WO2011132253A1 - 内燃機関の制御装置 - Google Patents
内燃機関の制御装置 Download PDFInfo
- Publication number
- WO2011132253A1 WO2011132253A1 PCT/JP2010/056946 JP2010056946W WO2011132253A1 WO 2011132253 A1 WO2011132253 A1 WO 2011132253A1 JP 2010056946 W JP2010056946 W JP 2010056946W WO 2011132253 A1 WO2011132253 A1 WO 2011132253A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat generation
- generation amount
- internal combustion
- combustion engine
- combustion
- 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
- 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
- F02D35/028—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions by determining the combustion timing or phasing
-
- 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
- F02D35/023—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions by determining the cylinder pressure
- F02D35/024—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions by determining the cylinder pressure using an estimation
-
- 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
- F02D41/021—Introducing corrections for particular conditions exterior to the engine
- F02D41/0235—Introducing corrections for particular conditions exterior to the engine in relation with the state of the exhaust gas treating apparatus
- F02D41/024—Introducing corrections for particular conditions exterior to the engine in relation with the state of the exhaust gas treating apparatus to increase temperature of the exhaust gas treating apparatus
- F02D41/0255—Introducing corrections for particular conditions exterior to the engine in relation with the state of the exhaust gas treating apparatus to increase temperature of the exhaust gas treating apparatus to accelerate the warming-up of the exhaust gas treating apparatus at engine start
-
- 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
- F02D41/1497—With detection of the mechanical response of the engine
- F02D41/1498—With detection of the mechanical response of the engine measuring engine roughness
Definitions
- the present invention relates to a control device for an internal combustion engine.
- a technique for determining the amount of heat generated by combustion of an internal combustion engine and using it for various controls of the internal combustion engine is known. During combustion of the internal combustion engine, the amount of heat generation increases from the start of combustion to the end of combustion. The heat generation amount can be used for, for example, calculation of the combustion air-fuel ratio as in the conventional technique.
- the amount of heat generation can be obtained based on the amount of change (difference) between the amount of heat at the start of combustion and the amount of heat at the end of combustion.
- the amount of heat generation at the end of combustion is detected using the output value of the in-cylinder pressure sensor at the end of combustion. Specifically, an in-cylinder pressure sensor output value at the time when the end of combustion is reached is obtained, and the amount of heat generation is obtained based on this output value.
- the present inventor has conducted earnest research and has found that a heat generation amount can be estimated by using information before the end of combustion without using the sensor detection value at the end of combustion. I found it.
- the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a control device for an internal combustion engine that can estimate the amount of heat generation using information before the end of combustion. .
- a first invention is a control device for an internal combustion engine, An acquisition means for obtaining a heat generation amount of the internal combustion engine or a parameter having a correlation with the heat generation amount as a heat generation amount information value; An estimation means for estimating a heat generation amount after the period based on a value that is a predetermined multiple of the heat generation amount information value at a time when the rate of change of the heat generation amount information value takes a maximum value; Control means for controlling the internal combustion engine using the heat generation amount estimated by the estimation means; It is characterized by providing.
- the second invention is the first invention, wherein
- the acquisition means includes Sensor output acquisition means for acquiring an output of an in-cylinder pressure sensor of the internal combustion engine; Means for determining the heat generation amount or the parameter based on the output of the in-cylinder pressure sensor acquired by the sensor output acquisition means; It is characterized by including.
- the third invention is the first or second invention, wherein
- the acquisition means includes means for obtaining the heat generation amount information value at predetermined intervals during operation of the internal combustion engine
- the estimation means includes A peak time point specifying means for specifying a peak time point, which is a time point at which the rate of change of the heat generation amount information value takes a maximum value, by detection or estimation;
- specific information acquisition means for acquiring a value for the peak time specified by the peak time specifying means;
- a calculation means for obtaining the heat generation amount after the peak time point by calculation using the heat generation amount information value acquired by the specific information acquisition means and a predetermined coefficient; It is characterized by including.
- the calculation means includes means for obtaining a heat generation amount at the end of combustion based on a value obtained by doubling the heat generation amount information value for the peak time acquired by the specific information acquisition means. .
- the fifth invention is the third or fourth invention, wherein
- the calculating means includes The heat generation amount information value acquired by the specific information acquisition means after elapse of a predetermined time before the end of combustion of the internal combustion engine is excluded from numerical values used for the calculation for obtaining the heat generation amount To exclude It is characterized by including.
- Determining means for determining whether or not the combustion end timing of the internal combustion engine is likely to be later or later than a predetermined time uses the heat generation amount obtained by the heat generation amount acquisition means when the determination means determines that the combustion end timing may be later or later than the predetermined time. Control of an internal combustion engine is performed.
- the seventh invention is the sixth invention, wherein
- the case where the determination means determines that the combustion end timing of the internal combustion engine is likely to be later or later than a predetermined time is when the internal combustion engine is warmed up by a catalyst when the retardation of the internal combustion engine is greater than or equal to a predetermined value.
- the machine includes at least one of a case where an amount of EGR (Exhaust Gas Recirculation) in the internal combustion engine is equal to or greater than a predetermined amount and a case where the internal combustion engine is performing lean combustion. To do.
- EGR exhaust Gas Recirculation
- control means uses the heat generation amount estimated by the estimation means, uses an air-fuel ratio detection means for detecting an air-fuel ratio at the time of combustion of the internal combustion engine, and uses the heat generation amount estimated by the estimation means. And at least one of property detecting means for detecting the fuel property of the fuel of the internal combustion engine.
- the heat generation amount can be estimated by utilizing the relationship that the combustion rate is 50% when the rate of change of the heat generation amount is maximum.
- the heat generation amount information value (the heat generation amount or a parameter having a correlation with the heat generation amount) obtained from the in-cylinder pressure sensor output
- the third invention it is possible to clearly identify the time when the rate of change of the amount of heat generation or the rate of change of the parameter correlated therewith takes the maximum value. Based on the heat generation amount at the specified time or a parameter correlated therewith, the heat generation amount at the combustion end time can be calculated.
- the amount of heat generated at the end of combustion can be obtained with high accuracy by simple calculation.
- the use of the calculated value of the heat generation amount is discontinued at a point some time before the end of combustion. be able to. As a result, the amount of heat generation can be accurately obtained even under conditions where the noise of the heat generation amount information value increases in the later stage of the combustion stroke.
- the heat generation amount at the combustion end timing can be reliably used in the control of the internal combustion engine.
- the seventh invention it is possible to accurately determine whether or not the combustion end timing of the internal combustion engine is delayed according to a specific situation.
- the detection when the combustion air-fuel ratio or the fuel property is detected using the heat generation amount, the detection can be performed at an early stage.
- FIG. 1 is a diagram illustrating a configuration of a control device for an internal combustion engine according to a first embodiment of the present invention.
- the control device according to the present embodiment is suitable for controlling a moving body such as a vehicle, specifically, an internal combustion engine mounted on an automobile.
- FIG. 1 is a diagram showing an internal combustion engine (hereinafter simply referred to as an engine) to which the control device of this embodiment is applied.
- the engine shown in FIG. 1 is a spark ignition type 4-stroke reciprocating engine provided with a spark plug 6.
- it is also a cylinder direct injection engine provided with the fuel direct injection injector 7 which injects a fuel directly in a cylinder.
- the engine to which the present invention is applied is not limited to the in-cylinder direct injection engine according to the present embodiment.
- the present invention can also be applied to a port injection type engine.
- variable valve timing VVT: Variable Valve Timing
- FIG. 1 shows only one cylinder, but a general vehicle engine is composed of a plurality of cylinders.
- An in-cylinder pressure sensor 5 for measuring the in-cylinder pressure is attached to at least one of the cylinders.
- crank angle sensor 8 that outputs a signal according to the rotation angle of the crankshaft is attached to this engine. From the signal CA of the crank angle sensor 8, the in-cylinder volume V determined by the engine speed (the number of revolutions per unit time) and the position of the piston can be calculated.
- An air cleaner 1 is provided at the inlet of the intake passage connected to the cylinder, and a throttle valve 2 is disposed downstream of the air cleaner 1.
- a surge tank 4 is provided downstream of the throttle valve 2, and an intake pressure sensor 3 for measuring the intake pressure is attached to the surge tank 4.
- two catalysts 10 and 11 are arranged in the exhaust passage connected to the cylinder.
- various exhaust gas sensors such as an air-fuel ratio sensor and a sub oxygen sensor may be provided.
- This engine is provided with an EGR passage connecting the exhaust passage and the intake passage.
- An EGR cooler 13 and an EGR valve 12 are provided in the EGR passage.
- a water temperature sensor 14 for measuring the cooling water temperature is attached to the EGR cooler 13.
- this engine includes an arithmetic processing device 20 as a control device.
- the arithmetic processing unit 20 processes signals from the sensors 3, 5, 8, and 14 and reflects the processing results on the operations of the actuators 2, 6, 7, and 12 and the variable valve mechanism described above.
- the arithmetic processing unit 20 may be a so-called ECU (Electronic Control Unit).
- the arithmetic processing unit 20 stores a process of analog / digital conversion (AD conversion) by synchronizing the output signal of the in-cylinder pressure sensor 5 with the crank angle. By executing this process, the value of the in-cylinder pressure at a desired timing can be detected.
- AD conversion analog / digital conversion
- the arithmetic processing unit 20 stores a PV ⁇ calculation process for calculating a parameter PV ⁇ that correlates with the heat generation amount. This processing is performed using P ( ⁇ ) ⁇ V ( ⁇ ) using in-cylinder pressure P ( ⁇ ) for each crank angle, in-cylinder volume V ( ⁇ ) and specific heat ratio ⁇ for each crank angle in accordance with the crank angle ⁇ . ⁇ can be calculated. Further, the arithmetic processing unit 20 stores a process for calculating a change rate of P ( ⁇ ) ⁇ V ( ⁇ ) ⁇ . By this processing, the rate of change dPV ⁇ / d ⁇ of the heat generation amount at a desired timing (crank angle) during the combustion stroke can be calculated.
- the arithmetic processing unit 20 stores processing for obtaining the air-fuel ratio by calculation using the value of PV ⁇ .
- this process is a process of obtaining the heat generation amount during the intake stroke and the heat generation amount immediately after the end of combustion from the output value of the in-cylinder pressure sensor 5, and obtaining the air-fuel ratio by calculation.
- This type of air-fuel ratio detection technique is known as described in, for example, Japanese Patent Application Laid-Open No. 2006-144463, and therefore further explanation is omitted.
- [Operation of Control Device According to First Embodiment] 2 to 4 are diagrams for explaining the operation of the control device according to the first embodiment of the present invention.
- the amount of heat generation can be obtained based on the amount of change (difference) between the amount of heat at the start of combustion and the amount of heat at the end of combustion.
- the difference between the amount of heat at the start of combustion and the amount of heat at the end of combustion is also referred to as “total heat generation amount” and may be represented by the symbol Q.
- the amount of heat generation at the end of combustion is detected using the output value of the in-cylinder pressure sensor at the end of combustion.
- FIG. 2 is a diagram showing the concept of a heat generation amount calculation method.
- the amount of heat generation can be obtained from the amount of change in PV ⁇ from the start of combustion to the end of combustion (arrow in FIG. 2).
- the combustion start time can be determined at the ignition timing or the timing just before it.
- the end point of combustion can be a point of time when PV ⁇ is maximized from the viewpoint of the effect of cooling loss in the expansion stroke or the influence of noise (such as a sensor thermal strain error).
- FIG. 3 shows the in-cylinder pressure P waveform under normal combustion conditions (FIG. 3A), the PV ⁇ waveform (FIG. 3B), and the rate of change in heat generation dPV ⁇ / d ⁇ with the change in crank angle. It is a figure which shows the waveform (FIG.3 (c)), respectively. 4 shows the in-cylinder pressure P waveform (FIG. 4 (a)), the PV ⁇ waveform (FIG. 4 (b)), and the rate of change in the amount of heat generation in the retarded angle combustion condition as the crank angle changes. It is a figure which respectively shows the waveform (FIG.4 (c)) of dPV (kappa) / d (theta).
- the total heat generation amount Q is obtained from the maximum value PV ⁇ max of PV ⁇ based on the difference (change amount) of PV ⁇ between the combustion start point and the combustion end point. be able to.
- the retarded combustion condition as shown in FIG. 4 a situation may occur in which combustion is still in progress even when the exhaust valve opens.
- the present inventor conducted intensive research and found a technique that can estimate the amount of heat generation using information before the end of combustion without using the sensor detection value at the end of combustion. .
- the inventor of the present application has focused on the fact that a value obtained by doubling the “heat generation amount at the crank angle at which the rate of change of the combustion ratio becomes maximum” can be handled as the total heat generation amount Q.
- the combustion ratio (hereinafter also referred to as “MFB”) is a value defined as an index representing the progress of combustion. Specifically, it is assumed that the combustion ratio varies in the range of 0 to 1 (or in the range of 0% to 100%). When the combustion ratio is 0 (0%), the combustion start point is indicated. When the combustion ratio is 1 (100%), the combustion end point is indicated.
- P ⁇ 0 and V ⁇ 0 are the in-cylinder pressure P and the in-cylinder volume V when the crank angle ⁇ is the predetermined combustion start timing ⁇ 0
- P ⁇ f and V ⁇ f are respectively
- P ⁇ and V ⁇ are the in-cylinder pressure P and the in-cylinder volume V, respectively, when the crank angle ⁇ is an arbitrary value.
- ⁇ is a specific heat ratio.
- crank angle at the 50% combustion rate coincides with the crank angle at which the rate of change in the combustion rate is maximum, that is, the crank angle at which the rate of change in PV ⁇ is maximum.
- the crank angle at which dPV ⁇ / d ⁇ takes the maximum value is specified, and the total heat generation amount Q is determined based on the value obtained by doubling PV ⁇ at the crank angle. .
- crank angle at which dPV ⁇ / d ⁇ takes the maximum value while PV ⁇ is increasing is also referred to as “ ⁇ CA50 ” as meaning “the crank angle of the 50% combustion ratio”.
- the PV ⁇ calculated for ⁇ CA50 is also referred to as “PV ⁇ CA50 ”.
- PV ⁇ CA50 a difference PV kappa and PV kappa CA50 (in the present embodiment is set to zero as shown in FIGS. 3 and 4) in the combustion start time, also referred to as Pv kappa CA50.
- a value obtained by doubling ⁇ PV ⁇ CA50 is defined as a total heat generation amount Q.
- the future information of the heat generation amount Q is estimated using PV ⁇ CA50 without using the sensor detection value at the end of combustion, that is, without waiting for the end of combustion. Can be requested.
- the generation amount Q can be estimated in an estimated manner.
- FIG. 5 is a flowchart of a routine executed by the arithmetic processing unit 20 in the first embodiment of the present invention.
- the arithmetic processing unit 20 is configured to execute a process for calculating ⁇ PV ⁇ max in addition to the process for calculating ⁇ PV ⁇ CA50 described above.
- ⁇ PV ⁇ max first stores the maximum value of P ( ⁇ ) ⁇ V ( ⁇ ) ⁇ calculated according to the crank angle ⁇ , and the stored maximum value and P ( ⁇ ) ⁇ V at the start of combustion. It can be calculated by obtaining the difference between ( ⁇ ) ⁇ .
- step S100 it is first determined whether or not ⁇ PV ⁇ max exceeds a predetermined value ⁇ . In this step, first, ⁇ PV ⁇ max is calculated. If ⁇ PV ⁇ max is equal to or less than the predetermined value ⁇ , it is determined that misfire has occurred (step S102).
- step S104 it is next determined whether or not the catalyst warm-up control is being executed. In the present embodiment, it is assumed that catalyst warm-up control is executed under predetermined conditions in the engine shown in FIG. In step S104, it is determined whether the catalyst warm-up control is currently being executed based on the control command from the arithmetic processing unit 20.
- step S104 If the condition of step S104 is not satisfied, the catalyst warm-up control is not currently executed, and therefore there is little risk of adverse effects of the heat generation amount calculation due to the prolonged combustion period as exemplified with reference to FIG. Can think. Therefore, in the present embodiment, when the condition of step S104 is not satisfied, ⁇ PV ⁇ max is handled as the heat generation amount Q (step S114). Thus, an accurate PV ⁇ max is obtained by using the output value of the in-cylinder pressure sensor 5 at the end of combustion while avoiding the adverse effect of deterioration in accuracy due to the prolonged combustion period, and the actual measured value of the in-cylinder pressure sensor 5 It is possible to calculate the amount of heat generation based on the above.
- ⁇ CA50 is calculated (step S106). Since it is confirmed that the catalyst warm-up control is being executed when the condition of step S104 is satisfied, in the subsequent processing, the estimated value of the heat generation amount is calculated based on the method according to the first embodiment described above. First, using the values of P ( ⁇ ) and V ( ⁇ ) corresponding to the crank angle ⁇ , as schematically shown in FIG. 4C, the value of dPV ⁇ / d ⁇ corresponding to the crank angle ⁇ . Are calculated sequentially. Thereafter, the increase / decrease in dPV ⁇ / d ⁇ is monitored, and the crank angle ⁇ when dPV ⁇ / d ⁇ takes the maximum value is specified. The crank angle specified here is handled as ⁇ CA50 .
- step S108 a process for calculating ⁇ PV ⁇ CA50 is executed (step S108).
- PV ⁇ at the start of combustion is specified (in this embodiment, it is zero as shown in FIGS. 3 and 4). Then, determine the difference between the PV kappa and PV kappa CA50 in the combustion start time, address this difference as Pv kappa CA50.
- the Pv kappa CA50 which was calculated at step S108 to twice the value is substituted into the total heat generation amount Q.
- An image of this calculation is also schematically shown in FIG.
- step S112 a process for calculating the combustion air-fuel ratio is executed.
- the calculation processing of the air-fuel ratio stored in the arithmetic processing unit 20 is executed using the value of the total heat generation amount Q calculated in step S110 or step S114. Thereby, a combustion air fuel ratio can be calculated
- the heat generation amount correlation parameter PV ⁇ CA50 at the 50% combustion ratio is used instead of the heat generation amount correlation parameter PV ⁇ max at the combustion end time, so that the combustion end time is not waited. In both cases, future information on the heat generation amount Q can be estimated. Further, according to the above specific processing according to the first embodiment, when the amount of heat generation is calculated using PV ⁇ obtained from the output of the in-cylinder pressure sensor 5, the combustion end point is late as shown in FIG. Even so, the estimated value of the total heat generation amount Q can be acquired.
- the timing at which the rate of change of the heat generation amount or the rate of change of the parameter correlated therewith takes the maximum value is clearly specified according to the processing of step S106. be able to.
- the total heat generation amount Q can be calculated according to the processing of steps S108 and 110 based on the heat generation amount at the specified time or a parameter correlated therewith.
- the heat generation amount at the end of combustion can be obtained with high accuracy by a simple calculation of multiplying ⁇ PV ⁇ CA50 by 2.
- the process of step S114 and the process of step S110 are selectively executed in accordance with whether or not the condition of step S104 is satisfied, so that there is an advantage that the calculation process of ⁇ PV ⁇ can be shared.
- the above specific processing according to the first embodiment it is possible to determine whether or not the catalyst warm-up control is being executed, and to properly use the processing of steps S110 and S114 based on the determination result.
- the information on the heat generation amount can be reliably used in the control of the internal combustion engine.
- the information on the heat generation amount can be reliably used for calculating the combustion air-fuel ratio.
- PV ⁇ is the “parameter” in the first invention
- dPV ⁇ / d ⁇ is the “change rate of the heat generation amount information value” in the first invention.
- ⁇ CA50 is the “PV ⁇ calculation process” stored in the arithmetic processing unit 20 at the “time when the rate of change of the heat generation amount information value takes the maximum value” in the first invention. Each corresponds to “acquiring means”.
- the arithmetic processing unit 20 executes the processing of steps S106, S108 and S110 of the routine of FIG. 5
- the “estimating means” in the first invention performs arithmetic processing.
- the “control means” in the first invention is realized by the apparatus 20 executing the process of step S112 of the routine of FIG.
- the in-cylinder pressure sensor 5 corresponds to the “in-cylinder pressure sensor” in the second invention.
- the arithmetic processing unit 20 executes the process of step S106 in the routine shown in FIG. 5, so that the “peak time specifying means” in the third aspect of the invention is the step of step S108.
- the “specific information acquisition unit” in the third invention realizes the “calculation unit” in the third invention by executing the process of step S110.
- the “determination means” in the sixth aspect of the present invention is realized by the arithmetic processing unit 20 executing the process of step S104 of the routine of FIG.
- FIG. 6 is a diagram for explaining the effects obtained in the first embodiment of the present invention. The result verified about the air-fuel-ratio detection accuracy in catalyst warm-up operation is shown.
- FIG. 6 shows measurement points according to the “PV ⁇ max method” and measurement points according to “2 * PV ⁇ @ CA50 application”.
- In-cylinder pressure sensors are being developed by various companies as a system to respond to future fuel efficiency and emission regulations, and some have already been put into practical use. By mounting the in-cylinder pressure sensor, precise combustion control and accurate parameter detection can be performed. For this reason, the engine control performance can be improved.
- One technique for applying the in-cylinder pressure sensor is a technique for detecting a combustion air-fuel ratio (see, for example, Japanese Patent Application Laid-Open No. 2006-144643). According to such a technique, the air-fuel ratio can be detected in real time and more accurately than the conventional air-fuel ratio detection method using the air-fuel ratio sensor.
- PV ⁇ is used as a heat generation amount correlation parameter.
- the noise superimposed on the in-cylinder pressure sensor output is amplified by V ⁇ as the distance from the TDC increases. Therefore, if an attempt is made to search for a point where the amount of heat generation becomes maximum in retarded combustion in which the end point of combustion is far from TDC, it becomes susceptible to noise. Therefore, the heat generation amount calculation section may be divided up to the combustion center-of-gravity position ( ⁇ CA50 in the first embodiment).
- the PV ⁇ calculation section or the use permission section may be limited to a predetermined crank angle ( ⁇ CA50 in the first embodiment) according to the combustion gravity center position. Thereby, it can also be made hard to receive the influence of noise. Even in such a modification, according to the first embodiment, if the output value of the in-cylinder pressure sensor up to ⁇ CA50 is obtained, the subsequent heat generation amount can be estimated.
- the configuration for limiting the heat generation amount calculation section (PV ⁇ calculation section or use permission section) described here corresponds to the “exclusion means” in the fifth aspect of the present invention.
- the influence of the thermal strain error of the in-cylinder pressure sensor is small.
- the retarded combustion has a long combustion period (that is, the combustion speed is slow). Therefore, the lower the rotation speed, the longer the time that the in-cylinder pressure sensor is exposed to the combustion gas per unit time. As a result, a thermal strain error is caused in the in-cylinder pressure sensor.
- the influence of the thermal strain error is relatively small up to the combustion center of gravity position.
- the in-cylinder pressure sensor output value up to the combustion gravity center position ( ⁇ CA50 in the first embodiment) is used, so that the adverse effect of the thermal strain error can be avoided.
- a value obtained by doubling ⁇ PV ⁇ CA50 is calculated as the total heat generation amount Q.
- the present invention is not limited to this.
- the combustion rate is 50% when the rate of change of the heat generation amount is maximum, not only the heat generation amount at the end of combustion but also the future information of the heat generation amount, that is, ⁇ CA50
- a later heat generation amount (for example, information on 70%, 80%, 90%, etc. of the total heat generation amount Q) may be estimated.
- the processing unit 20 taking into account that twice the Pv kappa CA50 corresponds to the total heat generation amount Q, the processing unit 20, or to execute the calculation processing for appropriately constant multiple of Pv kappa CA50, or constant It is also possible to create a function (such as a coefficient map) as appropriate without limiting to the numerical value of and to execute a calculation process of multiplying the output value of this function by ⁇ PV ⁇ CA50 . Also by these arithmetic processes, it is possible to obtain an estimated value of the heat generation amount by multiplying ⁇ PV ⁇ CA50 by a predetermined number based on the relationship that the combustion rate is 50% when the rate of change of the heat generation amount is maximum. It is.
- a function such as a coefficient map
- ⁇ PV ⁇ CA50 is multiplied by 2.
- the present invention is not limited to the calculation format in which ⁇ PV ⁇ CA50 is strictly multiplied by 2.0.
- a predetermined coefficient approximately twice as large may be determined in accordance with the guideline that twice of ⁇ PV ⁇ CA50 corresponds to the total heat generation amount Q, and ⁇ PV ⁇ CA50 may be multiplied by this predetermined coefficient.
- the heat generation amount at the end of combustion is calculated based on a value obtained by doubling ⁇ PV ⁇ CA50 , so that heat generation is performed as in the first embodiment. This is because the amount can be estimated.
- the method of using the heat generation amount estimated in this embodiment is not limited to the method of using the combustion air-fuel ratio.
- the heat generation amount obtained in this embodiment can also be used when detecting fuel properties such as alcohol concentration, assuming that the heat generation amount / fuel injection amount is proportional ( ⁇ ) to the lower heating value.
- “the process of detecting the alcohol concentration assuming that the heat generation amount / fuel injection amount is proportional ( ⁇ ) to the lower heating value” corresponds to the “property detection means” in the eighth invention. ing.
- Embodiment 2 The hardware configuration and software configuration of the second embodiment are basically the same as the configuration of the first embodiment except that the control device according to the second embodiment can execute the routine shown in FIG.
- description is abbreviate
- the ⁇ CA50 is constantly monitored, and the heat generation amount is based on ⁇ PV ⁇ CA50 in the combustion cycle that is retarded from a predetermined value. Decided to estimate.
- FIG. 7 is used to explain specific processing executed in the control device for an internal combustion engine according to the second embodiment.
- FIG. 7 is a flowchart of a routine executed by the arithmetic processing unit 20 in the second embodiment of the present invention.
- the flowchart of FIG. 7 is obtained by deleting the process of step S104 of the flowchart of FIG. 5 and adding the process of step S206 instead. Processes similar to those in FIG. 5 are denoted by the same reference numerals, and description thereof is simplified or omitted.
- step S100 is executed. If the condition in step S102 is not satisfied, a misfire determination is made in step S102 as in the first embodiment.
- step S106 the ⁇ CA50 calculation process (step S106) according to the first embodiment is executed.
- step S206 it is determined whether or not ⁇ CA50 is greater than a predetermined value ⁇ (step S206). If the conditions of this step are not satisfied, it is determined that there is no occurrence of retarded combustion, which is a problem in the second embodiment. Accordingly, the process proceeds sequentially with steps S114 and S112, and the current routine is terminated after the air-fuel ratio is detected.
- step S206 determines whether retarded combustion, which is a problem in the second embodiment, has occurred. Therefore, in this case, the process proceeds with steps S108 and S110, and the heat generation amount estimated value calculation using ⁇ PV ⁇ CA50 is executed. Thereafter, the combustion air-fuel ratio is detected using the estimated heat generation amount (step S112), and the current routine ends.
- the heat generation amount at the combustion end timing can be reliably used in the control of the internal combustion engine.
- the “determination means” according to the sixth aspect of the present invention is implemented when the arithmetic processing unit 20 executes the process of step S206.
- the determination as to whether the combustion end timing is delayed may be performed, for example, as follows.
- EGR Exhaust Gas Recirculation
- the actual EGR amount may be calculated and it may be determined whether or not the combustion end timing is delayed or may be delayed depending on whether the EGR amount is a predetermined amount or more. In this case, it may be determined whether or not the combustion end timing is delayed to such an extent that deterioration in accuracy of heat generation amount calculation based on ⁇ PV ⁇ max in step S114 becomes a problem.
- the catalyst warm-up operation determination according to the first embodiment, and the predetermined value comparison determination of ⁇ CA50 according to the second embodiment may be used individually or in combination. It may be used.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
Abstract
Description
熱発生量情報値として内燃機関の熱発生量又は当該熱発生量と相関を有するパラメータを求める取得手段と、
前記熱発生量情報値の変化率が最大値をとる時期における前記熱発生量情報値の所定倍の値に基づいて、前記時期以後の熱発生量を推定する推定手段と、
前記推定手段で推定した前記熱発生量を利用して、前記内燃機関の制御を行う制御手段と、
を備えることを特徴とする。
前記取得手段は、
前記内燃機関の筒内圧センサの出力を取得するセンサ出力取得手段と、
前記センサ出力取得手段で取得した前記筒内圧センサの出力に基づいて、前記熱発生量又は前記パラメータを求める手段と、
を含むことを特徴とする。
前記取得手段が、前記内燃機関の運転中に所定期間ごとに前記熱発生量情報値を求める手段を含み、
前記推定手段は、
前記熱発生量情報値の変化率が最大値をとる時点であるピーク時点を検出または推定によって特定するピーク時点特定手段と、
前記内燃機関の運転中に前記情報取得手段で取得される前記熱発生量情報値のうち、前記ピーク時点特定手段で特定された前記ピーク時点についての値を取得する特定情報取得手段と、
前記特定情報取得手段で取得した前記熱発生量情報値と所定の係数とを用いた計算により、前記ピーク時点以後の前記熱発生量を求める算出手段と、
を含むことを特徴とする。
前記算出手段は、前記特定情報取得手段で取得した前記ピーク時点についての前記熱発生量情報値を2倍した値に基づいて燃焼終了時期の熱発生量を求める手段を、含むことを特徴とする。
前記算出手段は、
前記内燃機関の燃焼終了時点前の所定の時期を経過した後における前記特定情報取得手段で取得される前記熱発生量情報値を、前記熱発生量を求めるための前記計算に使用する数値から除外する除外手段を、
含むことを特徴とする。
前記内燃機関の燃焼終了時期が所定時期よりも遅い又は遅くなるおそれがあるか否かを判定する判定手段を備え、
前記制御手段は、前記燃焼終了時期が前記所定時期よりも遅い又は遅くなるおそれがあると前記判定手段が判定したときに、前記熱発生量取得手段で求めた前記熱発生量を利用して前記内燃機関の制御を行うことを特徴とする。
前記内燃機関の燃焼終了時期が所定時期よりも遅い又は遅くなるおそれがあると前記判定手段が判定する場合とは、前記内燃機関の遅角が所定値以上である場合、前記内燃機関が触媒暖機運転中である場合、前記内燃機関におけるEGR(Exhaust Gas Recirculation)の量が所定量以上である場合および前記内燃機関がリーン燃焼を行っている場合のうち少なくとも1つの場合を含むことを特徴とする。
前記制御手段は、前記推定手段で推定した前記熱発生量を利用して前記内燃機関の燃焼時の空燃比を検出する空燃比検出手段と、前記推定手段で推定した前記熱発生量を利用して前記内燃機関の燃料の燃料性状を検出する性状検出手段と、のうち少なくとも一方を含むことを特徴とする。
[実施の形態1の構成]
図1は、本発明の実施の形態1にかかる内燃機関の制御装置の構成を示す図である。本実施形態にかかる制御装置は、車両等の移動体、具体的には自動車に搭載される内燃機関の制御に好適である。
図2乃至4は、本発明の実施の形態1にかかる制御装置の動作を説明するための図である。熱発生量は、燃焼開始時点における熱量と燃焼終了時点における熱量との間の変化量(差分)に基づいて求めることができる。なお、以下、便宜上、燃焼開始時点における熱量と燃焼終了時点における熱量との差分を、「総熱発生量」とも称し、符号Qで表すこともある。従来の熱発生量算定手法においては、燃焼終了時点を迎えたときの筒内圧センサ出力値等を利用して、燃焼終了時期の熱発生量を検出している。
MFB=(PθVθ κ-Pθ0Vθ0 κ)/(PθfVθf κ-Pθ0Vθ0 κ)・・・(1)
但し、上記(1)式において、Pθ0およびVθ0は、それぞれクランク角度θが所定の燃焼開始時期θ0である場合の筒内圧Pおよび筒内容積Vであり、PθfおよびVθfは、それぞれクランク角度θが所定の燃焼終了時期θfである場合の筒内圧Pおよび筒内容積Vである。また、PθおよびVθは、それぞれクランク角度θが任意の値である場合の筒内圧Pおよび筒内容積Vである。κは、比熱比である。
以下、図5を用いて、実施の形態1にかかる内燃機関の制御装置において実行される具体的処理を説明する。図5は、本発明の実施の形態1において演算処理装置20が実行するルーチンのフローチャートである。
図6は、本発明の実施の形態1において得られる効果を説明するための図である。触媒暖機運転における空燃比検出精度について検証した結果を示す。図6には、「PVκmax法」にかかる測定点と、「2*PVκ@CA50適用」にかかる測定点とがそれぞれ示されている。縦軸が、筒内圧センサ(CPS)出力値を用いて推定的に求めた空燃比の値である。「PVκmax法」にかかる測定点は、図5のルーチンのステップS114でも記載したように「Q=ΔPVκ max」という関係から得た熱発生量を利用して、空燃比を検出した結果である。「2*PVκ@CA50適用」にかかる測定点は、実施の形態1にかかる「Q=2×ΔPVκ CA50」という関係に基づいて得た熱発生量を利用して、空燃比を検出した結果である。図6に示すように、触媒暖機運転においても、「2*PVκ@CA50適用」によれば、実際の空燃比に精度良く対応するリニアな特性が得られていることが判る。
筒内圧センサを応用する技術の1つとして、燃焼空燃比を検出する技術がある(例えば、日本特開2006-144643号公報参照)。このような技術によれば、空燃比センサによる従来の空燃比検出手法よりも、リアルタイムかつ正確な空燃比検出が可能となる。しかし、前述したように、燃焼が膨張行程後期~排気行程初期にまで及ぶような場合には、筒内圧センサ出力値に依拠した空燃比検出が困難となる。この点、本実施形態によれば、遅角燃焼条件において生ずる弊害を抑制しつつ、筒内圧センサを利用したリアルタイムかつ正確な空燃比検出を実現することができる。
(1)運転条件を限定しない制御構成が可能
本実施形態によれば、触媒暖機遅角のような場合、すなわち燃焼終了時点が排気弁開弁(EVO、Exhaust Valve Opening)時期付近あるいはそれ以降にずれ込む場合(「過遅角燃焼」)の場合でも、本来発生しうる熱発生量を推定することができる。これにより、運転条件を限定しない制御構成が可能となるという利点がある。
例えば、従来のガソリンエンジンにおける内燃機関制御では、触媒暖機時には空燃比センサが活性化していないため、空燃比フィードバック制御を行うことができない。しかし、本実施形態にかかる手法によれば、触媒暖機領域においても緻密な空燃比フィードバック制御を行うことが可能となり、エミッションの改善が可能となる。結果として全運転領域での空燃比検出が可能となり、空燃比検出機能を筒内圧センサに統合して空燃比センサを削減しうる。その結果、システムコストの削減も可能である。
(2)ノイズの影響が小さい
実施の形態1では、熱発生量相関パラメータとしてPVκを用いている。PVκでは、TDCから離れるほど、Vκによって筒内圧センサ出力に重畳するノイズを増幅することになる。従って、燃焼終了時点がTDCから遠く離れるような遅角燃焼で熱発生量が最大となる点をサーチしようとすると、ノイズの影響を受けやすくなる。
そこで、熱発生量の計算区間を、燃焼重心位置(実施の形態1ではθCA50)までに区切ってもよい。具体的には、演算処理装置20において、PVκの計算区間あるいは使用許可区間を、燃焼重心位置に応じた所定クランク角(実施の形態1ではθCA50)までに制限しても良い。これにより、ノイズの影響を受け難くすることもできる。このような変形例においても、実施の形態1によれば、θCA50までの筒内圧センサ出力値を得ていれば、その後の熱発生量を推定的に求めることができる。
なお、ここで述べた熱発生量の計算区間(PVκの計算区間、あるいは使用許可区間)の限定を行う構成が、前記第5の発明における「除外手段」に相当している。
遅角燃焼は、燃焼期間が長い(つまり、燃焼速度が遅い)。従って、低回転であるほど単位時間あたりに筒内圧センサが燃焼ガスに曝される時間が長くなる。結果として、筒内圧センサに熱歪誤差をもたらす。
一方、燃焼重心位置までであれば、熱歪誤差の影響は比較的小さい。この点、実施の形態1によれば、燃焼重心位置(実施の形態1ではθCA50)までの筒内圧センサ出力値を利用するので、熱歪誤差の悪影響を避けることもできる。
実施の形態2のハードウェア構成、ソフトウェア構成は、実施の形態2にかかる制御装置が図7に示すルーチンを実行可能である点を除き、基本的に実施の形態1の構成と同様とする。以下、重複を避けるために、適宜に説明を省略ないしは簡略化する。
(i)EGR(Exhaust Gas Recirculation)の量が所定量以上である場合
具体的には、EGRバルブ12の開度が所定開度以上であるか否かに基づいて、燃焼終了時期が遅くなるか否か又は遅くなるおそれがあるか否かを判定しても良い。或いは、実際のEGR量を算出し当該EGR量が所定量以上であるか等により、燃焼終了時期が遅くなるか否か又は遅くなるおそれがあるか否かを判定しても良い。その場合、上記ステップS114にかかるΔPVκ maxに基づく熱発生量算出の精度悪化が問題となる程度に燃焼終了時期が遅くなるか否かを、判定するようにしてもよい。
具体的には、現在におけるエンジンの制御空燃比などの各種制御パラメータの情報に基づいて、現在リーン燃焼を行っているか否かの判定ルーチンを実行すればよい。その場合、上記ステップS114にかかるΔPVκ maxに基づく熱発生量算出の精度悪化が問題となる程度に燃焼終了時期が遅くなるか否かを、判定するようにしてもよい。
2 スロットルバルブ
3 吸気圧センサ
4 サージタンク
5 筒内圧センサ
6 スパークプラグ
7 燃料直噴インジェクタ
8 クランク角度センサ
10,11 触媒
12 EGRバルブ
13 EGRクーラ
14 水温センサ
20 演算処理装置
Claims (8)
- 熱発生量情報値として内燃機関の熱発生量又は当該熱発生量と相関を有するパラメータを求める取得手段と、
前記熱発生量情報値の変化率が最大値をとる時期における前記熱発生量情報値の所定倍の値に基づいて、前記時期以後の熱発生量を推定する推定手段と、
前記推定手段で推定した前記熱発生量を利用して、前記内燃機関の制御を行う制御手段と、
を備えることを特徴とする内燃機関の制御装置。 - 前記取得手段は、
前記内燃機関の筒内圧センサの出力を取得するセンサ出力取得手段と、
前記センサ出力取得手段で取得した前記筒内圧センサの出力に基づいて、前記熱発生量又は前記パラメータを求める手段と、
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。 - 前記取得手段が、前記内燃機関の運転中に所定期間ごとに前記熱発生量情報値を求める手段を含み、
前記推定手段は、
前記熱発生量情報値の変化率が最大値をとる時点であるピーク時点を検出または推定によって特定するピーク時点特定手段と、
前記内燃機関の運転中に前記情報取得手段で取得される前記熱発生量情報値のうち、前記ピーク時点特定手段で特定された前記ピーク時点についての値を取得する特定情報取得手段と、
前記特定情報取得手段で取得した前記熱発生量情報値と所定の係数とを用いた計算により、前記ピーク時点以後の前記熱発生量を求める算出手段と、
を含むことを特徴とする請求項1または2に記載の内燃機関の制御装置。 - 前記算出手段は、前記特定情報取得手段で取得した前記ピーク時点についての前記熱発生量情報値を2倍した値に基づいて燃焼終了時期の熱発生量を求める手段を、含むことを特徴とする請求項3に記載の内燃機関の制御装置。
- 前記算出手段は、
前記内燃機関の燃焼終了時点前の所定の時期を経過した後における前記特定情報取得手段で取得される前記熱発生量情報値を、前記熱発生量を求めるための前記計算に使用する数値から除外する除外手段を、
含むことを特徴とする請求項3または4に記載の内燃機関の制御装置。 - 前記内燃機関の燃焼終了時期が所定時期よりも遅い又は遅くなるおそれがあるか否かを判定する判定手段を備え、
前記制御手段は、前記燃焼終了時期が前記所定時期よりも遅い又は遅くなるおそれがあると前記判定手段が判定したときに、前記熱発生量取得手段で求めた前記熱発生量を利用して前記内燃機関の制御を行うことを特徴とする請求項1乃至5のいずれか1項に記載の内燃機関の制御装置。 - 前記内燃機関の燃焼終了時期が所定時期よりも遅い又は遅くなるおそれがあると前記判定手段が判定する場合とは、前記内燃機関の遅角が所定値以上である場合、前記内燃機関が触媒暖機運転中である場合、前記内燃機関におけるEGR(Exhaust Gas Recirculation)の量が所定量以上である場合および前記内燃機関がリーン燃焼を行っている場合のうち少なくとも1つの場合を含む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。
- 前記制御手段は、前記推定手段で推定した前記熱発生量を利用して前記内燃機関の燃焼時の空燃比を検出する空燃比検出手段と、前記推定手段で推定した前記熱発生量を利用して前記内燃機関の燃料の燃料性状を検出する性状検出手段と、のうち少なくとも一方を含むことを特徴とする請求項1乃至7のいずれか1項に記載の内燃機関の制御装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112010005500.9T DE112010005500B4 (de) | 2010-04-19 | 2010-04-19 | Steuervorrichtung für eine Brennkraftmaschine |
PCT/JP2010/056946 WO2011132253A1 (ja) | 2010-04-19 | 2010-04-19 | 内燃機関の制御装置 |
US13/002,228 US8831856B2 (en) | 2010-04-19 | 2010-04-19 | Control apparatus for internal combustion engine using estimated quantity of heat generated |
JP2010540980A JP4893857B2 (ja) | 2010-04-19 | 2010-04-19 | 内燃機関の制御装置 |
CN201080001991.5A CN102439280B (zh) | 2010-04-19 | 2010-04-19 | 内燃机的控制装置 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2010/056946 WO2011132253A1 (ja) | 2010-04-19 | 2010-04-19 | 内燃機関の制御装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011132253A1 true WO2011132253A1 (ja) | 2011-10-27 |
Family
ID=44833814
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2010/056946 WO2011132253A1 (ja) | 2010-04-19 | 2010-04-19 | 内燃機関の制御装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US8831856B2 (ja) |
JP (1) | JP4893857B2 (ja) |
CN (1) | CN102439280B (ja) |
DE (1) | DE112010005500B4 (ja) |
WO (1) | WO2011132253A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10196974B2 (en) | 2014-04-22 | 2019-02-05 | Toyota Jidosha Kabushiki Kaisha | Heat generation rate waveform calculation device of internal combustion engine and method for calculating heat generation rate waveform |
Families Citing this family (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT513139B1 (de) | 2012-08-17 | 2014-02-15 | Ge Jenbacher Gmbh & Co Og | Verfahren zum Betreiben einer Brennkraftmaschine |
JP2014080918A (ja) * | 2012-10-16 | 2014-05-08 | Toyota Motor Corp | 内燃機関の筒内圧検出装置 |
JP5708674B2 (ja) * | 2013-01-24 | 2015-04-30 | トヨタ自動車株式会社 | 内燃機関の制御装置 |
JP5874686B2 (ja) * | 2013-05-31 | 2016-03-02 | トヨタ自動車株式会社 | 内燃機関の制御装置 |
CN105264206A (zh) * | 2013-06-05 | 2016-01-20 | 丰田自动车株式会社 | 内燃机的控制装置 |
BR112015030516B1 (pt) * | 2013-06-05 | 2021-08-31 | Toyota Jidosha Kabushiki Kaisha | Dispositivo de controle para controlar um estado de combustão de um motor de combustão interna |
RU2628019C2 (ru) * | 2013-06-10 | 2017-08-14 | Тойота Дзидося Кабусики Кайся | Устройство управления двигателем |
JP5979126B2 (ja) * | 2013-12-12 | 2016-08-24 | トヨタ自動車株式会社 | 機関制御装置 |
DE102014007009B4 (de) * | 2014-05-13 | 2018-01-18 | Mtu Friedrichshafen Gmbh | Motorüberwachung mittels zylinderindividueller Drucksensoren vorzüglich bei Magergasmotoren mit gespülter Vorkammer |
US9840998B2 (en) * | 2014-06-10 | 2017-12-12 | Avl Powertrain Engineering, Inc. | System and method for controlling fuel injection characteristics in an engine |
JP6156284B2 (ja) * | 2014-08-07 | 2017-07-05 | トヨタ自動車株式会社 | 内燃機関の燃焼制御装置 |
US10012155B2 (en) | 2015-04-14 | 2018-07-03 | Woodward, Inc. | Combustion pressure feedback based engine control with variable resolution sampling windows |
GB201619855D0 (en) | 2016-11-24 | 2017-01-11 | Maersk Olie & Gas | Cap for a hydrocarbon production well and method of use |
US10934965B2 (en) | 2019-04-05 | 2021-03-02 | Woodward, Inc. | Auto-ignition control in a combustion engine |
JP7431512B2 (ja) * | 2019-05-23 | 2024-02-15 | 日立Astemo株式会社 | 内燃機関制御装置 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004100567A (ja) * | 2002-09-09 | 2004-04-02 | Toyota Motor Corp | 内燃機関の燃料噴射制御装置 |
JP2006144643A (ja) * | 2004-11-18 | 2006-06-08 | Toyota Motor Corp | 内燃機関の制御装置および空燃比算出方法 |
JP2008025406A (ja) * | 2006-07-19 | 2008-02-07 | Toyota Motor Corp | 内燃機関の制御装置 |
Family Cites Families (28)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3736430A1 (de) * | 1987-10-28 | 1989-05-11 | Bosch Gmbh Robert | Verfahren zur regelung des zuendwinkels bei einer brennkraftmaschine |
JP2609892B2 (ja) * | 1988-02-22 | 1997-05-14 | マツダ株式会社 | エンジンの燃焼制御装置 |
US4976241A (en) * | 1988-10-13 | 1990-12-11 | Mitsubishi Jidosha Kogyo Kabushiki Kaisha | Method for determining combustion condition in spark ignition internal combustion engine and combustion condition control device |
US5067463A (en) * | 1990-02-26 | 1991-11-26 | Barrack Technology Limited | Method and apparatus for operating an engine |
US5544635A (en) * | 1993-11-12 | 1996-08-13 | Cosmo Research Institute | Spark-ignition engine and a method of adaptive control on the ignition timing thereof |
US6089077A (en) * | 1997-06-26 | 2000-07-18 | Cooper Automotive Products, Inc. | Mass fraction burned and pressure estimation through spark plug ion sensing |
JP4250856B2 (ja) * | 2000-05-24 | 2009-04-08 | 三菱自動車工業株式会社 | 筒内噴射型内燃機関 |
JP3873580B2 (ja) * | 2000-06-15 | 2007-01-24 | 日産自動車株式会社 | 圧縮自己着火式内燃機関 |
AT5650U1 (de) * | 2001-10-02 | 2002-09-25 | Avl List Gmbh | Verfahren zur ermittlung der lage einer verbrennung |
DE10159017A1 (de) | 2001-12-01 | 2003-06-18 | Bosch Gmbh Robert | Verfahren und Vorrichtung zur Steuerung einer Brennkraftmaschine |
EP1538325B1 (en) * | 2002-09-09 | 2013-08-21 | Toyota Jidosha Kabushiki Kaisha | Control device of internal combustion engine |
JP4281445B2 (ja) * | 2003-07-08 | 2009-06-17 | トヨタ自動車株式会社 | 内燃機関の制御装置および内燃機関の制御方法 |
JP4391774B2 (ja) * | 2003-07-17 | 2009-12-24 | トヨタ自動車株式会社 | 内燃機関の制御装置および内燃機関の制御方法 |
US7624718B2 (en) * | 2004-02-02 | 2009-12-01 | Yamaha Hatsudoki Kabushiki Kaisha | Engine control system, vehicle having the same, method for calculating combustion center of gravity, and method for controlling engine |
JP4380604B2 (ja) * | 2005-07-29 | 2009-12-09 | トヨタ自動車株式会社 | 内燃機関の制御装置 |
JP2007113396A (ja) | 2005-10-18 | 2007-05-10 | Denso Corp | 内燃機関の燃焼状態判定装置 |
JP2007120392A (ja) | 2005-10-27 | 2007-05-17 | Toyota Motor Corp | 内燃機関の空燃比制御装置 |
DE102005054737A1 (de) * | 2005-11-17 | 2007-05-24 | Robert Bosch Gmbh | Verfahren zum Betreiben einer Brennkraftmaschine |
JP4314585B2 (ja) * | 2006-06-16 | 2009-08-19 | 株式会社デンソー | 内燃機関の制御装置 |
JP2008069713A (ja) * | 2006-09-14 | 2008-03-27 | Toyota Motor Corp | 内燃機関の燃焼制御装置 |
JP4753854B2 (ja) * | 2006-12-12 | 2011-08-24 | ヤマハ発動機株式会社 | エンジンシステムおよびそれを備える車両 |
US7788017B2 (en) * | 2006-12-27 | 2010-08-31 | Denso Corporation | Engine control, fuel property detection and determination apparatus, and method for the same |
JP4882787B2 (ja) * | 2007-02-19 | 2012-02-22 | トヨタ自動車株式会社 | 内燃機関の制御装置 |
JP4784868B2 (ja) * | 2007-03-02 | 2011-10-05 | トヨタ自動車株式会社 | 内燃機関の制御装置 |
JP5056290B2 (ja) * | 2007-09-12 | 2012-10-24 | トヨタ自動車株式会社 | ディーゼルエンジンにおける燃料のセタン価判別装置 |
JP4893553B2 (ja) * | 2007-09-25 | 2012-03-07 | トヨタ自動車株式会社 | 内燃機関の制御装置 |
JP5167928B2 (ja) * | 2008-04-24 | 2013-03-21 | 株式会社デンソー | 燃焼制御装置 |
US8150596B2 (en) * | 2008-06-02 | 2012-04-03 | GM Global Technology Operations LLC | Fuel ignition quality detection |
-
2010
- 2010-04-19 DE DE112010005500.9T patent/DE112010005500B4/de not_active Expired - Fee Related
- 2010-04-19 US US13/002,228 patent/US8831856B2/en not_active Expired - Fee Related
- 2010-04-19 WO PCT/JP2010/056946 patent/WO2011132253A1/ja active Application Filing
- 2010-04-19 JP JP2010540980A patent/JP4893857B2/ja not_active Expired - Fee Related
- 2010-04-19 CN CN201080001991.5A patent/CN102439280B/zh not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004100567A (ja) * | 2002-09-09 | 2004-04-02 | Toyota Motor Corp | 内燃機関の燃料噴射制御装置 |
JP2006144643A (ja) * | 2004-11-18 | 2006-06-08 | Toyota Motor Corp | 内燃機関の制御装置および空燃比算出方法 |
JP2008025406A (ja) * | 2006-07-19 | 2008-02-07 | Toyota Motor Corp | 内燃機関の制御装置 |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10196974B2 (en) | 2014-04-22 | 2019-02-05 | Toyota Jidosha Kabushiki Kaisha | Heat generation rate waveform calculation device of internal combustion engine and method for calculating heat generation rate waveform |
Also Published As
Publication number | Publication date |
---|---|
JP4893857B2 (ja) | 2012-03-07 |
JPWO2011132253A1 (ja) | 2013-07-18 |
CN102439280A (zh) | 2012-05-02 |
US8831856B2 (en) | 2014-09-09 |
US20120046850A1 (en) | 2012-02-23 |
DE112010005500T5 (de) | 2013-04-11 |
DE112010005500B4 (de) | 2021-08-26 |
CN102439280B (zh) | 2014-10-22 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP4893857B2 (ja) | 内燃機関の制御装置 | |
JP5874686B2 (ja) | 内燃機関の制御装置 | |
JP4179192B2 (ja) | 内燃機関の燃焼状態検出装置 | |
JP5758862B2 (ja) | 内燃機関の筒内圧検出装置 | |
JP4605060B2 (ja) | 内燃機関の制御装置 | |
JP6006228B2 (ja) | 筒内圧センサの異常診断装置及びこれを備えた筒内圧センサの感度補正装置 | |
JP5331613B2 (ja) | 内燃機関の筒内ガス量推定装置 | |
WO2014061405A1 (ja) | 内燃機関の筒内圧検出装置 | |
JP2011241727A (ja) | 内燃機関の異常検出装置および内燃機関の制御装置 | |
JP5949075B2 (ja) | 内燃機関の制御装置 | |
JP2010127102A (ja) | 筒内圧センサの異常判定装置 | |
JP2015197074A (ja) | 内燃機関の制御装置 | |
JP4830986B2 (ja) | 内燃機関の制御装置 | |
US20120303240A1 (en) | Method for operating an internal combustion engine | |
JP6280087B2 (ja) | 内燃機関のエンジントルク推定装置 | |
GB2491110A (en) | Method of operating an internal combustion engine having crankshaft position sensor correction means | |
JP2010127229A (ja) | 内燃機関の制御装置 | |
JP2008180174A (ja) | 内燃機関の制御装置 | |
JP4345723B2 (ja) | 内燃機関の図示平均有効圧の推定方法 | |
JP5370207B2 (ja) | 内燃機関の制御装置 | |
JP5240208B2 (ja) | 内燃機関の制御装置 | |
JP5760924B2 (ja) | 内燃機関の筒内圧推定装置 | |
JP2012082712A (ja) | 内燃機関の失火検出装置 | |
JP2007002685A (ja) | 内燃機関の点火時期制御装置 | |
JP2023122432A (ja) | エンジン制御システム |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 201080001991.5 Country of ref document: CN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2010540980 Country of ref document: JP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13002228 Country of ref document: US |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 10850198 Country of ref document: EP Kind code of ref document: A1 |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120100055009 Country of ref document: DE Ref document number: 112010005500 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 10850198 Country of ref document: EP Kind code of ref document: A1 |