WO2014080523A1 - 内燃機関の制御装置 - Google Patents
内燃機関の制御装置 Download PDFInfo
- Publication number
- WO2014080523A1 WO2014080523A1 PCT/JP2012/080491 JP2012080491W WO2014080523A1 WO 2014080523 A1 WO2014080523 A1 WO 2014080523A1 JP 2012080491 W JP2012080491 W JP 2012080491W WO 2014080523 A1 WO2014080523 A1 WO 2014080523A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- egr
- target value
- egr rate
- internal combustion
- combustion engine
- Prior art date
Links
Images
Classifications
-
- 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
-
- 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]
- F02D41/0065—Specific aspects of external EGR control
-
- 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]
- F02D41/0077—Control of the EGR valve or actuator, e.g. duty cycle, closed loop control of position
-
- 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
- F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
-
- 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
- F02D41/1448—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 exhaust gas pressure
-
- 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
- F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
- F02M26/23—Layout, e.g. schematics
- F02M26/25—Layout, e.g. schematics with coolers having bypasses
-
- 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
- F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
- F02D2041/1413—Controller structures or design
-
- 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
- F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
- F02D2041/1413—Controller structures or design
- F02D2041/1431—Controller structures or design the system including an input-output delay
-
- 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
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/10—Air intakes; Induction systems
- F02M35/10373—Sensors for intake systems
- F02M35/1038—Sensors for intake systems for temperature or 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
- Y02T10/40—Engine management systems
Definitions
- the present invention relates to a control device for an internal combustion engine in which an exhaust passage and an intake passage are connected via an EGR valve.
- Japanese Patent Application Laid-Open No. 2005-54657 discloses a technique related to EGR control of a diesel engine.
- the target EGR rate is calculated based on the engine speed, the target injection amount, and the water temperature, and the opening degree of the EGR valve is controlled toward the target EGR rate.
- the estimated value of the EGR rate obtained by performing first-order lag processing or delay processing on the target EGR rate is used for the estimation of the intake fresh air amount, not the target EGR rate. This is because the actual EGR rate follows the target EGR rate with a delay in response due to a response delay caused by the volume of the EGR passage or the collector in the transition period in which the EGR rate changes rapidly.
- the above publication does not describe a specific method of the first-order lag processing or delay processing used for calculating the predicted value of the EGR rate.
- the estimation accuracy of the intake fresh air amount is enhanced by predicting the actual EGR rate by a method that takes into account the response delay of the EGR gas.
- no countermeasure is taken against the delay of the actual EGR rate with respect to the target EGR rate.
- the EGR rate and EGR amount are controlled to the target EGR rate in a transition period in which a response delay occurs although the target EGR rate is an optimum value of the EGR rate determined from the engine speed and the fuel injection amount. I can't. That is, the technique described in the above publication has a problem in terms of the control accuracy of the EGR rate or EGR amount.
- An object of the present invention is to improve the control accuracy of an EGR rate or EGR amount by operating an EGR valve in an internal combustion engine in which an exhaust passage and an intake passage are connected via an EGR valve.
- the control apparatus of the internal combustion engine which concerns on this invention is comprised so that the following operation
- the control device calculates a first-order lag time constant, which is an index of the response delay of the EGR gas movement with respect to the operation of the EGR valve, based on the pressure difference between the upstream and downstream of the EGR valve.
- the control apparatus calculates a control target value related to the control of the EGR valve from the calculated first-order lag time constant and the target value of the EGR rate or EGR amount.
- a method for calculating the control target value it is preferable to calculate the control target value by performing inverse first-order lag conversion using a first-order lag time constant on the target value of the EGR rate or EGR amount.
- the control device operates the EGR valve in accordance with the control target value thus obtained. According to this, the actual value of the EGR rate or EGR amount can be made to accurately follow the target value even in a transition period in which a response delay occurs.
- the target value of the EGR rate or EGR amount is preferably calculated by the following method.
- the base target value of the EGR rate or EGR amount based on steady performance is calculated based on the load and rotation speed of the internal combustion engine and the value of the temperature and pressure conditions that affect the EGR rate or EGR amount.
- the correction amount of the EGR rate or the EGR amount in the transition period is calculated based on the difference between the value of the temperature pressure condition and the steady value of the temperature pressure condition under the load and the rotational speed.
- the target value of the EGR rate or the EGR amount is calculated by correcting the base target value based on the steady performance with the correction amount in the transition period. According to such a method, the target value of the optimal EGR rate or EGR amount at the current load and rotation speed can be calculated even in the transition period.
- FIG. 1 is a diagram showing a configuration of an engine system to which a control device according to an embodiment of the present invention is applied.
- the internal combustion engine according to the present embodiment is a diesel engine with a turbocharger (hereinafter simply referred to as an engine).
- the engine body 2 is provided with four cylinders in series, and an injector 8 is provided for each cylinder.
- An intake manifold 4 and an exhaust manifold 6 are attached to the engine body 2.
- An intake passage 10 through which fresh air taken in from the air cleaner 20 flows is connected to the intake manifold 4.
- a turbocharger compressor 14 is attached to the intake passage 10.
- a diesel throttle 24 is provided downstream of the compressor 14 in the intake passage 10.
- An intercooler 22 is provided between the compressor 14 and the diesel throttle 24 in the intake passage 10.
- the exhaust manifold 6 is connected to an exhaust passage 12 for releasing the exhaust gas emitted from the engine body 2 into the atmosphere.
- a turbocharger turbine 16 is attached to the exhaust passage 12.
- the turbocharger is a variable displacement type, and the turbine 16 is provided with a variable nozzle 18.
- a catalyst device 26 for purifying exhaust gas is provided downstream of the turbine 16 in the exhaust passage 12.
- the engine according to the present embodiment includes an EGR device that recirculates exhaust gas from the exhaust system to the intake system.
- EGR device a position downstream of the diesel throttle 24 in the intake passage 10 and the exhaust manifold 6 are connected by an EGR passage 30.
- An EGR valve 32 is provided in the EGR passage 30.
- An EGR cooler 34 is provided on the exhaust side of the EGR valve 32 in the EGR passage 30.
- the EGR passage 30 is provided with a bypass passage 36 that bypasses the EGR cooler 34.
- a bypass valve 38 that switches the direction in which the exhaust gas flows is provided at a location where the bypass passage 36 branched from the EGR passage 30 joins the EGR passage 30 again.
- the engine system according to the present embodiment includes an ECU (Electronic Control Unit) 50.
- the ECU 50 is a control device that comprehensively controls the entire engine system, and the control device according to the present invention is embodied as one function of the ECU 50.
- ECU50 takes in and processes the signal of the sensor with which the engine system is provided. Sensors are installed in various parts of the engine system.
- An air flow meter 58 is attached to the intake passage 10 downstream of the air cleaner 20, a supercharging pressure sensor 54 is attached downstream of the diesel throttle, and a temperature sensor 60 is attached to the intake manifold 4.
- An exhaust pressure sensor 56 is attached to the exhaust manifold 6. Further, a rotation speed sensor 52 that detects rotation of the crankshaft, an accelerator opening sensor 62 that outputs a signal corresponding to the opening of the accelerator pedal, and the like are also attached.
- the ECU 50 processes the signals of the acquired sensors and operates the actuators according to a predetermined control program.
- the actuator operated by the ECU 50 includes the variable nozzle 18, the injector 8, the EGR valve 32, the diesel throttle 24, and the like. There are many actuators and sensors connected to the ECU 50 other than those shown in the figure, but the description thereof is omitted in this specification.
- the engine control executed by the ECU 50 includes EGR control.
- the EGR valve 32 is operated by feedforward control and feedback control so that the actual value of the EGR rate calculated from the signals of various sensors becomes the control target value.
- the target value of the EGR rate determined from the engine speed and the fuel injection amount is set as the control target value as it is, but in the EGR control of the present embodiment, the target value of the EGR rate is set. Based on this, a control target value that is a control target value is determined.
- the EGR rate target value is determined as the target value of one state quantity of the engine, and the control target value for EGR control by operating the EGR valve 32 is the EGR rate target value. It is decided separately.
- a method for determining the control target value in the EGR control of the present embodiment will be described.
- the response delay of the movement of the EGR gas with respect to the operation of the EGR valve 32 that is, the response delay of the change in the EGR rate with respect to the change in the opening degree of the EGR valve 32 can be represented by “primary delay”.
- the waveform of the EGR rate obtained by operating the EGR valve 32 according to the control target value corresponds to a waveform obtained by first-order delay processing of the control target value. Therefore, if the control target value is determined so that the waveform obtained by first-order delay processing of the control target value becomes the waveform of the target value of the EGR rate, the EGR valve 32 is operated according to the control target value, It becomes possible to achieve the target value of the EGR rate in the actual change of the EGR rate.
- the inventors of the present application have confirmed that the degree of response delay of the change in the EGR rate with respect to the change in the opening degree of the EGR valve 32 is related to the pressure difference between the upstream and downstream of the EGR valve 32.
- the response delay index is the first-order lag time constant, and it has been confirmed by experiments that there is a clear relationship between the first-order lag time constant and the pressure difference between the upstream and downstream sides of the EGR valve 32.
- FIG. 2 is a graph showing the results of examining the tendency of the first-order lag time constant with respect to the pressure difference between the exhaust pressure before the operation of the EGR valve 32 and the supercharging pressure. From this graph, it can be seen that as the pressure difference increases, the first-order lag time constant decreases, that is, the rate of change of the EGR rate increases.
- the first-order lag time constant can be uniquely specified. If the first-order lag time constant can be specified, the control target value for achieving it in the actual change in the EGR rate can be calculated from the target value of the EGR rate by inverse first-order lag conversion using the first-order lag time constant.
- a specific method of determining the control target value can be described using the flowchart of FIG.
- the flowchart of FIG. 3 shows a routine for EGR control executed by the ECU 50 in the present embodiment.
- step S1 of the routine shown in FIG. 3 the engine speed is measured from the signal of the speed sensor 52.
- step S2 the fuel injection amount is calculated according to the accelerator opening obtained from the signal of the accelerator opening sensor 62.
- step S ⁇ b> 3 the boost pressure that is the pressure downstream of the EGR valve 32 is calculated from the signal of the boost pressure sensor 54.
- step S4 the temperature of the gas in the intake manifold 4 is calculated from the signal from the temperature sensor 60.
- the processing in the above steps is processing for obtaining data necessary for calculating the EGR rate target value as the engine state quantity target value. Therefore, the order of each step can be changed as appropriate.
- EGR rate target value The calculation of the EGR rate target value is performed in steps S5 to S7.
- step S5 an EGR rate target value based on steady performance is calculated according to the engine speed, fuel injection amount, boost pressure, and intake manifold gas temperature acquired in steps S1-S4.
- the EGR rate target value based on the steady performance means a value of the EGR rate that can obtain a desired performance when the engine is in a steady state.
- the EGR rate target value based on the steady performance can be expressed as a function of the in-cylinder inflow air amount and the smoke limit air amount in the steady state.
- EGRst is an EGR rate target value on the assumption of steady performance
- Gcylinder the in-cylinder inflow air amount
- Glimit the steady-state smoke limit air amount.
- EGRst (Gcylinder-Glimit) / Gcylinder Equation 1
- the in-cylinder inflow air amount Gcylinder in Equation 1 can be expressed as a function of the supercharging pressure and the intake manifold gas temperature.
- Tin is the intake manifold gas temperature
- Pcharge is the supercharging pressure.
- A, a, and b are constants.
- Gcylinder (A / Tin) * (a * Pcharge + b) ... Equation 2
- the smoke limit air amount Glimit in Equation 1 means the lower limit value of the air amount that can suppress the generation of smoke to an acceptable level.
- the smoke limit air amount Glimit is a constant determined from the engine speed and the fuel injection amount.
- the fuel injection amount represents the magnitude of the engine load.
- the ECU 50 is provided with a map in which the smoke limit air amount is stored in association with the engine speed and the fuel injection amount.
- step S6 the correction amount of the EGR rate in the transition period is calculated according to the engine speed, the fuel injection amount, the boost pressure, and the intake manifold gas temperature acquired in steps S1 to S4. The following two types of EGR rate correction amounts are prepared.
- the first EGR rate correction amount is an EGR rate correction amount corresponding to the transient of the supercharging pressure, and is used as a correction coefficient for the EGR rate target value based on steady performance.
- the magnitude of the supercharging pressure affects the atomization speed of the sprayed fuel, and the smoke limit air amount becomes smaller as the fuel atomization speed increases.
- the first EGR rate correction amount is provided to correct the influence of the supercharging pressure on the smoke limit air amount, and is a constant corresponding to the difference between the current supercharging pressure and the normal supercharging pressure.
- the normal supercharging pressure means a supercharging pressure that is obtained from the current engine speed and fuel injection amount, assuming that the present is the normal time.
- the ECU 50 stores the map in which the normal supercharging pressure is stored in association with the engine speed and the fuel injection amount, and the first EGR rate correction amount in association with the difference between the current supercharging pressure and the normal supercharging pressure. A memorized map is prepared.
- the second EGR rate correction amount is an EGR rate correction amount corresponding to the intake manifold gas temperature transient, and is used as a correction coefficient for the EGR rate target value based on steady performance.
- the level of intake manifold gas temperature affects the atomization speed of the sprayed fuel as well as the supercharging pressure.
- the second EGR rate correction amount is provided to correct the influence of the intake manifold gas temperature on the smoke limit air amount, and is a constant corresponding to the difference between the current intake manifold gas temperature and the intake manifold gas temperature in the steady state. It is said that.
- the intake manifold gas temperature at the steady state means the intake manifold gas temperature obtained at the current engine speed and fuel injection amount, assuming that the current state is the steady state.
- the ECU 50 stores the map in which the steady-state intake manifold gas temperature is stored in association with the engine speed and the injection amount, and the second EGR rate correction amount in the difference between the current intake manifold gas temperature and the steady-state intake manifold gas temperature. A map stored in association is prepared.
- step S7 as shown in the following Expression 3, the EGR rate target value based on the steady performance is multiplied by the first EGR rate correction amount and the second EGR rate correction amount, thereby obtaining an engine state quantity.
- An EGR rate target value as a target value is calculated. According to such a method of calculating the EGR rate target value, the optimum EGR rate target value at the current engine load and engine speed can be calculated even in the transition period.
- EGRT is an EGR rate target value as a state quantity target value
- EGRcorrect1 is a first EGR rate correction amount
- EGRcorrect2 is a second EGR rate correction amount.
- EGRT EGRst * EGRcorrect1 * EGRcorrect2 ⁇ ⁇ ⁇ Equation 3
- steps S5 to S7 In the processing of steps S5 to S7 described above, the order of steps 5 and 6 can be appropriately changed.
- step S ⁇ b> 8 the exhaust pressure that is the pressure upstream of the EGR valve 32 is calculated from the signal of the exhaust pressure sensor 56.
- step S9 the pressure difference between the upstream and downstream sides of the EGR valve 32 is calculated using the boost pressure obtained in step S3 and the exhaust pressure obtained in step S8.
- step S10 a first-order lag time constant corresponding to the pressure difference between the upstream and downstream sides of the EGR valve 32 is calculated.
- the characteristics of the first-order lag time constant with respect to the pressure difference between the upstream side and the downstream side of the EGR valve 32 are mapped and stored. It should be noted that the process in step 8-S10 can be performed prior to the process in steps S5-S7 for calculating the EGR rate target value.
- step S11 the control target value is calculated by the following equation 4 using the EGR rate target value calculated in step S7 and the first-order lag time constant calculated in step S10.
- Expression 4 is an expression showing processing of inverse primary conversion.
- ControlT (i) is the current control target value
- EGRT (i) is the current EGR rate target value
- EGRT (i-1) is the previous EGR rate target value
- TL is the first-order lag time constant
- Ts is calculated It is a period.
- ControlT (i) (EGRT (i) ⁇ EGRT (i-1)) * (TL / Ts) + EGRT (i-1) Equation 4
- the graph of FIG. 4 shows an example of calculating the control target value using Equation 4 above.
- a control target value indicated by a black square in FIG. 4 is calculated every calculation cycle.
- step S11 by performing the calculation in step S11, it is possible to obtain a control target value having a reverse first-order lag relationship with respect to the EGR rate target value (state quantity target value).
- step S12 a feedforward value (F / F value) and a feedback value (F / F value) of the opening degree of the EGR valve 32 are calculated based on the control target value calculated in step S11.
- the graph of FIG. 4 also shows the calculation result of the EGR valve opening based on the control target value.
- the actual value of the EGR rate can be accurately followed by the target value not only in a steady state but also in a transition period in which a response delay occurs.
- the target value of the EGR rate is calculated as the state quantity target value
- the control target value is calculated from the target value of the EGR quantity.
- the target value of the EGR quantity is calculated as the state quantity target value.
- the control target value may be calculated from the target value of the EGR amount.
- the pressure downstream of the EGR valve is calculated from the output value of the supercharging pressure sensor, but the pressure downstream of the EGR valve is estimated from information related to the operating state of the engine and other sensor values. Also good. The same applies to the pressure upstream of the EGR valve.
- the pressure upstream of the EGR valve may be estimated not from the output value of the exhaust pressure sensor but from information related to the operating state of the engine and other sensor values.
- control device according to the present invention is applied to a supercharged engine, but the control device according to the present invention can also be applied to a naturally aspirated engine.
- the control device according to the present invention can be applied not only to a diesel engine but also to a spark ignition engine such as a gasoline engine.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Exhaust-Gas Circulating Devices (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Supercharger (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
Abstract
Description
EGRst=(Gcylinder-Glimit)/Gcylinder ・・・式1
Gcylinder=(A/Tin)*(a*Pcharge+b) ・・・式2
EGRT=EGRst*EGRcorrect1*EGRcorrect2 ・・・式3
ControlT(i)=(EGRT(i)-EGRT(i-1))*(TL/Ts)+EGRT(i-1) ・・・式4
4 インテークマニホールド
6 エキゾーストマニホールド
30 EGR通路
32 EGR弁
50 ECU
52 回転数センサ
54 過給圧センサ
56 排気圧センサ
60 温度センサ
62 アクセル開度センサ
Claims (4)
- 排気通路と吸気通路とをEGR弁を介して接続する内燃機関の制御装置において、
前記EGR弁の動作に対するEGRガスの動きの応答遅れの指標である一次遅れ時定数を前記EGR弁の上流と下流の圧力差に基づいて算出する一次遅れ時定数算出手段と、
前記一次遅れ時定数とEGR率或いはEGR量の目標値とから制御目標値を算出する制御目標値算出手段と、
前記制御目標値に従って前記EGR弁を動作させるEGR弁操作手段と、
を備えることを特徴とする内燃機関の制御装置。 - 前記制御目標値算出手段は、
前記内燃機関の負荷及び回転数とEGR率或いはEGR量に影響する温度圧力条件の値とに基づいて定常性能を前提としたEGR率或いはEGR量のベース目標値を算出する手段と、
前記ベース目標値が基礎とする前記内燃機関の負荷及び回転数のもとでの前記温度圧力条件の定常値と前記ベース目標値が基礎とする前記温度圧力条件の値との差に基づいて過渡期におけるEGR率或いはEGR量の補正量を算出する手段と、
前記ベース目標値を前記補正量で補正することによってEGR率或いはEGR量の前記目標値を算出する手段と、
を含む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。 - 前記制御目標値算出手段は、EGR率或いはEGR量の前記目標値に対して前記一次遅れ時定数を用いた逆一次遅れ変換を施すことによって前記制御目標値を算出することを特徴とする請求項1又は2に記載の内燃機関の制御装置。
- 前記内燃機関は過給機付きの内燃機関であって排気圧センサと過給圧センサとを備え、
前記一次遅れ時定数算出手段は、前記排気圧センサにより計測される排気圧と前記過給圧センサによる計測される過給圧との差から前記圧力差を得ることを特徴とする請求項1乃至3の何れか1項に記載の内燃機関の制御装置。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2012/080491 WO2014080523A1 (ja) | 2012-11-26 | 2012-11-26 | 内燃機関の制御装置 |
JP2014548417A JPWO2014080523A1 (ja) | 2012-11-26 | 2012-11-26 | 内燃機関の制御装置 |
EP12888626.4A EP2924272A4 (en) | 2012-11-26 | 2012-11-26 | DEVICE FOR CONTROLLING AN INTERNAL COMBUSTION ENGINE |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2012/080491 WO2014080523A1 (ja) | 2012-11-26 | 2012-11-26 | 内燃機関の制御装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014080523A1 true WO2014080523A1 (ja) | 2014-05-30 |
Family
ID=50775727
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2012/080491 WO2014080523A1 (ja) | 2012-11-26 | 2012-11-26 | 内燃機関の制御装置 |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2924272A4 (ja) |
JP (1) | JPWO2014080523A1 (ja) |
WO (1) | WO2014080523A1 (ja) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2016056802A (ja) * | 2014-09-10 | 2016-04-21 | 日産自動車株式会社 | Egr制御装置 |
JP2017008813A (ja) * | 2015-06-23 | 2017-01-12 | いすゞ自動車株式会社 | 内燃機関のegrバルブの制御装置及びegrバルブの制御方法 |
CN112523878A (zh) * | 2020-11-10 | 2021-03-19 | 东风汽车集团有限公司 | 一种基于egr率的egr阀闭环控制方法 |
CN113803174A (zh) * | 2020-06-16 | 2021-12-17 | 上海汽车集团股份有限公司 | 一种发动机控制方法和装置 |
US11459965B2 (en) * | 2020-05-06 | 2022-10-04 | Tula Technology, Inc. | Exhaust gas recirculation flow control for reducing emissions with variable displacement internal combustion engines |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0874675A (ja) * | 1994-09-06 | 1996-03-19 | Nissan Motor Co Ltd | 内燃機関の排気還流制御装置 |
JPH09287510A (ja) * | 1996-04-25 | 1997-11-04 | Unisia Jecs Corp | 内燃機関の空燃比制御装置 |
JP2002004904A (ja) * | 2000-06-19 | 2002-01-09 | Mitsubishi Motors Corp | 過給機付きエンジンのegr装置 |
JP2004150343A (ja) * | 2002-10-30 | 2004-05-27 | Komatsu Ltd | エンジンのegrシステムの制御方法 |
JP2005054657A (ja) | 2003-08-04 | 2005-03-03 | Nissan Motor Co Ltd | エンジンの制御装置 |
WO2010035554A1 (ja) * | 2008-09-29 | 2010-04-01 | ヤンマー株式会社 | エンジン |
JP2010261420A (ja) * | 2009-05-11 | 2010-11-18 | Toyota Motor Corp | 内燃機関の制御装置 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3462543B2 (ja) * | 1993-09-29 | 2003-11-05 | 本田技研工業株式会社 | 内燃機関の空燃比制御装置 |
US5918582A (en) * | 1995-07-13 | 1999-07-06 | Nissan Motor | Integrated internal combustion engine control system with high-precision emission controls |
JP3551717B2 (ja) * | 1997-08-08 | 2004-08-11 | 日産自動車株式会社 | エンジンのegr制御装置 |
JP2000097086A (ja) * | 1998-09-18 | 2000-04-04 | Hitachi Ltd | エンジンの吸入空気流量制御方法、制御装置および出力制御方法 |
JP3656518B2 (ja) * | 2000-05-18 | 2005-06-08 | 日産自動車株式会社 | ディーゼルエンジンの制御装置 |
JP3900081B2 (ja) * | 2002-12-17 | 2007-04-04 | トヨタ自動車株式会社 | 内燃機関の筒内流入排気ガス量算出装置、および、吸気通路内流入排気ガス量算出装置 |
US7281518B1 (en) * | 2007-03-15 | 2007-10-16 | Detroit Diesel Corporation | Method and system of diesel engine setpoint compensation for transient operation of a heavy duty diesel engine |
-
2012
- 2012-11-26 WO PCT/JP2012/080491 patent/WO2014080523A1/ja active Application Filing
- 2012-11-26 EP EP12888626.4A patent/EP2924272A4/en not_active Withdrawn
- 2012-11-26 JP JP2014548417A patent/JPWO2014080523A1/ja active Pending
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0874675A (ja) * | 1994-09-06 | 1996-03-19 | Nissan Motor Co Ltd | 内燃機関の排気還流制御装置 |
JPH09287510A (ja) * | 1996-04-25 | 1997-11-04 | Unisia Jecs Corp | 内燃機関の空燃比制御装置 |
JP2002004904A (ja) * | 2000-06-19 | 2002-01-09 | Mitsubishi Motors Corp | 過給機付きエンジンのegr装置 |
JP2004150343A (ja) * | 2002-10-30 | 2004-05-27 | Komatsu Ltd | エンジンのegrシステムの制御方法 |
JP2005054657A (ja) | 2003-08-04 | 2005-03-03 | Nissan Motor Co Ltd | エンジンの制御装置 |
WO2010035554A1 (ja) * | 2008-09-29 | 2010-04-01 | ヤンマー株式会社 | エンジン |
JP2010261420A (ja) * | 2009-05-11 | 2010-11-18 | Toyota Motor Corp | 内燃機関の制御装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP2924272A4 * |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2016056802A (ja) * | 2014-09-10 | 2016-04-21 | 日産自動車株式会社 | Egr制御装置 |
JP2017008813A (ja) * | 2015-06-23 | 2017-01-12 | いすゞ自動車株式会社 | 内燃機関のegrバルブの制御装置及びegrバルブの制御方法 |
US11459965B2 (en) * | 2020-05-06 | 2022-10-04 | Tula Technology, Inc. | Exhaust gas recirculation flow control for reducing emissions with variable displacement internal combustion engines |
CN113803174A (zh) * | 2020-06-16 | 2021-12-17 | 上海汽车集团股份有限公司 | 一种发动机控制方法和装置 |
CN113803174B (zh) * | 2020-06-16 | 2022-09-20 | 上海汽车集团股份有限公司 | 一种发动机控制方法和装置 |
CN112523878A (zh) * | 2020-11-10 | 2021-03-19 | 东风汽车集团有限公司 | 一种基于egr率的egr阀闭环控制方法 |
Also Published As
Publication number | Publication date |
---|---|
JPWO2014080523A1 (ja) | 2017-01-05 |
EP2924272A1 (en) | 2015-09-30 |
EP2924272A4 (en) | 2015-12-09 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP5043899B2 (ja) | 内燃機関のegr流量制御装置 | |
JP5888709B2 (ja) | 内燃機関の制御装置 | |
US7318342B2 (en) | Method for model-based determination of the fresh air mass flowing into the cylinder combustion chamber of an internal combustion engine during an intake phase | |
JP4506564B2 (ja) | 内燃機関の制御装置 | |
JP2008138630A (ja) | 内燃機関の制御装置 | |
JP2005220888A (ja) | 過給機付き内燃機関の過給圧推定装置 | |
WO2020066548A1 (ja) | 内燃機関制御装置 | |
JP2005307847A (ja) | 内燃機関の空気量算出装置 | |
JP5273183B2 (ja) | 内燃機関の制御装置 | |
WO2014080523A1 (ja) | 内燃機関の制御装置 | |
WO2014083654A1 (ja) | 過給機付きエンジンの制御装置 | |
JP2013053546A (ja) | 過給機の制御装置 | |
JP5146619B2 (ja) | 内燃機関の制御装置 | |
JP2020002818A (ja) | 内燃機関の制御装置 | |
JP5387914B2 (ja) | 内燃機関の筒内流入egrガス流量推定装置 | |
JP6222138B2 (ja) | 内燃機関のエミッション推定装置 | |
JP2018155167A (ja) | 内燃機関の制御装置 | |
JP6515903B2 (ja) | 内燃機関の制御装置 | |
JP3956458B2 (ja) | 内燃機関の燃料噴射制御装置 | |
JP2013155613A (ja) | 過給エンジンの制御装置 | |
JP2015206307A (ja) | 内燃機関の制御装置 | |
JP2015010548A (ja) | エンジンの制御装置 | |
JP6115571B2 (ja) | ディーゼルエンジンの制御装置 | |
JP2014152689A (ja) | ターボ過給機付き内燃機関の制御装置 | |
JP2017198091A (ja) | 内燃機関の制御装置 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 12888626 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2014548417 Country of ref document: JP Kind code of ref document: A |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
REEP | Request for entry into the european phase |
Ref document number: 2012888626 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2012888626 Country of ref document: EP |