part of exhaust gas to the internal combustion engine.
- an exhaust gas recirculation (EGR) device In a spark ignition type internal combustion engine (hereinafter simply referred to as an internal combustion engine), a technique for returning a part of exhaust gas to the internal combustion engine is widely known as an exhaust gas recirculation (EGR) device.
- EGR exhaust gas recirculation
- This exhaust gas recirculation lowers the combustion temperature of the air-fuel mixture in the combustion chamber, so that NOx emission and cooling loss can be reduced. It is also well known that pumping loss at low and medium loads, preignition and knocking at high loads can be reduced by exhaust gas recirculation.
- the theoretical thermal efficiency ⁇ c of the internal combustion engine increases as the specific heat ratio ⁇ increases.
- the average specific heat ratio ⁇ of the entire exhaust gas composition is about 1.3. It is a small value compared with the specific heat ratio ⁇ 1.4 of air. Therefore, when the ratio of the exhaust gas in the air-fuel mixture increases due to the exhaust gas recirculation, there is a problem that the specific heat ratio ⁇ of the air-fuel mixture decreases and the theoretical thermal efficiency ⁇ c decreases.
- nitrogen enrichment means for increasing the nitrogen concentration of exhaust gas is provided,
- the increased exhaust gas is supplied to the intake passage of the internal combustion engine.
- the specific heat ratio ⁇ of nitrogen is about 1.4, which is larger than 1.3, which is a specific heat ratio ⁇ of general exhaust gas, the thermal efficiency ⁇ c of the internal combustion engine compared to the case of recirculating general exhaust gas. Can be increased.
- an internal combustion engine is operated under conditions in which the load, the number of revolutions, the coolant temperature, the fuel properties, and the like change in various ways, and the composition of the exhaust gas recirculated to the internal combustion engine satisfies these various conditions. Adjustment and adaptation are effective in terms of improving fuel consumption, reducing exhaust gas harmful components, and improving output.
- Patent Document 1 there is no description about adjusting the composition of the exhaust gas recirculated to the internal combustion engine according to various operating conditions and fuel properties. Therefore, it is required to more practically control the composition of such exhaust gas in accordance with the operating conditions and fuel properties.
- An object of the present invention is to provide a novel powertrain capable of improving fuel efficiency, reducing exhaust gas harmful components, improving output, etc. by changing the composition of exhaust gas recirculated in accordance with operating conditions and fuel properties To provide a system.
- the features of the present invention are a spark ignition type internal combustion engine, a gas component separation means for extracting a plurality of gas components having different specific heat ratios from exhaust gas of the internal combustion engine, and a plurality of gas components returned to the combustion chamber of the internal combustion engine.
- the power train system includes a recirculation unit and a ratio adjustment unit that adjusts a ratio of a plurality of gas components recirculating to the combustion chamber in accordance with an operation state of the internal combustion engine or a fuel property.
- the composition of the exhaust gas recirculated to the internal combustion engine can be adjusted according to various operating conditions and fuel properties. Accordingly, it is possible to improve fuel consumption, reduce exhaust gas harmful components, improve output, and the like in accordance with a wide range of operating conditions of the internal combustion engine and the fuel used.
- Fig. 1 shows the configuration of the powertrain system.
- reference numeral 1 is a spark ignition type internal combustion engine
- reference numeral 2 is gas component separation means
- reference numeral 3 is ratio adjustment means for adjusting the ratio of gas components
- reference numeral 4 is ratio adjustment means 3. It is an engine controller to control.
- the exhaust gas of the internal combustion engine 1 is separated into at least water H 2 O, nitrogen N 2 and carbon dioxide CO 2 by the gas component separation means 2.
- the separated nitrogen N2 and carbon dioxide CO2 are adjusted to a predetermined ratio of nitrogen N2 and carbon dioxide CO2 by the ratio adjusting means 3 and recirculated to the internal combustion engine 1 as recirculation (EGR) gas.
- EGR recirculation
- the ratio of nitrogen N 2 and carbon dioxide CO 2 of the recirculation gas is arbitrarily set by a ratio command value 3 C sent from the engine controller 4 to the ratio adjusting means 3. Excess nitrogen N2 and carbon dioxide CO2 that have not been recirculated to the internal combustion engine 1 are discharged from the ratio adjusting means 3 to the outside (in the atmosphere).
- reference numeral 11 is a steam separator
- reference numeral 12 is a CO 2 separator.
- the water vapor separator 11 separates moisture H2O from the exhaust gas introduced from the internal combustion engine 1, and can be realized, for example, by adsorbing moisture H2O in the exhaust gas with an adsorbent such as zeolite.
- the water vapor separator 11 can also be realized by liquefying water vapor in the exhaust gas with a condenser and separating the liquefied water with a separator.
- the water vapor separator 11 discharges the separated water H 2 O to the outside, and supplies a mixed gas of carbon dioxide CO 2 and nitrogen N 2 to the CO 2 separator 12.
- the CO2 separation device 12 separates a mixed gas of carbon dioxide CO2 and nitrogen N2 into carbon dioxide CO2 and nitrogen N2.
- CO2 in the mixed gas is adsorbed by a CO2 adsorbent such as activated carbon, zeolite, or solid oxide. This can be achieved.
- the CO2 separation device 12 can be realized by filtering the mixed gas with a gas separation membrane. Carbon dioxide CO2 and nitrogen N2 separated by the CO2 separation device 12 are supplied to the ratio adjusting means 3, respectively.
- the gas component separated by the gas component separation means 2 does not necessarily have a purity of 100%, and is an enriched gas containing more of the corresponding component than the exhaust gas discharged from the internal combustion engine. It is good.
- the volume ratio of carbon dioxide CO2 in the exhaust gas when gasoline is burned with a theoretical mixture is about 10%. Therefore, when gasoline is burned with a theoretical mixture, the separated carbon dioxide CO2 is Carbon dioxide CO 2 enriched gas containing approximately 20% or more by volume of carbon dioxide CO 2 may be used.
- the volume ratio of nitrogen N2 in the exhaust gas when gasoline is burned with a stoichiometric mixture is about 70%, so the separated nitrogen gas contains nitrogen N2 component approximately 80% or more in volume ratio. N2 enriched gas may also be used.
- the separated water vapor H2O contains the water vapor H2O component approximately 20% or more by volume.
- H2O enriched gas is also acceptable.
- reference numerals 21, 22, and 23 are distribution valves that distribute the introduced gas in two directions, and the distribution ratio is arbitrarily set by a command value from the engine controller 4.
- Reference numeral 24 is a mixer for mixing the introduced two gas components, carbon dioxide CO2 and nitrogen N2.
- Nitrogen N2 and carbon dioxide CO2 are introduced into the ratio adjusting means 3 from the gas component separating means 2, respectively.
- the ratio of nitrogen N2 sent to the mixer 24 and nitrogen N2 discharged to the outside is adjusted based on the command value 21C from the engine controller 4.
- the distribution valve 22 adjusts the ratio of the carbon dioxide CO 2 sent to the mixer 24 and the carbon dioxide CO 2 discharged to the outside based on the command value 22 C from the engine controller 4.
- Nitrogen N 2 and carbon dioxide CO 2 supplied to the mixer 24 are mixed in the mixer 24, and a mixed gas of nitrogen N 2 and carbon dioxide CO 2 is sent to the distribution valve 23.
- the ratio of the mixed gas recirculated to the internal combustion engine 1 and the mixed gas discharged to the outside is adjusted based on the command value 23C from the engine controller 4.
- the ratio adjusting means 3 configured in this way, the ratio of nitrogen N2 and carbon dioxide CO2 of the mixed gas recirculated to the internal combustion engine 1 is adjusted by the command value 21C of the regulating valve 21 and the command value 22C of the regulating valve 22 Is done. Further, the amount of the mixed gas recirculated to the internal combustion engine 1 is adjusted by the command value 23C of the adjustment valve 23.
- the specific heat ratio ⁇ of nitrogen N 2 is about 1.4, and the specific heat ratio ⁇ of carbon dioxide CO 2 is about 1.3.
- the specific heat ratio ⁇ of nitrogen N2 is larger than the carbon dioxide CO2 specific heat ratio ⁇ , there is a function of improving the thermal efficiency.
- the specific heat ratio ⁇ of carbon dioxide CO2 is smaller than the specific heat ratio ⁇ of nitrogen N2, it has a function of reducing thermal efficiency, in other words, lowering the combustion temperature.
- the difference in specific heat ratio ⁇ is used, and combustion is controlled according to the operating state of the internal combustion engine.
- the expression that the specific heat ratio ⁇ is large or small is a relative comparison.
- FIG. 4 shows a combustion chamber and an intake / exhaust passage of a four-cycle spark ignition type internal combustion engine.
- the cylinder 31, the piston 32, the intake valve 33, the exhaust valve 34, and the cylinder head 35 form a combustion chamber 36 of the internal combustion engine 1.
- Reference numeral 37 is an intake port
- reference numeral 38 is an exhaust port
- reference numeral 41 is a throttle valve for adjusting the amount of intake air into the combustion chamber 36.
- Reference numeral 40 is a fuel injector for supplying fuel into the intake port 37
- reference numeral 39 is a spark plug
- reference numeral 42 is an air flow sensor for detecting the flow rate of air flowing through the intake port 37
- reference numeral 43 is an EGR pipe for introducing the exhaust gas recirculation gas into the intake port 37, and the opening thereof is provided downstream of the throttle valve 41.
- Reference numeral 44 is a crank angle sensor that detects the rotation angle of a crankshaft (not shown)
- reference numeral 45 is a water temperature sensor that detects the temperature of the cooling water of the internal combustion engine
- reference numeral 46 is O2 that detects the oxygen concentration in the exhaust gas. It is a sensor.
- the ignition timing by the ignition plug 39 is set by a command value 39C from the engine engine controller 4. Further, the fuel injection amount and the injection timing by the fuel injector 40 are also set by the command value 40C from the engine controller 4. Further, the opening degree of the throttle valve 41 is also set by a command value 41C from the engine controller 4.
- the intake air amount detection value 42C by the air flow sensor 42, the crank angle detection value 44C by the crank angle sensor 44, the water temperature detection value 45C by the water temperature sensor 45, and the O2 concentration detection value 46C by the O2 sensor 46 are sent to the engine controller 4, respectively.
- the air from the intake port 37, the recirculation gas from the EGR pipe 43, and the fuel from the injector 40 are mixed downstream of the throttle valve 41 and introduced into the combustion chamber 36.
- the air-fuel mixture in the combustion chamber compressed by the piston 32 is ignited and burned by the spark plug 39 at a predetermined timing, the piston 32 is pushed down by the explosive force, and rotational power can be obtained from the internal combustion engine 1.
- the fuel supplied from the fuel injector 40 is, for example, gasoline, alcohol, natural gas, propane, hydrogen, carbon monoxide gas, or the like.
- the fuel may be used alone or in combination.
- the fuel is supplied from a fuel tank (not shown) to the fuel injector 40 through a fuel pipe (not shown).
- the amount of air introduced into the combustion chamber 36 and the amount of fuel supplied by the fuel injector 40 are feedback controlled so that the O2 concentration in the exhaust gas detected by the O2 sensor 46 becomes a predetermined value.
- the amount of gasoline supplied from the fuel injector 40 is approximately equal to the mass ratio of gasoline 1 to air 15. Is adjusted by the command value 40C.
- the amount of air introduced from the throttle valve 41 is adjusted by the command value 41C.
- the air-fuel ratio is adjusted by adjusting either or both of the air amount and the fuel amount.
- the internal combustion engine 1 described above is operated under a wide range of operating conditions.
- the engine in the case of an internal combustion engine for an automobile, the engine is operated in a wide range from an idle operation to a fully open operation depending on the depression amount of an accelerator pedal. And it is necessary that the recirculation of the recirculated gas whose composition of the exhaust gas is adjusted within this wide operating range be performed rationally.
- FIG. 5 shows a region where knocking is difficult to occur (non-knock region) and a region where knocking is likely to occur (knock region) on the plane of the rotational speed of the internal combustion engine and the engine torque of the internal combustion engine (shown as engine torque in the figure). ).
- the knock region expands in the low torque direction as the rotational speed decreases. This is because the flame propagation speed in the combustion chamber becomes slower as the rotational speed of the internal combustion engine becomes lower. That is, if the flame propagation is slow, the unburned end gas is kept at a high temperature for a longer time, and the self-ignition reaction of the unburned end gas is likely to occur.
- the ignition timing by the spark plug is retarded from the maximum torque generation ignition timing (MBT), or the air-fuel ratio is enriched so that the amount of fuel increases, so that the gas temperature in the combustion chamber To prevent knocking.
- MBT maximum torque generation ignition timing
- knocking avoiding means brings about deterioration of the fuel consumption and output of the internal combustion engine and increase of the exhaust gas emission amount, and there is a strong demand for improvement.
- FIG. 6 illustrates an example of setting the EGR rate in the present embodiment. To do.
- FIG. 6 shows a setting example of the EGR rate with respect to the engine torque in the rotation speed range of a specific internal combustion engine.
- the EGR rate is defined by the following equation (2).
- the EGR rate is represented by EGRrate
- the reflux gas mass is represented by EGRmass
- the intake air mass is represented by AIRmass
- the fuel mass is represented by FUELmass.
- the EGR rate is increased according to the torque increase from the minimum torque to the predetermined first engine torque Tr1. Further, after the first engine torque Tr1, the EGR rate is set to be small as the torque increases.
- exhaust gas is recirculated to reduce pumping loss. That is, when the internal combustion engine is in a low load state, pump loss occurs due to air throttling by the throttle valve.
- the ratio of the recirculated gas is increased to increase the amount of gas introduced into the combustion chamber, the gas pressure in the combustion chamber during the intake stroke increases, so that the pumping loss can be reduced.
- the EGR rate is high and set to be almost constant as the torque increases.
- knocking can be suppressed because the unburned gas temperature is lowered by introducing exhaust gas recirculation. Since knocking is likely to occur as the torque increases, it is preferable to set the EGR rate higher as the torque increases. However, if the EGR rate is increased unnecessarily, misfires are likely to be induced. Therefore, even if the torque increases, the EGR rate is maintained at a substantially constant level.
- FIGS. 7 to 9 show an example in which the ratio of carbon dioxide CO2 and nitrogen N2 of the recirculation gas is adjusted with respect to the engine torque change of the internal combustion engine.
- the ratio of nitrogen N2 in the exhaust gas recirculated is increased in the non-knock region, and the carbon dioxide CO2 ratio in the exhaust gas recirculated in the knock region. Set high. This ratio will be briefly described below.
- the ratio can be changed by the distribution valves 21 and 22 of the ratio adjusting means 3 shown in FIG. Further, the recirculation amount of the exhaust gas in which the composition of the gas component is controlled can be performed by the distribution valve 23.
- a knock region larger than the second engine torque Tr2 is set at 80% nitrogen N2 and 20% carbon dioxide CO2. Then, a predetermined amount of exhaust gas having 20% nitrogen N2 and 80% carbon dioxide CO2 is recirculated to the internal combustion engine.
- FIG. 10 shows the ratio from the viewpoint of thermal efficiency rather than the viewpoint of non-knock area.
- the nitrogen N2 is set to 100% and the carbon dioxide CO2 is set to 0%, which is slightly greater than the second engine torque Tr2.
- the ratio of nitrogen N2 is gradually decreased as the engine torque increases, and conversely, the carbon dioxide CO2 is gradually increased as the engine torque increases, and finally the nitrogen N2
- a predetermined amount of exhaust gas having a composition of 0% and carbon dioxide CO2 is recirculated to the internal combustion engine.
- the thermal efficiency of the internal combustion engine increases as the specific heat ratio ⁇ increases.
- the specific heat ratio ⁇ of nitrogen N2 is about 1.4, and the specific heat ratio ⁇ of carbon dioxide CO2 is about 1.3.
- the specific heat ratio ⁇ of nitrogen N2 is larger than the specific heat ratio of carbon dioxide CO2. Therefore, in the non-knock region, the specific heat ratio ⁇ of the air-fuel mixture is increased by increasing the ratio of nitrogen N2, and high thermal efficiency can be obtained. This is as shown in FIG.
- the unburned gas temperature T TDC compression end temperature
- T BDC the unburned gas temperature before the start of compression
- ⁇ the compression ratio
- ⁇ the specific heat ratio
- the specific heat ratio ⁇ of the air-fuel mixture decreases, the unburned gas temperature T TDC decreases, and the occurrence of knocking is suppressed. be able to.
- the mixture of fuel and air diluted with carbon dioxide CO2 has a higher turbulent combustion rate than the mixture of fuel and air diluted with nitrogen N2.
- the combustion speed is high, flame propagation is completed before the unburned gas reaches self-ignition, and knocking hardly occurs.
- the use of carbon dioxide CO2 single component or carbon dioxide CO2-enriched gas separated from exhaust gas as the recirculation exhaust gas for recirculation can be highly effective in suppressing knock in both the specific heat ratio and the combustion speed. become.
- the combustion speed is increased and the occurrence of knocking can be suppressed.
- pre-ignition may occur in the knock region. This is a phenomenon in an internal combustion engine where a cylinder wall surface or lubricating oil that has become hot due to high load operation heats the fuel / air mixture, and the mixture self-ignites before the ignition timing.
- the unburned gas temperature T TDC is lowered, and the occurrence of pre-ignition can be suppressed.
- knocking may damage the internal combustion engine due to vibrations and large heat dissipation.
- the ignition timing is set later than the maximum torque generation point (MBT), or the air-fuel ratio is set to the side where the amount of fuel increases, so that knocking is not generated. It is common to suppress.
- MBT maximum torque generation point
- these methods have a problem that the fuel consumption of the internal combustion engine deteriorates.
- knocking can be suppressed by increasing the ratio of carbon dioxide CO2, which is a composition component of the exhaust gas that is recirculated, and fuel consumption in the knocking region can be further reduced.
- high thermal efficiency is obtained by increasing the specific heat ratio of the mixture of fuel and air by increasing the ratio of nitrogen N2. Therefore, according to the present embodiment, knocking can be suppressed in a wide operating range of the internal combustion engine, and the fuel efficiency in the overall operating range can be improved.
- the engine torque of the internal combustion engine and the fuel supply amount (fuel injection amount) have a first-order correlation. Therefore, instead of the engine torque as shown in FIGS. 7 to 10, the recirculated gas carbon dioxide CO2 and nitrogen N2 The ratio may be set based on the fuel supply amount (fuel injection amount) per cycle as shown in FIG.
- the ratio of carbon dioxide CO2 and nitrogen N2 is determined with the engine torque as an axis.
- the ratio of carbon dioxide CO2 and nitrogen N2 is determined by a parameter different from the engine torque.
- FIG. 12 shows an example in which the ratio of carbon dioxide CO2 and nitrogen N2 of the recirculation gas to the rotational speed is set under a condition of a constant high engine torque.
- nitrogen N2 is set to 0% and carbon dioxide CO2 is set to 100%.
- the ratio of nitrogen N2 is gradually increased, and conversely the rotational speed increases.
- exhaust gas having a composition in which nitrogen N2 is 100% and carbon dioxide CO2 is 0% is finally recirculated to the internal combustion engine.
- the carbon dioxide CO2 ratio of the recirculation gas is increased as the rotational speed is decreased, and the ratio of nitrogen N2 is set low. This is because, under conditions of high engine torque, the combustion speed becomes slow and knocking tends to occur as the rotational speed decreases. In addition, as the rotational speed decreases, it takes longer for the unburned gas to receive heat from the high heat source, so pre-ignition is likely to occur.
- unburned gas under conditions where knocking and pre-ignition are likely to occur by setting the ratio of carbon dioxide CO2 of the recirculation gas to be high and the ratio of nitrogen N2 to be low as the rotational speed is decreased.
- the occurrence of knocking and pre-ignition can be suppressed by lowering the temperature and further increasing the combustion rate. Note that, under conditions where the rotational speed increases and knocking or pre-ignition does not occur, the specific heat ratio ⁇ of the mixture of fuel and air can be increased by increasing the ratio of nitrogen N2 in the recirculation gas, and high thermal efficiency can be obtained. .
- the ratio of carbon dioxide CO2 and nitrogen N2 is set by one parameter such as engine torque, fuel supply amount, and rotation speed.
- FIG. 13 shows an example in which the ratio of carbon dioxide CO2 and nitrogen N2 of the recirculation gas is set on the plane of the rotational speed and engine torque of the internal combustion engine.
- carbon dioxide CO2 is set to 100% in the knock region
- nitrogen N2 is set to 100% in the non-knock region
- carbon dioxide CO2 is set to 50%
- nitrogen N2 is set to 50% in the vicinity of the boundary between the knock region and the non-knock region.
- the ratio of carbon dioxide CO2 and nitrogen N2 of the recirculation gas can be set according to temperature parameters such as cooling water temperature, intake air temperature, fuel temperature, and outside air temperature. These temperatures related to the operation of the internal combustion engine tend to easily cause knocking and preignition as the temperature increases.
- nitrogen N2 is set to 100% and carbon dioxide CO2 is set to 0%, and the ratio of nitrogen N2 gradually increases as the temperature rises.
- the carbon dioxide CO2 is gradually increased, and finally the exhaust gas having a composition in which nitrogen N2 is 0% and carbon dioxide CO2 is 100% is supplied to the internal combustion engine by a predetermined amount.
- the temperature to be used has a priority such as (1) cooling water temperature, (2) intake air temperature, (3) fuel temperature, and (3) outside air temperature, and is a parameter that affects the operation of the internal combustion engine. It is good to preferentially use the temperature.
- the ratio of carbon dioxide CO2 and nitrogen N2 as recirculation gas can be set according to the octane number of the fuel.
- nitrogen N2 is 0%
- carbon dioxide CO2 is 100%
- the ratio of nitrogen N2 is gradually increased as the octane number increases.
- the carbon dioxide CO2 is gradually reduced, and finally, a predetermined amount of exhaust gas having a composition of nitrogen N2 of 100% and carbon dioxide CO2 of 0% is returned to the internal combustion engine. It is circulating.
- the ratio of carbon dioxide CO2 and nitrogen N2 of the recirculation gas can be set according to the alcohol concentration of the fuel.
- the alcohol concentration of the fuel is low, the effect of suppressing knocking or preignition due to vaporization and cooling of the alcohol is reduced, and this needs to be compensated.
- the ratio of carbon dioxide CO2 and nitrogen N2 of the recirculation gas can be set according to the natural gas concentration of the fuel.
- the octane number of the mixed fuel decreases as the concentration of the natural gas in the fuel decreases, and the effect of suppressing knocking and preignition decreases. This needs to be compensated.
- the ratio of carbon dioxide CO2 and nitrogen N2 as recirculation gas can be set according to the power air-fuel ratio at the time of high load operation.
- the air-fuel ratio (power air-fuel ratio) set at the time of high-load operation increases (lean side)
- the temperature of the unburned mixture increases and knocking and pre-ignition are liable to occur. This needs to be compensated.
- the ratio of carbon dioxide CO2 and nitrogen N2 of the recirculation gas can be set according to the humidity (relative humidity) of the intake air sucked into the internal combustion engine.
- the humidity relative humidity
- the temperature of the unburned mixture decreases, and knocking and pre-ignition are less likely to occur.
- nitrogen N2 is set to 0% and carbon dioxide CO2 is set to 100%.
- the ratio of N2 is increased, and conversely, as the intake air humidity increases, the carbon dioxide CO2 is gradually lowered, and finally a predetermined amount of exhaust gas having a composition in which nitrogen N2 is 100% and carbon dioxide CO2 is 0%.
- the intake air humidity can be detected by, for example, a humidity sensor attached to the air flow sensor.
- nitrogen N2 and carbon dioxide CO2 are extracted from the exhaust gas of the internal combustion engine, and the ratio is controlled in accordance with the operating state and fuel properties. Over operating conditions, it is possible to improve fuel efficiency, reduce exhaust gas harmful components, improve output, and the like.
- the gas components controlled in the exhaust gas composition components are carbon dioxide CO2 and nitrogen N2.
- the specific heat ratio ⁇ of water vapor H 2 O is about 1.33, which is smaller than the specific heat ratio ⁇ 1.4 of nitrogen N 2. Therefore, in the knock region, the ratio of the water vapor H2O of the recirculation gas can be increased to reduce the specific heat ratio ⁇ of the air-fuel mixture, so that knocking and pre-ignition can be suppressed.
- a powertrain system according to a second embodiment of the present invention is shown in FIG.
- water vapor H 2 O obtained by the gas component separation means 2 is introduced into the ratio adjustment means 3. Since other configurations are the same as those of the powertrain system according to the first embodiment, the description thereof is omitted.
- the water vapor H2O separated by the gas component separation means 2 may be an enriched gas containing a larger amount of the corresponding component (water) than the exhaust gas discharged from the internal combustion engine.
- a moisture H2O-enriched gas containing approximately 20% or more by volume of moisture H2O may be used.
- the nitrogen N2 and water H2O are adjusted to a predetermined ratio of nitrogen N2 and water H2O by the ratio adjusting means 3 and recirculated to the internal combustion engine 1 as recirculation (EGR) gas.
- the ratio of the recirculated gas nitrogen N2 and water H2O is arbitrarily set by the ratio command value sent from the engine controller 4 to the ratio adjusting means 3.
- Excess nitrogen N 2 and water H 2 O that have not been recirculated to the internal combustion engine 1 are discharged to the outside from the ratio adjusting means 3.
- FIG. 21 shows an example in which the ratio of the water H2O and nitrogen N2 in the recirculation gas is set on the plane of the rotational speed and engine torque of the internal combustion engine.
- the water vapor H2O is 100% in the knock region
- the nitrogen N2 is 100% in the non-knock region
- the water vapor H2O is 50% and the nitrogen N2 is 50% near the boundary between the knock region and the non-knock region.
- the specific heat ratio ⁇ of the mixture of fuel and air can be reduced by increasing the ratio of moisture H 2 O of the recirculation gas in the knock region, and knocking and pre-ignition can be suppressed.
- the specific heat ratio of the fuel / air mixture can be increased to increase the thermal efficiency.
- water content H2O of water vapor has characteristics similar to those of carbon dioxide CO2, and therefore the ratio between the two may be set by parameters as shown in FIGS.
- the specific heat ratio ⁇ of the mixed gas of water vapor H 2 O and carbon dioxide CO 2 is smaller than the specific heat ratio ⁇ of nitrogen N 2. Therefore, in the knock region, the ratio of the mixed gas of the water vapor H2O of the recirculation gas and the carbon dioxide CO2 can be increased to reduce the specific heat ratio ⁇ of the mixture, so that knocking and preignition can be suppressed.
- a powertrain system according to a third embodiment of the present invention is shown in FIG.
- reference numeral 2B is a nitrogen separation means for separating nitrogen N2 and a mixed gas of water vapor H2O and carbon dioxide CO2 from the exhaust gas of the internal combustion engine 1.
- the nitrogen separation means 2B is different from that in the first embodiment. Since other configurations are the same as those of the powertrain system according to the first embodiment, the description thereof is omitted.
- Nitrogen separation means 2B can be realized by adsorbing moisture H2O and carbon dioxide CO2 in the exhaust gas with an adsorbent such as zeolite or cerium, for example.
- the nitrogen separation means 2B can be realized by using a nitrogen separation membrane.
- the mixed gas of nitrogen N2 separated by the nitrogen separation means 2B and water vapor H2O and carbon dioxide CO2 may be an enriched gas containing more components than the exhaust gas discharged from the internal combustion engine. It ’s good.
- the separated nitrogen N2 gas may be a nitrogen N2 enriched gas containing approximately 80% or more by volume ratio of nitrogen N2 gas.
- the mixed gas of water vapor H2O and carbon dioxide CO2 separated is an enriched mixture of water vapor H2O and carbon dioxide CO2 containing approximately 40% or more by volume ratio of the total components of water vapor H2O and carbon dioxide CO2. Gas is also good.
- the separated mixed gas of nitrogen N2, water vapor H2O and carbon dioxide CO2 is adjusted to a predetermined ratio of the mixed gas of nitrogen N2, water vapor H2O and carbon dioxide CO2 by the ratio adjusting means 3, It is recirculated to the internal combustion engine type 1 as recirculation (EGR) gas.
- EGR recirculation
- the ratio of the recirculated gas nitrogen N2 and the mixed gas of water vapor H2O and carbon dioxide CO2 is arbitrarily set by a ratio command value sent from the engine controller 4 to the ratio adjusting means 3.
- the excess mixed gas of nitrogen N 2, water vapor H 2 O, and carbon dioxide CO 2 that has not been recirculated to the internal combustion engine 1 is discharged from the ratio adjusting means 3 to the outside.
- FIG. 23 shows an example in which the ratio of the mixed gas of water vapor H 2 O and carbon dioxide CO 2 of the recirculation gas and nitrogen N 2 is set on the plane of the rotational speed and engine torque of the internal combustion engine.
- the mixed gas of carbon dioxide CO2 and water vapor H2O is set to 100%
- nitrogen N2 is set to 100%.
- the mixed gas is 50% and nitrogen N2 is 50%.
- the specific heat ratio of the mixed gas can be reduced by increasing the ratio of the mixed gas of the water vapor H2O of the recirculated gas and the carbon dioxide CO2 in the knock region, and knocking and pre-ignition can be suppressed.
- the specific heat ratio of the air-fuel mixture can be increased and the thermal efficiency can be increased by increasing the ratio of nitrogen N2 in the recirculation gas.
- the gas component separation means for extracting a plurality of gas components having different specific heat ratios from the exhaust gas of the internal combustion engine, the recirculation means for returning the plurality of gas components to the combustion chamber of the internal combustion engine,
- a powertrain system having a ratio adjusting means for adjusting a ratio of a plurality of gas components returning to the combustion chamber according to an operating state or a fuel property was constructed.
- the composition of the exhaust gas recirculated to the internal combustion engine can be adjusted according to various operating conditions. This makes it possible to improve fuel consumption, reduce exhaust gas harmful components, improve output, and the like over a wide range of operating conditions of the internal combustion engine.
- this invention is not limited to the above-mentioned Example, Various modifications are included.
- the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.
- a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.
- SYMBOLS 1 Spark ignition type internal combustion engine, 2 ... Gas component separation means, 4 ... Ratio adjustment means, 4 ... Engine controller, 11 ... Water vapor separation apparatus, 12 ... CO2 separation apparatus, 21, 22, 23 ... Distribution valve, 24 ... Mixer 31 ... Cylinder, 32 ... Piston, 33 ... Intake valve, 34 ... Exhaust valve, 35 ... Cylinder head, 36 ... Combustion chamber, 37 ... Intake port, 38 ... Exhaust port, 39 ... Spark plug, 40 ... Fuel injector, 41 ... Throttle valve, 42 ... Air flow sensor, 43 ... EGR pipe, 44 ... Crank angle sensor, 45 ... Water temperature sensor
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- General Engineering & Computer Science (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
- Exhaust-Gas Circulating Devices (AREA)
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Abstract
Description
図6は、本実施形態におけるEGR率の設定例を説明するものである。図6は、或る特定の内燃機関の回転数域において、機関トルクに対するEGR率の設定例を示している。ここでEGR率は以下の(2)式で定義されている。以下の(2)式で、EGR率はEGRrate、還流ガス質量はEGRmass、吸入空気質量はAIRmass、燃料質量はFUELmassで表している。
Claims (12)
- 火花点火式の内燃機関と、前記内燃機関の排気ガスからそれぞれ比熱比の異なる複数のガス成分を取り出すガス成分分離手段と、前記複数のガス成分を前記内燃機関の燃焼室に還流する還流手段と、前記燃焼室に還流する前記複数のガス成分の比率を前記内燃機関の運転状態、或いは燃料性状に対応して調整する比率調整手段とを設けたパワートレインシステム。
- 請求項1に記載のパワートレインシステムにおいて、
前記比熱比の異なるガス成分は、相対的に比熱比の大きいガス成分と比熱比の小さいガス成分であり、
前記比率調整手段は、前記内燃機関の機関トルクが所定値より低い場合には、前記比熱比の大きいガス成分の比率を高くし、前記機関トルクが前記所定値より高い場合には、前記比熱比の小さいガス成分の比率を高くすることを特徴とするパワートレインシステム。 - 請求項1に記載のパワートレインシステムにおいて、
前記比熱比の異なるガス成分は、相対的に比熱比の大きいガス成分と比熱比の小さいガス成分であり、
前記比率調整手段は、前記内燃機関の機関トルクが上昇するにしたがって、前記比熱比の大きいガス成分の比率を低くしていくと共に、前記比熱比の小さいガス成分の比率を高くしていくことを特徴とするパワートレインシステム。 - 請求項1に記載のパワートレインシステムにおいて、
前記比熱比の異なるガス成分は、相対的に比熱比の大きいガス成分と比熱比の小さいガス成分であり、
前記比率調整手段は、前記内燃機関に供給される燃料供給量が多い場合は前記比熱比の大きいガス成分の比率を低くする共に、前記比熱比の小さいガス成分の比率を高くすることを特徴とした請求項1に記載のパワートレインシステム。 - 請求項1に記載のパワートレインシステムにおいて、
前記比熱比の異なるガス成分は、相対的に比熱比の大きいガス成分と比熱比の小さいガス成分であり、
前記比率調整手段は、前記内燃機関の機関トルクが大きい状態で、前記内燃機関の回転数が上昇するにしたがって、前記比熱比の大きいガス成分の比率を高くしていくと共に、前記比熱比の小さいガス成分の比率を低くしていくことを特徴とするパワートレインシステム。 - 請求項1に記載のパワートレインシステムにおいて、
前記比熱比の異なるガス成分は、相対的に比熱比の大きいガス成分と比熱比の小さいガス成分であり、
前記比率調整手段は、前記内燃機関の冷却水温、または吸気温度、または燃料温度、または外気温度が上昇するにしたがって、前記比熱比の大きいガス成分の比率を低くしていくと共に、前記比熱比の小さいガス成分の比率を高くしていくことを特徴とするパワートレインシステム。 - 請求項1に記載のパワートレインシステムにおいて、
前記比熱比の異なるガス成分は、相対的に比熱比の大きいガス成分と比熱比の小さいガス成分であり、
前記比率調整手段は、前記内燃機関に供給される燃料のオクタン価が高くなるにしたがって、前記比熱比の大きいガス成分の比率を高くしていくと共に、前記比熱比の小さいガス成分の比率を低くしていくことを特徴とするパワートレインシステム。 - 請求項1に記載のパワートレインシステムにおいて、
前記比熱比の異なるガス成分は、相対的に比熱比の大きいガス成分と比熱比の小さいガス成分であり、
前記比率調整手段は、前記内燃機関に供給される燃料のアルコール濃度が高くなるにしたがって、前記比熱比の大きいガス成分の比率を高くしていくと共に、前記比熱比の小さいガス成分の比率を低くしていくことを特徴とするパワートレインシステム。 - 請求項1に記載のパワートレインシステムにおいて、
前記比熱比の異なるガス成分は、相対的に比熱比の大きいガス成分と比熱比の小さいガス成分であり、
前記比率調整手段は、前記内燃機関に供給される燃料の天然ガス濃度が高くなるにしたがって、前記比熱比の大きいガス成分の比率を高くしていくと共に、前記比熱比の小さいガス成分の比率を低くしていくことを特徴とするパワートレインシステム。 - 請求項1に記載のパワートレインシステムにおいて、
前記比熱比の異なるガス成分は、相対的に比熱比の大きいガス成分と比熱比の小さいガス成分であり、
前記比率調整手段は、前記内燃機関が高負荷で運転されている時、前記内燃機関に供給される燃料と空気の混合気の空燃比がリーン側に移行するにしたがって、前記比熱比の大きいガス成分の比率を低くしていくと共に、前記比熱比の小さいガス成分の比率を高くしていくことを特徴とするパワートレインシステム。 - 請求項1に記載のパワートレインシステムにおいて、
前記比熱比の異なるガス成分は、相対的に比熱比の大きいガス成分と比熱比の小さいガス成分であり、
前記比率調整手段は、前記内燃機関に吸入される吸気の吸気湿度が増加するにしたがって、前記比熱比の大きいガス成分の比率を高くしていくと共に、前記比熱比の小さいガス成分の比率を低くしていくことを特徴とするパワートレインシステム。 - 請求項1~請求項11のいずれか1つに記載のパワートレインシステムにおいて、
前記比熱比の小さいガス成分は前記排気ガスから分離された二酸化炭素であり、前記比熱比の大きいガス成分は前記排気ガスから分離された窒素であることを特徴とするパワートレインシステム。
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