WO2014080455A1 - ディーゼルエンジンの制御装置 - Google Patents
ディーゼルエンジンの制御装置 Download PDFInfo
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- WO2014080455A1 WO2014080455A1 PCT/JP2012/080080 JP2012080080W WO2014080455A1 WO 2014080455 A1 WO2014080455 A1 WO 2014080455A1 JP 2012080080 W JP2012080080 W JP 2012080080W WO 2014080455 A1 WO2014080455 A1 WO 2014080455A1
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- diesel engine
- egr
- control device
- temperature
- correlation value
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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
- 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
- F02D41/0055—Special engine operating conditions, e.g. for regeneration of exhaust gas treatment apparatus
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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
- F02D41/30—Controlling fuel injection
-
- 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
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
- F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
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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
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
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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
- F02D2021/083—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 controlling exhaust gas recirculation electronically
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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
- 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
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
- F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
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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
- F02M26/22—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
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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 a diesel engine provided with an EGR device that recirculates exhaust gas from an exhaust passage to an intake passage.
- an internal combustion engine equipped with an EGR device is known.
- the maximum in-cylinder pressure value is detected based on a signal from the in-cylinder pressure sensor. Then, when the difference between the target value and the in-cylinder pressure maximum value exceeds a predetermined stability limit value, it is determined that the combustion is abnormal, and the EGR rate is corrected in a decreasing direction.
- the EGR rate is corrected in the decreasing direction to improve the combustion.
- reducing the EGR amount does not always lead to the combustion improvement.
- the combustion instability changes as shown in the graph of FIG. In the graph of FIG. 7, changes in combustion instability (for example, torque fluctuation amount) with respect to the EGR amount at low outside air temperature and normal temperature are respectively depicted.
- the combustion instability immediately changes in the stable direction at both low outside air temperature and normal temperature. Immediate combustion improvement is due to an increase in oxygen concentration in the intake air due to a decrease in the EGR amount.
- the present invention has been made in view of the problems as described above, and provides a diesel engine control device capable of suppressing deterioration of a combustion state in a wide range of temperature environmental conditions in a diesel engine equipped with an EGR device. With the goal.
- a first invention provides a control apparatus for a diesel engine including an EGR device that recirculates exhaust gas from an exhaust passage to an intake passage.
- Control means for performing a reduction correction for reducing the exhaust gas recirculation amount by the EGR device when the combustion state of the diesel engine deteriorates;
- First acquisition means for acquiring a temperature correlation value correlated with an in-cylinder temperature at the time of ignition of the diesel engine;
- Limiting means for limiting execution of the weight loss correction when the temperature correlation value is smaller than a predetermined threshold; It is characterized by having.
- the first acquisition means acquires the temperature of intake air taken into the cylinder of the diesel engine as the temperature correlation value.
- the limiting unit is a unit that, when the temperature correlation value is smaller than the threshold, performs the increase correction for stopping the decrease correction and increasing the exhaust gas recirculation amount.
- a fourth invention is any one of the first to third inventions, Second acquisition means for acquiring a pressure correlation value correlated with an in-cylinder pressure at the time of ignition of the diesel engine; Means for setting the threshold according to the pressure correlation value; Is further provided.
- the second acquisition means acquires the pressure of air sucked into the cylinder of the diesel engine as the pressure correlation value.
- a sixth invention is any one of the first to fifth inventions, Means for obtaining an air-fuel ratio of the diesel engine; Means for inhibiting the execution of the limiting means when the air-fuel ratio is richer than a predetermined air-fuel ratio; Is further provided.
- a seventh invention is the invention according to any one of the first to sixth inventions, When the temperature correlation value is smaller than a threshold value, the fuel injection timing is further provided with means for changing the fuel injection timing to the advance side.
- the apparatus further includes means for increasing the injection amount of the pilot injection.
- the control means includes means for acquiring a time fluctuation rate of the rotational speed of the diesel engine, and reduces the exhaust gas recirculation amount by the EGR device when the time fluctuation rate is larger than a predetermined fluctuation rate. Yes.
- the temperature correlation value correlated with the in-cylinder temperature at the time of ignition is obtained.
- execution of the weight reduction correction is restricted. If the EGR amount is reduced while the in-cylinder temperature at the time of ignition is low, the contribution of combustion deterioration due to a decrease in intake air temperature and intake pressure is greater than the contribution to combustion stability due to an increase in intake oxygen concentration, and the combustion state is unstable. Transition to. For this reason, according to the present invention, it is possible to limit the weight reduction correction in accordance with the state of the in-cylinder temperature, so that deterioration of the combustion state can be suppressed under a wide range of temperature environmental conditions.
- the temperature correlation value can be acquired with a simple configuration.
- the decrease correction is stopped and the EGR amount increase correction is performed.
- the EGR amount is increased when the temperature correlation value is smaller than the threshold value, it is possible to prevent the combustion state from deteriorating by stopping the lowering of the intake air temperature and the intake air pressure.
- the threshold is set according to the pressure correlation value having a correlation with the in-cylinder pressure at the time of ignition.
- the in-cylinder temperature at the time of ignition when the combustion becomes unstable varies depending on the in-cylinder pressure. Therefore, according to the present invention, it is possible to accurately specify the time when combustion becomes unstable by variably setting the threshold according to the pressure correlation value.
- the pressure of the intake air drawn into the cylinder of the diesel engine is acquired as the pressure correlation value, it is possible to acquire the pressure correlation value with a simple configuration.
- the restriction on the weight reduction correction is prohibited.
- the combustion stability line is less likely to deteriorate. For this reason, according to the present invention, it is possible to effectively prevent a situation in which an unnecessary EGR amount is restricted under conditions where the deterioration of the combustion stability line does not occur.
- the fuel injection timing is changed to the advance side when the reduction of the EGR amount is restricted. For this reason, according to the present invention, since the ignition timing can be advanced, it is possible to improve combustion stability and effectively suppress a decrease in drivability.
- the injection amount of the pilot injection is increased when the reduction of the EGR amount is restricted. For this reason, according to the present invention, since the in-cylinder temperature can be increased, it is possible to increase the combustion stability and effectively suppress the decrease in drivability.
- the ninth aspect it is possible to accurately determine the combustion state using the time variation rate of the engine speed.
- Embodiment 1 FIG. Embodiment 1 of the present invention will be described with reference to the drawings.
- FIG. 1 is a diagram showing a configuration of an engine system as an embodiment of the present invention.
- the engine of 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 of the present embodiment is a variable capacity 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 of this 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 EGR passage 30 and the bypass passage 36 merge.
- the engine system of the present embodiment includes an ECU (Electronic Control Unit) 50.
- the ECU 50 is a control device that comprehensively controls the entire engine system.
- the ECU 50 captures and processes a sensor signal provided in the engine system. Sensors are installed in various parts of the engine system. For example, an air flow meter 58 is attached to the intake passage 10 downstream of the air cleaner 20, an intake air temperature sensor 60 is attached near the outlet of the intercooler 22, and a supercharging pressure sensor 54 is attached downstream of the diesel throttle. ing.
- 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 feedback control so that the actual EGR rate calculated from the signals of various sensors becomes the target EGR rate.
- PID control based on the difference between the actual value and the target value is performed in EGR control.
- the present invention relates to a specific method of feedback control in EGR control. There is no limitation.
- EGR reduction correction a process for reducing the EGR amount (hereinafter referred to as “EGR reduction correction”) when combustion becomes unstable is performed. More specifically, in the EGR reduction correction, for example, a time fluctuation rate (hereinafter referred to as “rotational fluctuation”) of the engine rotational speed is calculated as a value representing the degree of instability of combustion, and the calculated rotational fluctuation is more than a predetermined threshold value. Is also larger, the target EGR rate is corrected to the low rate side. In this embodiment, in the EGR reduction correction, the correction amount is set according to the magnitude of the rotational fluctuation. However, in the implementation of the present invention, there is no limitation regarding a specific calculation method of the correction amount. .
- FIG. 2 is a timing chart showing combustion instability, EGR amount, and in-cylinder temperature (compression end temperature) at the time of ignition.
- the EGR reduction correction according to the present embodiment when combustion becomes unstable, the EGR amount is controlled in the reduction direction. For this reason, in the example shown in this figure, the instability of combustion shifts in a stable direction by reducing the EGR amount.
- FIG. 3 is a diagram comparing the change in the degree of combustion instability with respect to the EGR amount at a low outside air temperature and a high outside air temperature.
- the combustion instability becomes an almost constant value after immediately changing in the stable direction.
- the combustion instability degree changes in the stable direction, but if the EGR amount is further reduced, the combustion state changes again in the unstable direction.
- the in-cylinder temperature at the time of ignition is about 1000 ° C. or less due to the influence of the outside air temperature or the like, instability of combustion due to EGR reduction occurs.
- FIG. 4 is a timing chart for explaining the EGR control according to the embodiment of the present invention.
- the ECU 50 performs the above-described EGR reduction correction at time t1.
- the ECU 50 estimates the in-cylinder temperature at the time of ignition based on the intake air temperature measured by the intake air temperature sensor 60, the supercharging pressure measured by the supercharging pressure sensor 54, and the like during the EGR reduction correction.
- the ECU 50 limits the reduction in the EGR amount by the EGR reduction correction.
- the EGR reduction correction is stopped and the EGR amount is maintained at an optimal correction amount (in some cases, an increase correction for increasing the EGR amount is performed), or the in-cylinder temperature at the time of ignition is A method of changing the feedback gain of EGR control according to the in-cylinder temperature so as not to fall below the threshold can be performed.
- the predetermined threshold value a value determined by experiment or the like (for example, 1000 ° C.) can be used as the in-cylinder temperature at the time of ignition when the combustion instability phenomenon occurs.
- a value that can be used as a determination as to whether or not the EGR reduction correction can be performed may be a value that has a correlation with the in-cylinder temperature at the time of ignition.
- the value is measured by the intake air temperature sensor 60 instead of the in-cylinder temperature at the time of ignition.
- the taken intake air temperature may be used.
- the EGR reduction correction is limited when the in-cylinder temperature at the time of ignition is lower than a predetermined threshold value.
- the fuel injection timing is advanced. It is good also as performing control to increase, and control to increase the injection quantity of pilot injection (preheating injection). According to such control, it is possible to further improve combustion stability and effectively suppress a decrease in drivability. This control can also be applied to the engine systems of Embodiments 2 and 3 to be described later.
- FIG. 5 is a diagram comparing the change in the degree of combustion anxiety with respect to the EGR amount between a low atmospheric pressure and a high atmospheric pressure. In the example shown in FIG.
- the combustion instability deteriorates when the in-cylinder temperature at the time of low atmospheric pressure is about 1100 degrees or less, whereas the in-cylinder temperature at the time of ignition is low at low atmospheric pressure. Combustion instability deteriorates when the temperature is about 1000 degrees or less.
- the in-cylinder pressure at the time of ignition is measured or estimated using a known method, and whether or not the EGR reduction correction can be executed is determined according to the in-cylinder pressure.
- a threshold value for in-cylinder temperature is set.
- FIG. 6 is an example of a map that defines the relationship between the in-cylinder temperature at the time of ignition and the in-cylinder pressure at the time of ignition limiting EGR reduction correction. As shown in this figure, the higher the in-cylinder pressure at the time of ignition, the lower the in-cylinder temperature at the time of ignition that limits EGR reduction correction. As a result, in an environment where the in-cylinder pressure is low, the execution range of the EGR reduction correction is expanded, so that it is possible to provide an engine system with little decrease in drivability.
- a threshold for determining whether or not EGR reduction correction can be performed is set based on the in-cylinder pressure at the time of ignition.
- the value that can be used for setting the threshold only needs to be a value that has a correlation with the in-cylinder pressure at the time of ignition.
- the intake pressure measured by the boost pressure sensor 54 instead of the in-cylinder pressure at the time of ignition. May be used.
- a threshold for determining whether or not EGR reduction correction can be performed is set based on the in-cylinder pressure at the time of ignition, but according to the in-cylinder pressure at the time of ignition.
- the feedback gain of EGR control may be changed.
- Embodiment 3 FIG. Next, Embodiment 3 of the present invention will be described with reference to the drawings.
- the engine system of the third embodiment is characterized in that it is determined whether or not the EGR reduction correction can be performed according to the air-fuel ratio. That is, in the engine system of the first embodiment described above, it is determined whether or not the EGR reduction correction can be performed based on the in-cylinder temperature at the time of ignition. However, according to the knowledge of the inventor, combustion instability due to EGR reduction correction does not occur unless the air-fuel ratio is excessive.
- the air-fuel ratio (A / F) is measured or estimated using a known method, the in-cylinder temperature at the time of ignition is below a predetermined threshold, and the air-fuel ratio is When the air-fuel ratio is leaner than a predetermined air-fuel ratio, execution of EGR reduction correction is prohibited. As a result, it is possible to more accurately determine whether or not the EGR reduction correction can be performed, and thus it is possible to provide an engine system with little decrease in drivability.
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
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Abstract
Description
前記ディーゼルエンジンの燃焼状態が悪化した場合に前記EGR装置による排気還流量を減量する減量補正を行う制御手段と、
前記ディーゼルエンジンの着火時の筒内温度と相関を持つ温度相関値を取得する第1の取得手段と、
前記温度相関値が所定の閾値より小さい場合に、前記減量補正の実行を制限する制限手段と、
を備えることを特徴としている。
前記第1の取得手段は、前記ディーゼルエンジンの筒内へ吸入される吸気の温度を前記温度相関値として取得することを特徴としている。
前記制限手段は、前記温度相関値が前記閾値より小さい場合に、前記減量補正を停止するとともに前記排気還流量を増量する増量補正を行う手段であることを特徴としている。
前記ディーゼルエンジンの着火時の筒内圧力と相関を持つ圧力相関値を取得する第2の取得手段と、
前記圧力相関値に応じて前記閾値を設定する手段と、
を更に備えることを特徴としている。
前記第2の取得手段は、前記ディーゼルエンジンの筒内へ吸入される空気の圧力を前記圧力相関値として取得することを特徴としている。
前記ディーゼルエンジンの空燃比を取得する手段と、
前記空燃比が所定空燃比よりもリッチである場合に、前記制限手段の実行を禁止する手段と、
を更に備えることを特徴としている。
前記温度相関値が閾値より小さい場合に、燃料噴射時期を進角側へ変更する手段を更に備えることを特徴としている。
前記温度相関値が閾値より小さい場合に、パイロット噴射の噴射量を増量する手段を更に備えることを特徴としている。
前記制御手段は、前記ディーゼルエンジンの回転数の時間変動率を取得する手段を含み、前記時間変動率が所定の変動率よりも大きい場合に前記EGR装置による排気還流量を減量することを特徴としている。
本発明の実施の形態1について図を参照して説明する。
次に、本発明の実施の形態2について図を参照して説明する。実施の形態2のエンジンシステムでは、筒内圧力に応じてEGR減量補正の実行可否を判断する点に特徴を有している。上述した実施の形態1のエンジンシステムでは、着火時の筒内温度に基づいてEGR減量補正の実行可否を判断することとしている。ここで、燃焼不安定度が悪化する着火時の筒内温度は筒内圧力の影響を受ける。図5は、EGR量に対する燃焼不安程度の変化を、低大気圧時と高大気圧時とで比較した図である。図5に示す例では、低大気圧時には着火時の筒内温度が約1100度以下の場合に燃焼不安定度が悪化しているのに対して、低大気圧時には着火時の筒内温度が約1000度以下の場合に燃焼不安定度が悪化している。
次に、本発明の実施の形態3について図を参照して説明する。実施の形態3のエンジンシステムでは、空燃比に応じてEGR減量補正の実行可否を判断する点に特徴を有している。すなわち、上述した実施の形態1のエンジンシステムでは、着火時の筒内温度に基づいてEGR減量補正の実行可否を判断することとしている。しかしながら、発明者の知見では、空燃比が空気過多の状態でないとEGR減量補正による燃焼不安定は発生しない。
4 吸気マニホールド
6 排気マニホールド
8 インジェクタ
10 吸気通路
12 排気通路
14 コンプレッサ
16 タービン
18 可変ノズル
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
58 エアフローメータ
60 吸気温センサ
62 アクセル開度センサ
Claims (9)
- 排気通路から吸気通路へ排気ガスを再循環させるEGR装置を備えたディーゼルエンジンの制御装置において、
前記ディーゼルエンジンの燃焼状態が悪化した場合に前記EGR装置による排気還流量を減量する減量補正を行う制御手段と、
前記ディーゼルエンジンの着火時の筒内温度と相関を持つ温度相関値を取得する第1の取得手段と、
前記温度相関値が所定の閾値より小さい場合に、前記減量補正の実行を制限する制限手段と、
を備えることを特徴とするディーゼルエンジンの制御装置。 - 前記第1の取得手段は、前記ディーゼルエンジンの筒内へ吸入される吸気の温度を前記温度相関値として取得することを特徴とする請求項1に記載のディーゼルエンジンの制御装置。
- 前記制限手段は、前記温度相関値が前記閾値より小さい場合に、前記減量補正を停止するとともに前記排気還流量を増量する増量補正を行う手段であることを特徴とする請求項1または2に記載のディーゼルエンジンの制御装置。
- 前記ディーゼルエンジンの着火時の筒内圧力と相関を持つ圧力相関値を取得する第2の取得手段と、
前記圧力相関値に応じて前記閾値を設定する手段と、
を更に備えることを特徴とする請求項1乃至3の何れか1項に記載のディーゼルエンジンの制御装置。 - 前記第2の取得手段は、前記ディーゼルエンジンの筒内へ吸入される空気の圧力を前記圧力相関値として取得することを特徴とする請求項4に記載のディーゼルエンジンの制御装置。
- 前記ディーゼルエンジンの空燃比を取得する手段と、
前記空燃比が所定空燃比よりもリッチである場合に、前記制限手段の実行を禁止する手段と、
を更に備えることを特徴とする請求項1乃至5の何れか1項記載のディーゼルエンジンの制御装置。 - 前記温度相関値が閾値より小さい場合に、燃料噴射時期を進角側へ変更する手段を更に備えることを特徴とする請求項1乃至6の何れか1項記載のディーゼルエンジンの制御装置。
- 前記温度相関値が閾値より小さい場合に、パイロット噴射の噴射量を増量する手段を更に備えることを特徴とする請求項1乃至6の何れか1項記載のディーゼルエンジンの制御装置。
- 前記制御手段は、前記ディーゼルエンジンの回転数の時間変動率を取得する手段を含み、前記時間変動率が所定の変動率よりも大きい場合に前記EGR装置による排気還流量を減量することを特徴とする請求項1乃至8の何れか1項記載のディーゼルエンジンの制御装置。
Priority Applications (6)
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BR112015010030A BR112015010030A2 (pt) | 2012-11-20 | 2012-11-20 | dispositivo de controle para motor a diesel |
PCT/JP2012/080080 WO2014080455A1 (ja) | 2012-11-20 | 2012-11-20 | ディーゼルエンジンの制御装置 |
EP12888950.8A EP2924264A4 (en) | 2012-11-20 | 2012-11-20 | CONTROL DEVICE FOR DIESEL ENGINE |
US14/439,711 US20150315987A1 (en) | 2012-11-20 | 2012-11-20 | Control device for diesel engine |
CN201280077199.7A CN104813008A (zh) | 2012-11-20 | 2012-11-20 | 柴油发动机的控制装置 |
JP2014548356A JP6115571B2 (ja) | 2012-11-20 | 2012-11-20 | ディーゼルエンジンの制御装置 |
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EP (1) | EP2924264A4 (ja) |
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JP7485026B2 (ja) | 2020-06-04 | 2024-05-16 | 日産自動車株式会社 | 内燃機関の制御方法および制御装置 |
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JPH05215004A (ja) | 1992-02-05 | 1993-08-24 | Nissan Motor Co Ltd | 内燃機関の燃焼制御装置 |
JP2011220310A (ja) * | 2010-04-14 | 2011-11-04 | Toyota Motor Corp | 内燃機関の制御装置 |
JP2011252393A (ja) * | 2010-05-31 | 2011-12-15 | Mazda Motor Corp | ディーゼルエンジンの燃焼制御装置 |
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US5758309A (en) * | 1992-02-05 | 1998-05-26 | Nissan Motor Co., Ltd. | Combustion control apparatus for use in internal combustion engine |
JP3931549B2 (ja) * | 2000-10-19 | 2007-06-20 | 日産自動車株式会社 | 内燃機関のバルブタイミング制御装置 |
JP3975695B2 (ja) * | 2001-06-25 | 2007-09-12 | 日産自動車株式会社 | 自己着火式エンジン |
JP4251123B2 (ja) * | 2003-11-04 | 2009-04-08 | 株式会社デンソー | 内燃機関 |
JP4691012B2 (ja) * | 2006-12-25 | 2011-06-01 | 三菱重工業株式会社 | 内部egrシステム付きエンジン |
EP2392808A4 (en) * | 2009-02-02 | 2015-10-21 | Toyota Motor Co Ltd | CONTROL DEVICE FOR INTERNAL COMBUSTION ENGINE |
CN102650244A (zh) * | 2012-05-17 | 2012-08-29 | 大连理工大学 | 一种低排放直喷式柴油机的实现方法 |
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2012
- 2012-11-20 CN CN201280077199.7A patent/CN104813008A/zh active Pending
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- 2012-11-20 WO PCT/JP2012/080080 patent/WO2014080455A1/ja active Application Filing
- 2012-11-20 BR BR112015010030A patent/BR112015010030A2/pt not_active IP Right Cessation
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JPH05215004A (ja) | 1992-02-05 | 1993-08-24 | Nissan Motor Co Ltd | 内燃機関の燃焼制御装置 |
JP2011220310A (ja) * | 2010-04-14 | 2011-11-04 | Toyota Motor Corp | 内燃機関の制御装置 |
JP2011252393A (ja) * | 2010-05-31 | 2011-12-15 | Mazda Motor Corp | ディーゼルエンジンの燃焼制御装置 |
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CN104813008A (zh) | 2015-07-29 |
US20150315987A1 (en) | 2015-11-05 |
JPWO2014080455A1 (ja) | 2017-01-05 |
EP2924264A1 (en) | 2015-09-30 |
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