WO2013111385A1 - 内燃機関の制御装置 - Google Patents
内燃機関の制御装置 Download PDFInfo
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- WO2013111385A1 WO2013111385A1 PCT/JP2012/074873 JP2012074873W WO2013111385A1 WO 2013111385 A1 WO2013111385 A1 WO 2013111385A1 JP 2012074873 W JP2012074873 W JP 2012074873W WO 2013111385 A1 WO2013111385 A1 WO 2013111385A1
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- internal combustion
- combustion engine
- oxygen excess
- cylinder oxygen
- egr
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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
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D21/00—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas
- F02D21/06—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air
- F02D21/08—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air the other gas being the exhaust gas of engine
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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
- F02D23/00—Controlling engines characterised by their being supercharged
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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
- F02D35/00—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
- F02D35/02—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions
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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
- F02D41/0002—Controlling intake air
- F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
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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
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/04—Introducing corrections for particular operating conditions
- F02D41/045—Detection of accelerating or decelerating state
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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
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/04—Introducing corrections for particular operating conditions
- F02D41/10—Introducing corrections for particular operating conditions for acceleration
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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
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
- F02D41/1444—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases
- F02D41/1454—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being an oxygen content or concentration or the air-fuel ratio
- F02D41/1458—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being an oxygen content or concentration or the air-fuel ratio with determination means using an estimation
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- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
- F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
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- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
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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
- F02D41/0002—Controlling intake air
- F02D2041/0017—Controlling intake air by simultaneous control of throttle and exhaust gas recirculation
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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
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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
- Y02T10/12—Improving ICE efficiencies
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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 control device for an internal combustion engine, and more particularly to coordinated control of EGR control by an exhaust gas recirculation device (hereinafter abbreviated as EGR) of the internal combustion engine and supercharger control by a supercharger with a variable flow rate mechanism.
- EGR exhaust gas recirculation device
- An exhaust gas recirculation system comprising a turbocharger control device capable of controlling the supercharging amount and the supercharging pressure of a turbocharger with variable flow rate mechanism, and recirculating a part of exhaust gas into an intake passage or a cylinder
- EGR Internal combustion engines with EGR
- the exhaust pressure is increased by the control of a turbocharger with a variable flow rate mechanism, the intake flow rate to the combustion chamber and the oxygen concentration in the combustion chamber are increased
- Control of EGR and a variable flow rate mechanism for example, the generation of smoke (PM) is not secured, and the reduction amount of the exhaust gas is not secured due to the decrease of the exhaust pressure, so that the NOx reduction effect can not be obtained.
- PM smoke
- Patent Document 1 is an example of this type of cooperative control.
- the EGR control valve is fed back so that the air-fuel ratio becomes the target air-fuel ratio while adjusting the opening of the variable flow rate mechanism within the predetermined range of the partial opening in the operation range for performing exhaust gas recirculation (EGR). By doing this, it is possible to reduce NOx and PM.
- EGR exhaust gas recirculation
- Patent Document 1 exhaust gas recirculation is performed in the partial load region, so in other load regions, NOx and PM can not be reduced by cooperative control. Further, although the PM emission amount largely depends on the in-cylinder oxygen excess rate, in the coordinated control in Patent Document 1, the in-cylinder oxygen excess rate is not considered as a control parameter, and there is room for improvement.
- FIG. 8 is a graph showing the transition of the fuel injection amount, the supplied oxygen concentration, the in-cylinder oxygen excess rate, the NOx emission amount, and the PM emission amount in the transient state.
- the fuel injection amount increases, and feedback control is performed so as to obtain a new target fuel injection amount.
- the intake amount increases, so the air supply oxygen concentration and the in-cylinder oxygen excess rate also temporarily decrease and then start to increase, and then become the new target air supply oxygen concentration Feedback control.
- the oxygen concentration in the supplied air temporarily increases, which causes a problem in that NOx contained in the exhaust gas is increased.
- the in-cylinder oxygen excess rate temporarily decreases in the transient state, which causes a problem in that PM contained in the exhaust gas increases.
- the present invention has been made in view of the above problems, and it is possible to perform coordinated control of EGR control and turbocharger control so as to suppress NOx and PM in exhaust gas in a transition state where the load of the internal combustion engine changes.
- An object of the present invention is to provide a control device for an internal combustion engine.
- the control device for an internal combustion engine transmits an EGR command signal so that an EGR gas supply amount by an exhaust gas recirculation (EGR) device becomes a target EGR gas supply amount, and an EGR valve.
- the supercharge command signal is transmitted to control the opening degree of the variable flow rate mechanism so that the supercharging amount of the supercharger with the variable flow rate mechanism becomes the target supercharging amount.
- a control device for an internal combustion engine including feeder control means, an in-cylinder oxygen excess rate calculation means for calculating an in-cylinder oxygen excess rate based on the operating state of the internal combustion engine, and the in-cylinder oxygen excess rate calculation means Transient state determination means for determining whether the internal combustion engine is in a transient state based on the calculated in-cylinder oxygen excess rate, and when it is determined by the transient state determination means that the internal combustion engine is in a transient state Said EGR valve So that the opening of the probe opening and said variable flow mechanism is smaller than the normal state, characterized in that a switching means for switching the EGR command signal and the supercharging command signal.
- the opening degree and the variable degree of the EGR valve are switched by switching the EGR command signal and the supercharging command signal by the switching means. Control is performed so that the opening degree of the flow rate mechanism becomes smaller than that in the normal state. As a result, a temporary increase in the oxygen concentration in the transient air state and a decrease in the in-cylinder oxygen excess rate are suppressed, so coordinated control that can reduce the NOx and PM emissions can be realized.
- the switching means may switch the EGR command signal and the supercharging command signal so that the opening degree of the EGR valve and the opening degree of the variable flow rate mechanism become lower limit values set in advance. According to this, by controlling the opening degree of the EGR valve and the opening degree of the variable flow rate mechanism to be lower limit values, the temporary increase in the supplied oxygen concentration and the decrease in the in-cylinder oxygen excess rate in the transient state are controlled. Thus, NOx and PM emissions can be reduced.
- the lower limit value of the opening degree of the EGR valve may be set in advance according to the operating state of the internal combustion engine.
- the lower limit value of the degree of opening of the EGR valve is not zero, and by setting the lower limit value defined according to the operating state of the internal combustion engine, NOx and PM emissions can be maintained while keeping the operating efficiency of the internal combustion engine good. The amount can be reduced.
- the transient state determining means is a first determining means for determining whether the in-cylinder oxygen excess rate calculated by the in-cylinder oxygen excess rate calculating means is less than or equal to a first threshold;
- the in-cylinder oxygen excess ratio deviation between the in-cylinder oxygen excess ratio calculated by the ratio calculating means and the optimum value of the in-cylinder oxygen excess ratio preset based on the operating state of the internal combustion engine is not less than a second threshold
- the second in-cylinder oxygen excess rate is equal to or less than the first threshold value in the first determination means, and the second determination means determines the second determination means in the second determination means. If it is determined that the in-cylinder oxygen excess rate deviation is greater than or equal to the second threshold value, it is determined that the internal combustion engine is in a transient state.
- the first determination means in view of the temporary decrease of the in-cylinder oxygen excess rate in the transient state, is the in-cylinder oxygen excess rate calculated by the in-cylinder oxygen excess rate calculation means less than the first threshold value? By determining whether or not there is a transient state.
- the second determination means in view of the in-cylinder oxygen excess rate deviating from the optimum value defined based on the operating state of the internal combustion engine in the transient state, the cylinder of the in-cylinder oxygen excess rate and its optimum value It is determined that there is a transient state by determining whether the internal oxygen excess rate deviation is equal to or greater than the second threshold.
- the determination can be performed with high accuracy by determining that there is a transient state. .
- the transient state determination means determines that the supercharging pressure deviation between the supercharging pressure of the supercharger and the optimal value of the supercharging pressure previously set based on the operating state of the internal combustion engine is equal to or greater than a third threshold. It is determined that the internal combustion engine is in a transition state if the third determination means further determines that the boost pressure deviation is equal to or greater than the third determination means. It is good to do.
- the third determination means in view of the fact that the supercharging pressure deviates from the optimal value specified based on the operating state of the internal combustion engine in the transient state, the supercharging pressure deviation between the supercharging pressure and the optimal value is By determining whether the threshold value is 3 or more, it is determined that there is a transient state. This makes it possible to detect the transient state more accurately.
- the switching means may release switching control for the EGR command signal and the supercharging command signal when it is determined by the transient state determination means that the internal combustion engine is not in a transient state. According to this, when it is determined by the transient state determination means that the transient state is ended, the switching control by the switching means is released and the normal operation state is restored.
- the transient state determination means determines a fourth determination means for determining whether the in-cylinder oxygen excess rate calculated by the in-cylinder oxygen excess rate calculation means is larger than a fourth threshold value;
- the in-cylinder oxygen excess ratio deviation between the in-cylinder oxygen excess ratio calculated by the oxygen excess ratio calculating means and the optimum value of the in-cylinder oxygen excess ratio preset based on the operating state of the internal combustion engine is less than the fifth threshold.
- the fifth in-cylinder oxygen excess rate is larger than the fourth threshold in the fourth determination means, or in the fifth determination means. If it is determined that the in-cylinder oxygen excess rate deviation is less than the fifth threshold value, it may be determined that the internal combustion engine is not in a transient state.
- the fourth threshold and the fifth threshold may be set to be the same as or different from the first threshold and the second threshold described above, respectively.
- the switching means may reset the EGR command signal so that the opening degree of the EGR valve becomes a predetermined opening degree larger than the opening degree during the switching control when canceling the switching control.
- supercharge command signal limiting means may be further provided for limiting the supercharge command signal so that the opening degree of the variable flow rate mechanism becomes the opening degree in the steady state of the internal combustion engine.
- the supercharging command signal is generated so as to reduce the supercharging pressure when the actual supercharging pressure is higher than the target supercharging pressure.
- a transient state for example, sudden acceleration of the vehicle
- a time lag until the supercharge pressure is turned to increase. Increases.
- the in-cylinder oxygen excess rate decreases and PM in the exhaust gas increases, which causes a problem.
- the variable flow rate is preliminarily changed so that the supercharging pressure is not excessively reduced.
- the opening degree and the variable degree of the EGR valve are switched by switching the EGR command signal and the supercharging command signal by the switching means. Control is performed so that the opening degree of the flow rate mechanism becomes smaller than that in the normal state. As a result, a temporary increase in the oxygen concentration in the transient air state and a decrease in the in-cylinder oxygen excess rate are suppressed, so coordinated control that can reduce the NOx and PM emissions can be realized.
- FIG. 1 is a schematic view showing an entire configuration of a control device for an internal combustion engine according to a first embodiment.
- the diesel engine (engine) 1 includes an exhaust turbocharger 3 having an exhaust turbine 3 and a compressor 5 coaxially driven thereby, and the air discharged from the compressor 5 of the exhaust turbocharger 7 is an intake valve. After the air enters the intercooler 11 through the passage 9 and the intake air is cooled, the intake flow rate is controlled by the intake throttle valve 13 and thereafter flows from the intake manifold 15 into the combustion chamber (not shown) of the engine 1 .
- the exhaust turbocharger 7 is a variable flow mechanism-equipped turbocharger (VFT), and its specific structure is shown in FIG. As shown in FIG. 3, the exhaust turbocharger 7 has an inner scroll 19 and an outer scroll 21 extending so as to continuously surround the entire circumference of the turbine rotor in the circumferential direction, and exhaust gas is emitted only to the inner scroll 19.
- VFT control valve 23 which is switching means for switching between the state of flowing the exhaust gas and the state of flowing exhaust gas to both the inner scroll 19 and the outer scroll 21. By operating the VFT control valve 23, the state of flowing exhaust gas only to the inner scroll 19 and the state of flowing exhaust gas to both the inner scroll 19 and the outer scroll 21 are switched.
- the engine 1 is provided with a fuel injection device 29 that controls the fuel injection timing and injection amount from the fuel injection valve 27 and injects the fuel into the combustion chamber.
- the combustion gas ie, the exhaust gas 31 burned in the combustion chamber of the engine 1 passes through the exhaust manifold 33 and the exhaust passage 35 by collecting exhaust ports provided for each cylinder, and the exhaust turbine of the exhaust turbocharger 7. After driving 3 to become a power source of the compressor 5, it is discharged through an exhaust passage 35 through an exhaust gas post-treatment device (not shown).
- the EGR passage 37 is branched from the middle of the exhaust passage 35 or the exhaust manifold 33, and a part of the exhaust gas is injected into the downstream portion of the intake throttle valve 13 through the EGR cooler 39 and the EGR control valve 41.
- An apparatus 40 is provided.
- An air flow meter 43 and an atmospheric temperature sensor 45 are provided on the upstream side of the exhaust turbocharger 7, and an intake temperature sensor 47 and a supercharging pressure sensor 49 are provided in the intake manifold 15. Further, an engine speed sensor 51 and an atmospheric pressure sensor 53 are provided, and signals from the respective sensors are taken into a control unit (ECU) 57 via a signal converter 55.
- ECU control unit
- a drive signal is output to the EGR control valve 41 via the EGR valve control means (EGR control means) 59, and an EGR valve opening degree signal is input to the control device 57.
- a drive signal is output to the intake throttle valve 13 via the throttle valve drive circuit 61, and a throttle valve valve opening degree signal is input to the controller 57.
- a drive signal is output to the VFT control valve 23 (see FIG. 3) constituting the variable flow rate mechanism via the VFT valve control means (supercharger control means) 63.
- the valve opening degree signal of the VFT control valve 23 is input to the control device 57.
- FIG. 2 is an internal configuration block diagram of the control device 57 of the internal combustion engine according to the first embodiment.
- the opening control of the EGR control valve 41 and the coordinated control of the VFT control valve 23 are performed.
- the target boost pressure setting means 65 displays a target boost pressure map 67 based on the engine speed by the engine speed sensor 51 and the fuel injection amount by the fuel injection device 29, which indicate the operating state of the engine 1.
- the target boost pressure r1 is determined using this.
- the actual boost pressure y1 is determined based on the signal from the boost pressure sensor 49.
- the deviation e1 between the actual supercharging pressure y1 and the target supercharging pressure r1 set by the target supercharging pressure setting means 65 is calculated by the adder / subtractor 69, and the PID control unit 80 is used as the supercharging pressure control amount. Is input to
- the target air supply oxygen concentration setting means 73 determines the operating condition of the engine 1, for example, the engine speed by the engine speed sensor 51 and the fuel injection amount by the fuel injection device A target supplied oxygen concentration r2 is obtained using a target supplied oxygen concentration map 75.
- the state quantity estimation calculation unit 77 indicates the operating state of the engine 1, the engine speed from the engine speed sensor 51, the fuel injection amount from the fuel injection device 29, the supercharging pressure from the supercharging pressure sensor 49, and intake. Based on the intake manifold temperature from the temperature sensor 47 and the intake flow rate from the air flow meter 43, the actual supplied oxygen concentration and the in-cylinder oxygen excess rate are calculated. Then, the adder / subtractor 79 calculates the deviation e2 between the actual supplied oxygen concentration y2 estimated by the state quantity estimation calculation unit 77 and the target supplied oxygen concentration r2 set by the target supplied oxygen concentration setting means 73. , And is input to the PID control unit 80 as an air supply oxygen concentration control amount.
- the PID control unit 80 sets the actual boost pressure r1 to the target boost pressure y1 and the actual boost oxygen concentration r2 to the target boost, based on the boost pressure control amount e1 and the boost oxygen concentration control amount e2 input.
- the opening command of the EGR control valve 41 (hereinafter referred to as “EGR opening command” as appropriate) and the opening command of the VFT control valve 23 (hereinafter referred to as “VFT opening command” as appropriate so that the air oxygen concentration y2 is obtained. Generate).
- EGR opening command opening command
- VFT opening command opening command
- the in-cylinder oxygen excess rate estimated by the state quantity estimation calculation unit 77 and the actual boost pressure from the boost pressure sensor 49 are input to the ⁇ limit control unit 81.
- the ⁇ limit control unit 81 switches each of the EGR control valve opening degree command and the VFT control valve opening degree command generated by the PID control unit 80 based on the determination result of the transient state described later. And VFT switching command).
- the upper and lower limit values are regulated by the EGR command value limiter 91. It is output as an opening degree command signal.
- the VFT control command generated by the PID control unit 80 is switched by the VFT switching command generated by the ⁇ limit control unit 81, the upper and lower limit values are restricted by the VFT command value limiter 97, and the VFT control is performed. It is output as an opening degree command signal of the valve 23.
- FIG. 4 is an internal configuration block diagram regarding switching control in the ⁇ limit control unit 81 according to the present invention. As shown in FIG. 4, the in-cylinder oxygen excess ratio ⁇ O 2 input to the ⁇ limit control unit 81 is input to the comparators 101, 102, and 104, and the actual supercharging pressure is input to the adder / subtractor 106. Ru.
- the first determination unit 110 it is determined in the comparator 101 whether or not the in-cylinder oxygen excess rate ⁇ O 2 is less than or equal to a predetermined ⁇ O 2 limit value (for example, 2 or less).
- a predetermined ⁇ O 2 limit value for example, 2 or less.
- the ⁇ O 2 limit value is an example of the “first threshold value” according to the present invention, and as described above with reference to FIG. 10, for determining the decrease of the in-cylinder oxygen excess rate at the time of the transient state occurrence. It is a threshold. That is, in view of the in-cylinder oxygen excess rate temporarily decreasing in the transient state, the first determination unit 110 determines whether or not the in-cylinder oxygen excess rate input is equal to or less than the first threshold value. To determine the presence or absence of a transient state.
- the ⁇ O 2 map 107 is a map that defines the optimum value of the in-cylinder oxygen excess rate with respect to the operating state of the engine 1, and although not shown in FIG.
- the operating state of the engine 1 such as the fuel injection amount is acquired, and the optimum value of the in-cylinder oxygen excess rate corresponding to this is output and input to the adder / subtractor 105.
- a ⁇ O 2 offset value which is an example of the “second threshold value” according to the present invention is input to the adder / subtractor 105 to generate a deviation from the optimum value of the in-cylinder oxygen excess rate ⁇ O 2. Then, it is determined whether the in-cylinder oxygen excess rate ⁇ O 2 is equal to or greater than the deviation.
- the second determination unit 112 compares the in-cylinder oxygen excess rate with the optimum value. By determining whether the in-cylinder oxygen excess rate deviation is greater than or equal to the second threshold, it is determined that there is a transient state.
- the target boost pressure map 108 is a map that defines the optimal value of boost pressure with respect to the operating state of the engine 1, and although not shown in FIG.
- the operating state of the engine 1 such as the fuel injection amount is acquired, and the target boost pressure corresponding to this is output and input to the adder / subtractor 106.
- the actual supercharging pressure is input to the adder / subtractor 106, a deviation from the target supercharging pressure is generated, and the deviation is defined in advance by the comparator 103. It is determined whether or not it is an example of the “third threshold” or more.
- the third determining means 114 further determines the supercharging pressure between the supercharging pressure and the optimal value. By determining whether the deviation is greater than or equal to the third threshold, it is determined that there is a transient state.
- the first determination unit 110, the second determination unit 112, and the third determination unit 114 multiplely determine the transient state based on the different conditions, so that the presence or absence of the transient state can be accurately performed. It can be judged.
- the in-cylinder oxygen excess ratio ⁇ O 2 input to the ⁇ limit control unit 81 in the comparator 104 and the predetermined ⁇ O 2 lower limit value are input in the in-cylinder oxygen excess ratio ⁇ O 2. Is determined to be equal to or less than the ⁇ O 2 lower limit value.
- the ⁇ O 2 lower limit value is a threshold set smaller than the ⁇ O 2 limit value (first threshold value) in the first determination unit 110, and the first determination unit 110, the second determination unit 112, and This is a threshold value for determining that there is a transient state when an extreme decrease in the in-cylinder oxygen excess ratio ⁇ O 2 is detected regardless of the determination result in the third determination unit 114.
- the ⁇ O 2 lower limit value is a threshold set smaller than the ⁇ O 2 limit value (first threshold value) in the first determination unit 110, and the first determination unit 110, the second determination unit 112, and This is a threshold value for determining that there is a transient state when an extreme decrease in the in-cylinder oxygen excess ratio ⁇ O 2 is detected
- the switching command generation unit 122 when it is determined that the transition state is present, the switching command generation unit 122 generates and outputs an EGR switching command and a VFT switching command.
- the EGR switching command is generated using an EGR opening lower limit value map 124 that defines the opening lower limit value of the EGR control valve 41 based on the operating state of the engine 1.
- an EGR switching command for switching the EGR control command is generated so that the operating state of the engine 1 is acquired and the opening degree of the EGR control valve 41 becomes the opening lower limit value based on the EGR opening lower limit value map 124 Be done.
- the VFT switching command is generated so that the opening degree of the VFT control valve 23 becomes the opening lower limit value (typically, zero) regardless of the operating state of the engine 1.
- the opening degree of the EGR control valve 41 and the opening degree of the VFT control valve 23 are compared with those in the normal state by switching the EGR control command and the VFT control command. Control to be smaller. As a result, a temporary increase in the oxygen concentration in the transient air state and a decrease in the in-cylinder oxygen excess rate are suppressed, so coordinated control that can reduce the NOx and PM emissions can be realized.
- FIG. 5 is an internal configuration block diagram regarding cancellation control of switching control in the ⁇ limit control unit 81 according to the present invention.
- cancellation control of switching control it is determined in the above-described first determination unit 110 and second determination unit 112 whether or not it is not in the transient state. That is, in the first determination unit 110, the comparator 101 determines whether the in-cylinder oxygen excess rate ⁇ O 2 is larger than a predetermined ⁇ O 2 limit value (for example, 2 or less). Then, in the second determination unit 112, it is determined whether the in-cylinder oxygen excess rate deviation between the in-cylinder oxygen excess rate and the optimum value thereof is less than the second threshold.
- a predetermined ⁇ O 2 limit value for example, 2 or less
- the first determination unit 110 and the second determination unit 112 in FIG. 5 are examples of the “fourth determination means” and the “fifth determination means” in the present invention respectively.
- the “fourth threshold” and the “fifth threshold” according to the present invention are set to be the same as the “first threshold” and the “second threshold” according to the present invention, respectively.
- the illustrated case is illustrated, but may be set to be different from each other.
- control device 57 since the temporary increase in the supplied oxygen concentration and the decrease in the in-cylinder oxygen excess rate are suppressed in the transient state, the emission of NOx and PM Cooperative control that can reduce the amount can be realized.
- FIG. 6 is a block diagram of an internal configuration of the PID control unit 80 of the control system for an internal combustion engine according to the second embodiment.
- the deviation e2 between the supplied oxygen concentration y2 estimated by the calculation unit 77 and the target supplied oxygen concentration r2 set by the target supplied oxygen concentration setting means 73 is input.
- the PID control unit 80 outputs the VFT opening command based on the inputted deviation e1 and outputs the EGR opening command based on the deviation e2, but in FIG. 6, in particular, the EGR opening command It shows that the signal is output through the integrator 132 after the predetermined gain 130 is applied based on the deviation e2.
- a ⁇ limit control signal indicating whether or not the above-described switching control is in an execution state is input from the ⁇ limit control unit 81.
- the S / W 134 is a switching unit that outputs a reset signal when the ⁇ limit control signal is in the ON state (that is, when the switching control is being performed).
- the integrator 132 resets the integrated value of the gain 130, and outputs an EGR control valve command so that the EGR control valve 41 has a predetermined opening.
- the opening degree of the EGR control valve 41 when the transient state ends and returns to the normal operating state, a delay occurs before the opening degree of the EGR control valve 41, which was closed by switching in the transient state, opens, and the supplied oxygen concentration May increase and NOx may increase.
- the opening degree of the EGR control valve 41 is rapidly increased to prevent an increase in NOx.
- FIG. 7 is a configuration block diagram around the VFT command value limiter 97 of the control system for an internal combustion engine according to the third embodiment.
- the VFT command value limiter 97 is an example of the “supercharging command signal limiting means” according to the present invention, and is set by the upper limit and lower limit setting means 138 set by the upper limit setting means 136 with respect to the VFT opening degree command. Limit to the range specified by the lower limit value.
- the range set by the upper limit value setting means 136 and the lower limit value setting means 138 is the opening range of the VFT control valve 23 allowed in the steady state of the engine 1, and the upper limit value and the lower limit value thereof are respectively the VFT maximum opening degree map It is defined according to the operating state of the engine 1 by the 140 and VFT minimum opening map 142.
- the VFT opening degree command is generated so as to reduce the supercharging pressure when the actual supercharging pressure is higher than the target supercharging pressure.
- the VFT opening command is the supercharge pressure decrease command
- a transient state for example, sudden acceleration of the vehicle
- a time lag until the supercharge pressure is increased. Increases.
- the in-cylinder oxygen excess rate decreases and PM in the exhaust gas increases, which causes a problem.
- the opening degree of the VFT control valve 23 by limiting the opening degree of the VFT control valve 23 to the opening degree in the steady state of the engine 1 in the VFT command value limiter 97, the supercharging pressure is prevented from being excessively reduced, and a transient state It is possible to reduce the time lag when it occurs and to suppress the increase in PM.
- the present invention relates to a control device for an internal combustion engine, and in particular, to coordinated control of EGR control by an exhaust gas recirculation device (hereinafter abbreviated as EGR) of the internal combustion engine and supercharger control by a supercharger with a variable flow rate mechanism. It is possible.
- EGR exhaust gas recirculation device
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Exhaust-Gas Circulating Devices (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Supercharger (AREA)
Abstract
Description
図1は第1実施形態に係る内燃機関の制御装置の全体構成を示す模式図である。ディーゼルエンジン(エンジン)1は、排気タービン3とこれに同軸駆動されるコンプレッサ5を有する排気ターボ過給機7を備えており、該排気ターボ過給機7のコンプレッサ5から吐出された空気は吸気通路9を通って、インタークーラ11に入り吸気が冷却された後、吸気スロットルバルブ13で吸気流量が制御され、その後、吸気マニホールド15からエンジン1の図示しない燃焼室内に流入するようになっている。
尚、図5における第1の判定部110及び第2の判定部112は、それぞれ本発明の「第4の判定手段」及び「第5の判定手段」の一例である。本実施形態では特に、本発明に係る「第4の閾値」及び「第5の閾値」が、それぞれ本発明に係る「第1の閾値」及び「第2の閾値」と同一になるように設定された場合を例示しているが、互いに異なるように設定してもよい。
続いて図6を参照して、第2実施形態に係る内燃機関の制御装置について説明する。第2実施形態では第1実施形態と共通する箇所には共通する符号を付すこととし、重複する説明は適宜省略することとする。
続いて図7を参照して、第3実施形態に係る内燃機関の制御装置について説明する。第3実施形態では第1及び第2実施形態と共通する箇所には共通する符号を付すこととし、重複する説明は適宜省略することとする。
Claims (9)
- 排気ガス再循環(EGR)装置によるEGRガス供給量が目標EGRガス供給量になるようにEGR指令信号を送信してEGRバルブの開度を制御するEGR制御手段と、可変流量機構付き過給機の過給量が目標過給量になるように過給指令信号を送信して前記可変流量機構の開度を制御する過給機制御手段とを備えた内燃機関の制御装置において、
前記内燃機関の運転状態に基づいて筒内酸素過剰率を算出する筒内酸素過剰率算出手段と、
前記筒内酸素過剰率算出手段で算出した筒内酸素過剰率に基づいて前記内燃機関が過渡状態にあるか否かを判定する過渡状態判定手段と、
前記過渡状態判定手段によって前記内燃機関が過渡状態にあると判定された場合、前記EGRバルブの開度及び前記可変流量機構の開度が平常状態に比べて小さくなるように、前記EGR指令信号及び前記過給指令信号を切り換える切換手段と
を備えたことを特徴とする内燃機関の制御装置。 - 前記切換手段は、前記EGRバルブの開度及び前記可変流量機構の開度が予め設定された下限値になるように、前記EGR指令信号及び前記過給指令信号を切り換えることを特徴とする請求項1に記載の内燃機関の制御装置。
- 前記EGRバルブの開度の下限値は、前記内燃機関の運転状態に応じて予め設定されていることを特徴とする請求項2に記載の内燃機関の制御装置。
- 前記過渡状態判定手段は、
前記筒内酸素過剰率算出手段で算出された筒内酸素過剰率が第1の閾値以下であるか否かを判定する第1の判定手段と、
前記筒内酸素過剰率算出手段で算出された筒内酸素過剰率と前記内燃機関の運転状態に基づいて予め設定された筒内酸素過剰率の最適値との筒内酸素過剰率偏差が第2の閾値以上であるか否かを判定する第2の判定手段と
を備えてなり、
前記第1の判定手段で前記筒内酸素過剰率が前記第1の閾値以下であり、且つ、前記第2の判定手段で前記筒内酸素過剰率偏差が前記第2の閾値以上であると判定された場合に、前記内燃機関が過渡状態にあると判定することを特徴とする請求項1から3のいずれか一項に記載の内燃機関の制御装置。 - 前記過渡状態判定手段は、前記過給機の過給圧と前記内燃機関の運転状態に基づいて予め設定された過給圧の最適値との過給圧偏差が第3の閾値以上であるか否かを判定する第3の判定手段を備え、
前記第3の判定手段で更に前記過給圧偏差が以上であると判定された場合に、前記内燃機関が過渡状態にあると判定することを特徴とする請求項4に記載の内燃機関の制御装置。 - 前記切換手段は、前記過渡状態判定手段によって前記内燃機関が過渡状態にないと判定された場合、前記EGR指令信号及び前記過給指令信号に対する切換制御を解除することを特徴とする請求項1から5のいずれか一項に記載の内燃機関の制御装置。
- 前記過渡状態判定手段は、
前記筒内酸素過剰率算出手段で算出された筒内酸素過剰率が第4の閾値より大きいか否かを判定する第4の判定手段と、
前記筒内酸素過剰率算出手段で算出された筒内酸素過剰率と前記内燃機関の運転状態に基づいて予め設定された筒内酸素過剰率の最適値との筒内酸素過剰率偏差が第5の閾値未満であるか否かを判定する第5の判定手段と
を備えてなり、
前記第4の判定手段で前記筒内酸素過剰率が前記第4の閾値より大きい、又は、前記第5の判定手段で前記筒内酸素過剰率偏差が前記第5の閾値未満であると判定された場合に、前記内燃機関が過渡状態にないと判定することを特徴とする請求項6に記載の内燃機関の制御装置。 - 前記切換手段は前記切換制御を解除する際に、前記EGRバルブの開度が前記切換制御時の開度より大きな所定開度になるように前記EGR指令信号をリセットすることを特徴とする請求項6又は7に記載の内燃機関の制御装置。
- 前記可変流量機構の開度が、前記内燃機関の定常状態における開度となるように前記過給指令信号を制限する過給指令信号制限手段を更に備えることを特徴とする請求項1から8のいずれか一項に記載の内燃機関の制御装置。
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EP12866915.7A EP2808515B1 (en) | 2012-01-24 | 2012-09-27 | Control apparatus for internal combustion engine |
KR1020147010988A KR101563831B1 (ko) | 2012-01-24 | 2012-09-27 | 내연 기관의 제어 장치 |
CN201280053266.1A CN103906908B (zh) | 2012-01-24 | 2012-09-27 | 内燃机的控制装置 |
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CN103906908A (zh) | 2014-07-02 |
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