JP2017223189A - Control apparatus for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an internal combustion engine control apparatus capable of accurately estimating an EGR ratio of in-cylinder gas while appropriately eliminating an influence of a deviation in an air-fuel ratio even in a case where an actual air-fuel ratio of the in-cylinder gas is deviated from a designed air-fuel ratio.SOLUTION: An internal combustion engine control apparatus performs: obtaining an actual fuel injection amount QFINJ_ACT injected into a cylinder 3a (step 25 in FIG. 4); calculating, as reference in-cylinder pressure P_REF, in-cylinder pressure generated at a given reference crank angle CA_REF amid a compression stage on the basis of a specific heat ratio of the in-cylinder gas in accordance with an actual fuel injection amount QFINJ_ACT under a condition where no external EGR gas due to an exhaust gas return exists in the in-cylinder gas (step 6 in FIG. 3, and FIG. 4); and estimating an EGR ratio R_EGR of the in-cylinder gas on the basis of a pressure difference ΔP between the reference in-cylinder pressure P_REF and detected in-cylinder pressure P_CPS detected at the reference crank angle CA_REF (step 10-11 in FIG. 3).SELECTED DRAWING: Figure 8

Description

  The present invention relates to a control device for an internal combustion engine that estimates an EGR rate of in-cylinder gas filled in a cylinder using in-cylinder pressure detected by an in-cylinder pressure sensor.

  As this type of conventional control device, for example, one disclosed in Patent Document 1 is known. In this control device, assuming that the change in state of the combustion gas during the expansion stroke is adiabatic expansion and the specific heat ratio κexp of the combustion gas is approximated by the polytropic index, κexp = − (lnP2-lnP1) / (lnV2-lnV1) Is calculated by P1 and P2 are in-cylinder pressures detected at two points during the expansion stroke, and V1 and V2 are in-cylinder volumes V1 and V2 at two points. Further, assuming that a certain relationship independent of the air-fuel ratio is established between the specific heat ratio κexp of the combustion gas and the EGR rate, this relationship is mapped in advance and the specific heat ratio of the combustion gas calculated as described above By searching this map according to κexp, the EGR rate is estimated.

Japanese Patent No. 5263184

  In the conventional control device described above, the specific heat ratio of the combustion gas is calculated based on the change in the state of the combustion gas during the expansion stroke. However, the state of combustion gas such as temperature and pressure changes depending on the combustion state in the cylinder, so it is unstable, and the specific heat ratio of combustion gas is further influenced by temperature, so it is very inefficient. It is stable. For this reason, in the conventional method of calculating the specific heat ratio based on the in-cylinder pressure detected at two points during the expansion stroke, it is difficult to stably and accurately calculate the specific heat ratio. Therefore, based on the calculated specific heat ratio. The EGR rate cannot be estimated with high accuracy.

  For this reason, it is preferable to estimate the EGR rate based on the specific heat ratio of the in-cylinder gas before combustion, in which the temperature and pressure are stable compared to the combustion gas. However, since the specific heat ratio of the in-cylinder gas is affected by both the EGR rate and the air-fuel ratio, for example, when the actual air-fuel ratio deviates from the assumed air-fuel ratio, the EGR rate is accurately set. Cannot be estimated.

  The present invention has been made to solve the above-described problems. Even when the actual air-fuel ratio of the in-cylinder gas deviates from the assumed air-fuel ratio, the influence of the air-fuel ratio deviation is affected. It is an object of the present invention to provide a control device for an internal combustion engine that can accurately estimate the EGR rate of in-cylinder gas while appropriately eliminating the exhaust gas.

  In order to achieve the above object, the invention according to claim 1 is a control device for an internal combustion engine that estimates the EGR rate R_EGR of the in-cylinder gas charged in the cylinder 3a, wherein the pressure in the cylinder 3a is controlled by the cylinder. An in-cylinder pressure sensor 51 that detects the internal pressure PCYL, and an actual fuel injection amount acquisition means that acquires the actual fuel amount injected into the cylinder 3a as an actual fuel injection amount QFINJ_ACT (in the embodiment (hereinafter the same in this section) ECU 2) Based on the characteristic of the specific heat ratio of the in-cylinder gas according to the obtained actual fuel injection amount QFINJ_ACT, under the condition that the external EGR gas due to exhaust gas recirculation does not exist in the in-cylinder gas, in step 25) of FIG. Thus, the reference cylinder pressure calculating means for calculating the pressure in the cylinder 3a generated at the predetermined reference crank angle CA_REF during the compression stroke as the reference cylinder pressure P_REF. ECU 2, step 6 in FIG. 3, FIG. 4) and the pressure difference ΔP between the calculated reference in-cylinder pressure P_REF and the detected in-cylinder pressure P_CPS detected by the in-cylinder pressure sensor 51 at the reference crank angle CA_REF. EGR rate estimating means (ECU 2, steps 10 to 11 in FIG. 3) for estimating the EGR rate R_EGR.

  In the control device for an internal combustion engine of the present invention, the cylinder pressure (in-cylinder pressure) is detected by the cylinder pressure sensor, and the cylinder pressure predicted to be generated at a predetermined reference crank angle during the compression stroke is used as the cylinder reference pressure. calculate. Then, based on the pressure difference between the reference in-cylinder pressure and the detected in-cylinder pressure detected by the in-cylinder pressure sensor at the reference crank angle, the EGR rate R_EGR of the in-cylinder gas is estimated.

  Further, according to the present invention, the actual fuel amount injected into the cylinder is acquired as the actual fuel injection amount, and the calculation of the reference in-cylinder pressure is performed in the in-cylinder gas by the external EGR gas due to exhaust gas recirculation. This is performed based on the characteristic of the specific heat ratio of the in-cylinder gas according to the acquired actual fuel injection amount. If the air-fuel ratio of the in-cylinder gas deviates from the assumed air-fuel ratio due to the change in the actual fuel injection amount, the specific heat ratio of the in-cylinder gas changes due to the increase or decrease in the ratio of the fuel component. Thus, the in-cylinder pressure during the compression stroke changes. For example, when the air-fuel ratio shifts to the rich side, the specific heat ratio of the in-cylinder gas decreases due to the increase in the ratio of the fuel component, so that the in-cylinder pressure decreases and the air-fuel ratio shifts to the lean side. The reverse of the above. As a result, the detected in-cylinder pressure also changes, and the accuracy of estimating the EGR rate based on the pressure difference from the reference in-cylinder pressure is reduced.

  In contrast, according to the present invention, as described above, the calculation of the reference in-cylinder pressure is performed based on the characteristic of the specific heat ratio of the in-cylinder pressure gas according to the acquired actual fuel injection amount. The change in the in-cylinder pressure due to the deviation of the air-fuel ratio accompanying the change in can be reflected in the reference in-cylinder pressure. As a result, the pressure difference between the reference in-cylinder pressure and the detected in-cylinder pressure does not include the change in the in-cylinder pressure due to the deviation of the air-fuel ratio, and reflects only the pressure difference due to the EGR rate. Therefore, based on this pressure difference, the EGR rate of the in-cylinder gas can be accurately estimated while appropriately eliminating the influence of the air-fuel ratio shift.

  According to a second aspect of the present invention, in the control device for an internal combustion engine according to the first aspect, the reference in-cylinder pressure calculating means has no external EGR gas in the in-cylinder gas and the air-fuel ratio of the in-cylinder gas is the theoretical sky. Basic value calculating means (ECU 2, step 23 in FIG. 4, FIG. 5) for calculating the pressure in the cylinder generated at the reference crank angle CA_REF as the basic value P_REF_B of the reference in-cylinder pressure P_REF under the condition of the fuel ratio, Reference fuel injection amount calculation means for calculating, as a reference fuel injection amount QFINJ_REF, a fuel injection amount when the air-fuel ratio of the in-cylinder gas becomes the stoichiometric air-fuel ratio under the condition that no external EGR gas is present in the internal gas. ECU 2, step 24) of FIG. 4, and based on the difference between the calculated reference fuel injection amount QFINJ_REF and the actual fuel injection amount QFINJ_ACT (injection amount difference ΔQF). And correction amount calculation means (ECU2, steps 26 and 27 in FIG. 4) for calculating the correction amount P_QFM of the reference in-cylinder pressure P_REF, and by adding the correction amount P_QFM to the basic value P_REF_B, It is characterized by calculating P_REF (step 28 in FIG. 4).

  According to this configuration, the calculation of the reference in-cylinder pressure is performed as follows. First, the basic value of the reference in-cylinder pressure is calculated. This basic value is the in-cylinder pressure generated at the reference crank angle under the condition of in-cylinder gas in which no external EGR gas is present and the air-fuel ratio is the stoichiometric air-fuel ratio, that is, the reference in-cylinder pressure corresponding to the stoichiometric air-fuel ratio. It corresponds to. Next, a reference fuel injection amount is calculated. The reference fuel injection amount is a fuel injection amount when the air-fuel ratio of the in-cylinder gas becomes the stoichiometric air-fuel ratio under the condition that no external EGR gas is present in the in-cylinder gas. For this reason, the difference between the calculated reference fuel injection amount and the actual fuel injection amount represents a deviation of the actual fuel injection amount from the fuel amount equivalent to the theoretical air-fuel ratio, and accordingly, the deviation of the air-fuel ratio from the theoretical air-fuel ratio. Represent.

  Then, a correction amount for the reference in-cylinder pressure is calculated based on the difference between the reference fuel injection amount and the actual fuel injection amount, and the calculated correction amount is added to the basic value corresponding to the theoretical air-fuel ratio, thereby obtaining a reference value. In-cylinder pressure is calculated. As a result, the reference in-cylinder pressure can be accurately calculated while appropriately reflecting the influence of the change in in-cylinder pressure due to the deviation of the air-fuel ratio. Therefore, the EGR rate is estimated based on the pressure difference between the reference in-cylinder pressure and the detected in-cylinder pressure. Furthermore, it can be performed with high accuracy.

  According to a third aspect of the present invention, in the control apparatus for an internal combustion engine according to the second aspect, an intake pressure detecting means (intake pressure sensor 56) for detecting the pressure of the intake air taken into the cylinder 3a as the intake pressure PBA, and the internal combustion engine A rotation speed detection means (crank angle sensor 52) for detecting the rotation speed NE of the engine 3; the reference fuel injection amount calculation means is based on the detected intake pressure PBA and the rotation speed NE of the internal combustion engine 3; Then, a reference fuel injection amount QFINJ_REF is calculated (step 24 in FIG. 4).

  The combination of the intake pressure and the rotational speed of the internal combustion engine favorably represents the amount of gas sucked into the cylinder. Therefore, the calculation of the reference fuel injection amount is simplified by calculating the reference fuel injection amount according to the detected intake pressure and the rotational speed of the internal combustion engine under the condition that no external EGR is present in the in-cylinder gas. And can be performed accurately.

  According to a fourth aspect of the present invention, in the control device for an internal combustion engine according to the second or third aspect, the correction amount calculating means calculates a difference (injection amount difference ΔQF) between the reference fuel injection amount QFINJ_REF and the actual fuel injection amount QFINJ_ACT. The correction amount P_QFM of the reference in-cylinder pressure P_REF is calculated by multiplying the correction coefficient KF (step 27 in FIG. 4).

  As will be described later, under conditions where the EGR rate is constant, the in-cylinder pressure in the compression stroke increases or decreases in a linear relationship with the fuel injection amount. Therefore, by setting the inclination of the in-cylinder pressure with respect to the fuel injection amount as a correction coefficient, and multiplying the difference between the reference fuel injection amount and the actual fuel injection amount by this correction coefficient, the correction amount of the reference in-cylinder pressure can be easily and accurately performed. It can be calculated well.

1 is a diagram schematically showing a configuration of an internal combustion engine to which the present invention is applied. It is a block diagram which shows schematic structure of a control apparatus. It is a flowchart which shows the estimation process of an EGR rate. It is a flowchart which shows the subroutine of the calculation process of a reference | standard cylinder pressure. It is a figure which shows the reference in-cylinder pressure map used for calculation of the basic value of a reference in-cylinder pressure, and its input-output relationship. It is a figure which shows the relationship between the pressure difference of a reference | standard cylinder pressure-detection cylinder pressure, and an EGR rate. It is a figure which shows the EGR coefficient map used for calculation of an EGR coefficient, and its input-output relationship. It is a figure for demonstrating the correction method of a reference | standard in-cylinder pressure while showing an example of the relationship between an actual fuel injection amount and an EGR rate, and the in-cylinder pressure obtained in a compression stroke. It is a timing chart which shows the operation example by this embodiment with a comparative example. It is a flowchart which shows the control processing of the ignition timing using an EGR rate.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. As shown in FIG. 1, an internal combustion engine (hereinafter referred to as “engine”) 3 to which the present invention is applied is, for example, a gasoline engine having four cylinders 3a, and is mounted as a power source in a vehicle (not shown). .

  Each cylinder 3a of the engine 3 is provided with a fuel injection valve 4 and a spark plug 5 so as to face a combustion chamber (not shown) of the cylinder 3a. The fuel injection valve 4 is a direct injection type that directly injects fuel into the combustion chamber. The fuel injection amount by the fuel injection valve 4 and the ignition timing IGLOG of the spark plug 5 are controlled by a control signal from an electronic control unit (hereinafter referred to as “ECU”) 2 (see FIG. 2).

  In the embodiment, “in-cylinder gas” refers to all the gas charged in the cylinder 3a and used for combustion. When the external EGR or internal EGR described later is not executed, the fuel and air It corresponds to the air-fuel mixture and, when being executed, further includes an external EGR gas and an internal EGR gas.

  Each cylinder 3a is provided with an in-cylinder pressure sensor 51 for detecting an internal pressure (in-cylinder pressure). In this embodiment, the in-cylinder pressure sensor 51 is integrated with the fuel injection valve 4 and is not shown, but faces the combustion chamber and amplifies the signal from the pressure detection element that picks up the in-cylinder pressure and the pressure detection element. In addition, an output amplifier circuit and the like are integrally assembled with the fuel injection valve 4. A detection signal representing the in-cylinder pressure PCYL detected by the in-cylinder pressure sensor 51 is input to the ECU 2.

  The engine 3 also includes a variable intake phase mechanism 11, a variable exhaust phase mechanism 12, a turbocharger 13, an EGR device 14, and the like.

  The variable intake phase mechanism 11 changes the relative phase (hereinafter referred to as “intake phase”) CAIN of an intake valve (both not shown) with respect to the crankshaft of the engine 3 in a stepless manner. 11a (see FIG. 2) and the like. The intake phase control motor 11a rotates the intake camshaft (not shown) with respect to the crankshaft in response to a control signal from the ECU 2, and changes the relative angle between the two, thereby making the intake phase CAIN stepless. change.

  Similarly, the variable exhaust phase mechanism 12 changes the relative phase (hereinafter referred to as “exhaust phase”) CAEX of an exhaust valve (not shown) with respect to the crankshaft continuously, and the exhaust phase control motor 12a ( Etc.). The exhaust phase control motor 12a rotates the exhaust camshaft (not shown) with respect to the crankshaft in response to a control signal from the ECU 2, and changes the relative angle between the two, thereby making the exhaust phase CAEX stepless. change.

  The variable intake phase mechanism 11 and the variable exhaust phase mechanism 12 control the timing of opening and closing the intake valve and the exhaust valve by changing the intake phase CAIN and the exhaust phase CAEX, respectively, and valve overflow between the intake valve and the exhaust valve. Used to control internal EGR by wrapping.

  The turbocharger 13 includes a compressor 21 provided in the intake passage 6 and a turbine 23 provided in the exhaust passage 7 and integrally connected to the compressor 21 via a shaft 22. The turbine 23 is driven by the exhaust gas flowing through the exhaust passage 7, and the compressor 21 rotates integrally therewith, whereby the intake air is supercharged.

  In the intake passage 6, an intake throttle valve 25, a compressor 21 of the turbocharger 13, an intercooler 26 for cooling intake air whose temperature has been increased by supercharging, and a throttle valve 27 are provided in this order from the upstream side. The intake throttle valve 25 generates a negative pressure for introducing the external EGR gas downstream thereof, and its opening degree is controlled via the LP actuator 25a in accordance with a control signal from the ECU 2.

  The throttle valve 27 is disposed upstream of the intake manifold 6 a in the intake passage 6. The opening degree of the throttle valve 27 is controlled via the TH actuator 27a in accordance with a control signal from the ECU 2, thereby controlling the in-cylinder gas amount sucked into the cylinder 3a.

  A three-way catalyst 28 is provided downstream of the turbine 23 in the exhaust passage 7. In the active state, the three-way catalyst 28 purifies the exhaust gas by oxidizing HC and CO in the exhaust gas and reducing NOx.

  The EGR device 14 recirculates a part of the exhaust gas discharged from the cylinder 3a into the exhaust passage 7 to the intake passage 6 as an external EGR gas via the EGR passage 41. As shown in FIG. 1, the EGR passage 41 is connected downstream of the turbine 23 and the three-way catalyst 28 in the exhaust passage 7 and between the compressor 21 and the intake throttle valve 25 in the intake passage 6. With this configuration, the external EGR gas has a relatively low pressure because the exhaust gas is taken out after the exhaust gas has worked on the turbine 23. That is, the EGR device 14 is configured as a so-called low pressure EGR device.

  In the middle of the EGR passage 41, an EGR valve 42 and an EGR cooler 43 for cooling the external EGR gas are provided. The opening degree of the EGR valve 42 is controlled via the EGR actuator 42a in accordance with a control signal from the ECU 2, thereby controlling the external EGR gas amount.

  Further, the engine 3 is provided with various sensors as described below in addition to the above-described in-cylinder pressure sensor 51 in order to detect the operating state, and these detection signals are input to the ECU 2 ( (See FIG. 2).

  The crank angle sensor 52 outputs a CRK signal and a TDC signal, which are pulse signals, for each predetermined crank angle as the crankshaft rotates. The CRK signal is output every predetermined crank angle (for example, 0.5 degrees). The ECU 2 calculates the engine speed (hereinafter referred to as “engine speed”) NE of the engine 3 based on the CRK signal.

  Further, the TDC signal is a signal indicating that in any cylinder 3a, the piston (not shown) of the engine 3 is at a predetermined crank angle position near the top dead center (intake TDC) at the start of the intake stroke. Yes, when the engine 3 has four cylinders as in this embodiment, it is output every 180 degrees of crank angle. The ECU 2 calculates a crank angle CA based on the output timing of the TDC signal for each cylinder 3a according to the TDC signal and the CRK signal, and a predetermined crank angle (for example, 30) with respect to the calculated crank angle CA. Crank angle stage FISTG (= 0-23) is calculated and assigned for each degree.

  The intake camshaft to which the variable intake phase mechanism 11 is attached and the exhaust camshaft to which the variable exhaust phase mechanism 12 is attached are provided with an intake phase sensor 53 and an exhaust phase sensor 54, respectively. The intake phase sensor 53 outputs a CAMIN signal that is a pulse signal at every predetermined cam angle (for example, 0.5 degrees) as the intake camshaft rotates. The ECU 2 calculates the intake phase CAIN based on the CAMIN signal and the CRK signal. Similarly, the exhaust phase sensor 54 outputs a CAMEX signal at every predetermined cam angle (for example, 0.5 degrees) as the exhaust camshaft rotates. The ECU 2 calculates the exhaust phase CAEX based on the CAMEX signal and the CRK signal.

  Further, in the intake passage 6, an air flow sensor 55 is provided on the upstream side of the intake throttle valve 25, and an intake pressure sensor 56 and an intake air temperature sensor 57 are provided in the intake chamber 6 b on the downstream side of the throttle valve 27. The air flow sensor 55 detects the amount (intake air amount) GAIR of air (fresh air) sucked into the cylinder 3a, the intake pressure sensor 56 detects the intake pressure PBA as an absolute pressure, and the intake air temperature sensor 57 An intake air temperature (intake air temperature) TA including the external EGR gas sucked into the cylinder 3a is detected.

  A LAF sensor 58 is provided between the turbine 23 and the three-way catalyst 28 in the exhaust passage 7. The LAF sensor 58 continuously detects the oxygen concentration in the exhaust gas flowing into the three-way catalyst 28 in a wide air-fuel ratio region including the stoichiometric air-fuel ratio, and outputs a detection signal thereof. The ECU 2 calculates an exhaust gas equivalent ratio (hereinafter referred to as “actual equivalent ratio”) KACT based on the detection signal.

  Further, the water temperature sensor 59 outputs a detection signal indicating the temperature (hereinafter referred to as “engine water temperature”) TW of cooling water for cooling the engine 3, and the fuel pressure sensor 60 is a pressure of fuel injected from the fuel injection valve 4 ( A detection signal representing the fuel pressure PF is output, and the accelerator opening sensor 61 outputs a detection signal representing the depression amount (hereinafter referred to as “accelerator opening”) AP of an accelerator pedal (not shown) of the vehicle.

  The ECU 2 is composed of a microcomputer including a CPU, a RAM, a ROM, an I / O interface (all not shown), and the like. The ECU 2 executes overall engine control including control of the fuel injection amount of the fuel injection valve 4 and the ignition timing IGLOG of the spark plug 5 in accordance with the detection signals of the various sensors described above. Further, particularly in the present embodiment, the ECU 2 executes an estimation process for estimating the EGR rate R_EGR of the in-cylinder gas using the in-cylinder pressure PCYL detected by the in-cylinder pressure sensor 51.

  In the present embodiment, the ECU 2 corresponds to actual fuel injection amount acquisition means, reference in-cylinder pressure calculation means, EGR rate estimation means, basic value calculation means, reference fuel injection amount calculation means, and correction amount calculation means.

  FIG. 3 shows an estimation process of the EGR rate R_EGR executed by the ECU 2. The EGR rate R_EGR is defined as the ratio of the EGR gas amount to the total amount of in-cylinder gas. This estimation process is basically the same as that disclosed in detail in the application filed by the present applicant (Japanese Patent Application No. 2015-241446), and is characterized by the calculation of the reference in-cylinder pressure therein.

  This process is repeatedly executed for each cylinder 3a at the same cycle (for example, every 30 degrees of crank angle) as the switching cycle of the crank angle stage FISTG described above. In addition, the process directly related to the in-cylinder pressure PCYL detected by the in-cylinder pressure sensor 51 is executed at the same cycle as the CRK signal generation cycle (for example, every 0.5 degrees of crank angle) separately from the present process. For example, the detected in-cylinder pressure PCYL is stored corresponding to the crank angle CA.

  In the estimation process of FIG. 3, first, in step 1 (illustrated as “S1”, the same applies hereinafter), the crank angle stage FISTG reaches a first predetermined value STG1 corresponding to the top dead center (intake TDC) at the start of the intake stroke. Determine whether they are equal. If the determination result is YES, corresponding to immediately after the cylinder 3a has shifted to the intake stroke, an intake-related parameter is acquired (step 2). Specifically, the detected intake air temperature TA and engine water temperature TW and the calculated intake air phase CAIN and exhaust gas phase CAEX are read out as the intake-related parameters and stored in a predetermined area of the ECU 2 RAM, and this process is terminated. To do.

  When the determination result in step 1 is NO, it is determined whether or not the crank angle stage FISTG is equal to a second predetermined value STG2 corresponding to the bottom dead center (compression BDC) at the start of the compression stroke (step 3). . When the determination result is YES, which corresponds to immediately after the cylinder 3a has shifted to the compression stroke, the compression-related parameters are acquired (step 4). Specifically, the detected intake pressure PBA and in-cylinder pressure PCYL are read out as compression-related parameters, acquired as the compression start intake pressure PBAC and the compression start in-cylinder pressure PCYLC, respectively, and the detected engine speed NE and The ignition timing IGLOG set at that time is read out and stored in a predetermined area of the ECU 2 RAM.

  Next, a reference crank angle CA_REF is set (step 5). This reference crank angle CA_REF predicts the timing immediately before the start of in-cylinder gas combustion, and is represented by the crank angle. In this setting process, a retardation correction amount ΔC_CA is calculated by searching a predetermined map (not shown) according to the compression start intake pressure PBAC and the engine speed NE acquired in step 4, and this The reference crank angle CA_REF is set by subtracting the retard correction amount ΔC_CA from the ignition timing IGLOG acquired in step 4.

  In step 6 following step 5, the reference in-cylinder pressure P_REF is calculated. The reference in-cylinder pressure P_REF is an in-cylinder pressure predicted to be generated at the reference crank angle CA_REF, and is calculated by a subroutine shown in FIG.

  In this process, first, in step 21, the intake valve closing timing (hereinafter referred to as “intake valve closing timing”) IVC is calculated from the intake phase CAIN acquired in step 2. When the intake valve closing timing IVC is set during the compression stroke, it corresponds to the crank angle at the start of compression. Next, by searching a predetermined map (not shown) according to the intake air temperature TA, the intake air phase CAIN, and the exhaust gas phase CAEX acquired in step 2, the initial cylinder that is the temperature in the cylinder 3a at the start of compression. An internal temperature T_STRT is calculated (step 22).

  Next, by searching the reference in-cylinder pressure map shown in FIG. 5 according to the reference crank angle CA_REF set in step 5, the intake valve closing timing IVC, the initial in-cylinder temperature T_STRT, and the compression start intake pressure PBAC, A basic value P_REF_B of the reference in-cylinder pressure is calculated (step 23). This reference in-cylinder pressure map is obtained for various conditions of the above four input parameters under the condition that there is no external EGR gas in the in-cylinder gas and the air-fuel ratio of the in-cylinder gas is the stoichiometric air-fuel ratio. The reference in-cylinder pressure is calculated in advance and mapped based on the temperature characteristics of the specific heat ratio of the internal gas.

  In the next steps 24 to 28, the basic value P_REF_B is corrected. In this correction process, the basic value P_REF_B is corrected according to the actual fuel injection amount (actual fuel injection amount) AFINJ_ACT injected into the cylinder 3a, and the reference in-cylinder pressure P_REF is calculated. FIG. 8 shows the actual fuel injection amount AFINJ_ACT on the X-axis for three different EGR rates (= 0, 10%, 20%) in order to explain the purpose and content of this correction, and the predetermined compression stroke The in-cylinder pressure PCYL at the crank angle is represented on the Y axis.

  As shown in the figure, under the condition that the actual fuel injection amount QFINJ_ACT is constant, the higher the EGR rate, the lower the specific heat ratio, and thus the in-cylinder pressure PCYL further decreases. Further, under the condition where the EGR rate is constant, the specific heat ratio increases as the actual fuel injection amount QFINJ_ACT decreases, and thus the in-cylinder pressure PCYL further increases. The in-cylinder pressure PCYL has a linear relationship with the fuel injection amount QFINJ, and increases and decreases along straight lines A, B, and C having the same inclination when the EGR rate = 0, 10%, and 20%, respectively. .

  A point P0 on the straight line A represents a reference point at which the EGR rate of the cylinder pressure gas = 0 and the air-fuel ratio is the stoichiometric air-fuel ratio. Therefore, the in-cylinder pressure PCYL at the reference point P0 corresponds to the basic value P_REF_B of the reference in-cylinder pressure calculated from the above-described reference in-cylinder pressure map. When the actual fuel injection amount QFINJ_ACT at the reference point P0 is defined as the reference fuel injection amount QFINJ_REF, the coordinates of the reference point P0 are represented by (QFINJ_REF, P_REF_B).

  In the correction processing in steps 24-28, the basic value P_REF_B is corrected according to the actual fuel injection amount QFINJ_ACT, so that the reference in-cylinder pressure P_REF is a value corresponding to the actual fuel injection amount QFINJ_ACT on the straight line A (for example, FIG. 8). P_REF).

  First, in step 24, the reference fuel injection amount QFINJ_REF is calculated by searching a predetermined map (not shown) according to the intake pressure PBA and the engine speed NE. The combination of the intake pressure PBA and the engine speed NE represents the amount of gas sucked into the cylinder 3a, so that the reference fuel injection amount QFINJ_REF can be calculated easily and accurately according to both parameters. .

  Next, the actual fuel injection amount QFINJ_ACT is calculated (step 25). The calculation is performed, for example, by searching a predetermined fuel injection amount characteristic map (not shown) according to the valve opening time T_OUT and the fuel pressure PF set for controlling the fuel injection valve 4.

  Next, the difference between the calculated reference fuel injection amount QFINJ_REF and the actual fuel injection amount QFINJ_ACT is calculated as an injection amount difference ΔQF (step 26), and in step 27, the injection amount difference ΔQF is multiplied by a correction coefficient KF. To calculate the correction amount P_QFM of the reference in-cylinder pressure (see FIG. 8). This correction coefficient KF corresponds to the slope of the straight line A in FIG. Therefore, the calculated reference in-cylinder pressure correction amount P_QFM (= ΔQF · KF) corresponds to the difference between the reference in-cylinder pressure P_REF corresponding to the actual fuel injection amount QFINJ_ACT and the basic value P_REF_B (see FIG. 8). Accordingly, in the next step 28, the reference in-cylinder pressure P_REF corresponding to the actual fuel injection amount QFINJ_ACT is calculated by adding the correction amount P_QFM to the basic value P_REF_B.

  In the next step 29, a heat transfer correction coefficient K_HT is calculated by searching a predetermined map (not shown) according to the engine speed NE and the engine water temperature TW. The heat transfer correction coefficient K_HT is for compensating for the influence of heat exchanged between the cylinder 3a and the outside. Next, the final reference in-cylinder pressure P_REF is calculated by multiplying the reference in-cylinder pressure P_REF calculated in step 28 by the heat transfer correction coefficient K_HT (step 30), and the process of FIG.

  Returning to FIG. 3, in step 7 following the calculation processing of the reference in-cylinder pressure P_REF in step 6, the EGR coefficient C_EGR is calculated, and the processing in FIG. 3 is ended. The EGR coefficient C_EGR has a linear (proportional) relationship as shown in FIG. 6 between the pressure difference ΔP (difference between a reference in-cylinder pressure P_REF and a detected in-cylinder pressure P_CPS described later, see FIG. 8) and the EGR rate R_EGR. Therefore, the slope (= R_EGR / ΔP) is defined as the EGR coefficient C_EGR. Further, since this inclination has a characteristic that it changes according to the intake condition and the compression condition, it is calculated in this step 7.

  In this calculation process, as shown in FIG. 7, the same four input parameters (reference crank angle CA_REF, intake valve closing timing IVC, initial in-cylinder temperature T_STRT, and compression start intake pressure PBAC) are used as in the reference in-cylinder pressure map. Accordingly, the EGR coefficient C_EGR is calculated by searching the EGR coefficient map. This EGR coefficient map is obtained by previously calculating and mapping the EGR coefficient C_EGR for various conditions of these four input parameters.

  When the determination result in step 3 is NO, it is determined whether or not the crank angle stage FISTG is equal to a third predetermined value STG3 corresponding to the top dead center (compression TDC) at the end of the compression stroke (step 8). . When this determination result is NO, this process is terminated as it is. On the other hand, if the determination result in step 8 is YES and the cylinder 3a corresponds to immediately after the end of the compression stroke, the in-cylinder pressure PCYL detected at the reference crank angle CA_REF set in step 5 is read from the RAM, and the reference crank Obtained as the detected in-cylinder pressure P_CPS at the angle CA_REF (step 9).

  Next, a difference (= P_REF−P_CPS) between the reference in-cylinder pressure P_REF and the detected in-cylinder pressure P_CPS is calculated as a pressure difference ΔP (step 10). Then, by multiplying the pressure difference ΔP by the EGR coefficient C_EGR calculated in step 7, the EGR rate R_EGR of the in-cylinder gas is calculated (step 11), and this process is terminated.

  Next, an operation example obtained by the above-described EGR rate estimation process will be described with reference to FIG. 9 together with a comparative example. FIG. 9 shows that the actual fuel injection amount QFINJ_ACT temporarily changes to the increasing side (t1 to t1) as shown in (a) in a state where the operating condition of the engine 3 including the EGR rate R_EGR (for example, 10%) is constant. t2) In accordance with this, the actual equivalent ratio KACT is shifted to the rich side from the value 1.0 corresponding to the theoretical air-fuel ratio.

  In this case, since the basic value P_REF_B of the reference in-cylinder pressure P_REF calculated by the reference in-cylinder pressure map is on condition that the air-fuel ratio of the in-cylinder gas is the stoichiometric air-fuel ratio, as shown in FIG. Regardless of the actual fuel injection amount QFINJ_ACT (actual equivalent ratio KACT), it is a constant low value. On the other hand, when the actual equivalent ratio KACT shifts to the rich side, the specific heat ratio of the in-cylinder gas decreases accordingly, and the in-cylinder pressure PCYL decreases, so the detected in-cylinder pressure P_CPS at the reference crank angle CA_REF decreases.

  From the above relationship, when the basic value P_REF_B is used as it is as the reference in-cylinder pressure P_REF without correction, and the difference between the detected in-cylinder pressure PCPS and the basic value P_REF_B is the pressure difference ΔP, the pressure difference ΔP is the actual fuel injection amount. It decreases as QFINJ_ACT increases (dashed line in (b)). As a result, the EGR rate R_EGR calculated based on the pressure difference ΔP greatly shifts to a smaller side than the actual value (= 10%) (broken line (c)), and the EGR rate R_EGR is calculated with high accuracy. I can't.

  On the other hand, in the estimation process of the embodiment, the reference in-cylinder pressure P_REF is calculated by correcting the basic value P_REF_B according to the actual fuel injection amount QFINJ_ACT. In this case, in this example, since the EGR rate R_EGR = 10% and the actual fuel injection amount QFINJ_ACT corresponding to the actual equivalent ratio KACT = 1 is smaller than that in the case of R_EGR = 0, the corrected reference in-cylinder pressure is corrected. P_REF becomes larger than the basic value P_REF_B as a whole. When the actual equivalent ratio KACT is deviated as described above, the decrease in the in-cylinder pressure PCYL corresponding to the deviation is reflected in the reference in-cylinder pressure P_REF, and the reference in-cylinder pressure P_REF is corrected to a smaller value ((b ) Solid line). As a result, the pressure difference ΔP between the corrected reference in-cylinder pressure P_REF and the detected in-cylinder pressure P_CPS is kept equal to the other period during which the actual fuel injection amount QFINJ_ACT has not increased, so the EGR rate R_EGR is accurately calculated. (Solid line in (c)).

  Next, an ignition timing control process will be described as an example of engine control using the estimated EGR rate R_EGR with reference to FIG. This process is executed for each cylinder 3a in synchronization with the generation of the TDC signal. In this process, first, in step 41, a basic ignition timing IG_BASE is calculated by searching a predetermined map (not shown) according to the engine speed NE and the required torque TRQCMD. The required torque TRQCMD is calculated based on the accelerator opening AP and the engine speed NE.

  Next, an EGR correction amount ΔIGEGR is calculated by searching a predetermined map (not shown) according to the EGR rate R_EGR (step 42). Next, a correction amount ΔIGTTL due to factors other than the EGR rate R_EGR is calculated according to the engine water temperature TW, the engine speed NE, and the like (step 43). Finally, the ignition timing IGLOG is calculated by adding the EGR correction amount ΔIGEGR and the correction amount ΔIGTTL to the basic ignition timing IG_BASE (step 44), and this processing is terminated.

  As described above, according to the present embodiment, the in-cylinder pressure predicted to occur at the reference crank angle CA_REF during the compression stroke is calculated as the reference in-cylinder pressure P_REF, and the calculated reference in-cylinder pressure P_REF and the reference crank angle CA_REF are calculated. The EGR rate R_EGR of the in-cylinder gas is estimated based on the pressure difference ΔP from the detected in-cylinder pressure P_CPS detected by the in-cylinder pressure sensor 51 in FIG.

Further, since the calculation of the reference in-cylinder pressure P_REF is performed based on the characteristic of the specific heat ratio of the in-cylinder pressure gas in accordance with the acquired actual fuel injection amount QFINJ_ACT, the cylinder due to the deviation of the air-fuel ratio accompanying the change in the actual fuel injection amount QFINJ_ACT. The change in the internal pressure can be reflected in the reference in-cylinder pressure P_REF. As a result, the pressure difference ΔP between the reference in-cylinder pressure P_REF and the detected in-cylinder pressure P_CPS does not include the change in the in-cylinder pressure due to the deviation of the air-fuel ratio, and only the pressure difference due to the EGR rate is reflected. Based on P , it is possible to accurately estimate the EGR rate R_EGR of the in-cylinder gas while appropriately eliminating the influence of the deviation of the air-fuel ratio due to the change in the actual fuel injection amount QFINJ_ACT.

  More specifically, the calculation of the reference in-cylinder pressure P_REF is performed as follows. That is, the basic value P_REF_B of the reference in-cylinder pressure P_REF is obtained using the reference in-cylinder pressure map of FIG. Calculate (step 23 in FIG. 4). Further, the reference fuel injection amount QFINJ_REF when the air-fuel ratio of the in-cylinder gas becomes the stoichiometric air-fuel ratio under the condition that no external EGR gas is present in the in-cylinder gas (step 24) and the calculated reference Based on the injection amount difference ΔQF between the fuel injection amount QFINJ_REF and the actual fuel injection amount QFINJ_ACT, a correction amount P_QFM for the reference in-cylinder pressure P_REF is calculated (steps 26 and 27). Then, the reference in-cylinder pressure P_REF is calculated by adding the calculated correction amount P_QFM to the basic value P_REF_B (step 28).

  As described above, the reference in-cylinder pressure P_REF can be accurately calculated while appropriately reflecting the influence of the change in the in-cylinder pressure due to the deviation of the air-fuel ratio accompanying the change in the actual fuel injection amount QFINJ_ACT. Therefore, the reference in-cylinder pressure P_REF and the detected in-cylinder pressure It is possible to accurately estimate the EGR rate R_EGR based on the pressure difference ΔP with P_CPS.

  Furthermore, since the reference fuel injection amount QFINJ_REF is calculated according to the detected intake pressure PBA and the engine speed NE, the reference fuel injection amount QFINJ_REF can be calculated easily and accurately. In addition, the correction amount P_QFM of the reference in-cylinder pressure P_REF is calculated by multiplying the injection amount difference ΔQF between the reference fuel injection amount QFINJ_REF and the actual fuel injection amount QFINJ_ACT by the correction coefficient KF. Therefore, the correction amount P_QFM can be easily calculated. And can be performed accurately.

  In addition, this invention can be implemented in various aspects, without being limited to the described embodiment. For example, in the embodiment, the reference in-cylinder pressure P_REF is calculated by calculating the basic value P_REF_B corresponding to the theoretical air-fuel ratio using the reference in-cylinder pressure map and correcting the basic value P_REF_B according to the actual fuel injection amount QFINJ_ACT. Calculated. The present invention is not limited to such a correction method, and can be implemented by other methods. For example, by adding the actual fuel injection amount QFINJ_ACT or the like to the input parameter of the reference in-cylinder pressure map, and creating a reference in-cylinder pressure map corresponding to that in advance, the reference in-cylinder pressure P_REF corresponding to the actual fuel injection amount QFINJ_ACT is changed to the reference cylinder You may make it obtain | require directly from an internal pressure map.

  In addition, it has been described that the actual fuel injection amount QFINJ_ACT is calculated by searching the fuel injection amount characteristic map according to the valve opening time T_OUT and the fuel pressure PF of the fuel injection valve 4, but for controlling the fuel injection valve 4 Of course, it is possible to use the calculated fuel injection amount as it is.

  Furthermore, in the embodiment, the ignition timing control is executed in accordance with the estimated EGR rate R_EGR. However, instead of or in addition to this, other engine control, for example, EGR control via the EGR valve 42, throttle valve The intake air amount control via 27, the fuel injection control via the fuel injection valve 4, etc. may be executed.

  Moreover, although the EGR apparatus 14 is comprised with the low voltage | pressure EGR apparatus, it may replace with this and may use a high voltage | pressure EGR apparatus in this case, and this invention can be applied similarly also in that case. Furthermore, the in-cylinder pressure sensor 51 is integrated with the fuel injection valve 4, but it is needless to say that it may be a separate type arranged separately from the fuel injection valve 4.

  Furthermore, in the embodiment, the engine 3 is a vehicle engine, but the present invention can also be applied to an engine for other uses, for example, an engine for an outboard motor in which a crankshaft is arranged in the vertical direction. In addition, the detailed configuration can be changed as appropriate within the scope of the gist of the present invention.

2 ECU (actual fuel injection amount acquisition means, reference in-cylinder pressure calculation means, EGR rate estimation means, basic value calculation means, reference fuel injection amount calculation means, and correction amount calculation means)
3 Internal combustion engine 3a Cylinder 51 In-cylinder pressure sensor 52 Crank angle sensor (rotational speed detection means)
56 Intake pressure sensor (Intake pressure detection means)
R_EGR EGR rate of in-cylinder gas
PCYL In-cylinder pressure QFINJ_ACT Actual fuel injection amount CA_REF Reference crank angle P_REF Reference in-cylinder pressure P_CPS Detection in-cylinder pressure
ΔP Pressure difference between reference in-cylinder pressure and detected in-cylinder pressure P_REF_B Basic value of reference in-cylinder pressure QFINJ_REF Reference fuel injection amount
ΔQF injection amount difference (difference between reference fuel injection amount and actual fuel injection amount)
P_QFM correction amount (reference cylinder pressure correction amount)
PBA intake pressure (internal combustion engine operating condition)
NE engine speed (speed of internal combustion engine)
KF correction factor

Claims (4)

A control device for an internal combustion engine that estimates an EGR rate of in-cylinder gas filled in a cylinder,
An in-cylinder pressure sensor for detecting a pressure in the cylinder as an in-cylinder pressure;
Actual fuel injection amount acquisition means for acquiring an actual fuel amount injected into the cylinder as an actual fuel injection amount;
Based on the characteristic of the specific heat ratio of the in-cylinder gas in accordance with the obtained actual fuel injection amount under the condition that there is no external EGR gas due to exhaust gas recirculation in the in-cylinder gas, a predetermined reference during the compression stroke Reference in-cylinder pressure calculating means for calculating the in-cylinder pressure generated at the crank angle as a reference in-cylinder pressure;
EGR rate estimating means for estimating an EGR rate of in-cylinder gas based on a pressure difference between the calculated reference in-cylinder pressure and a detected in-cylinder pressure detected by the in-cylinder pressure sensor at the reference crank angle;
A control device for an internal combustion engine, comprising: The reference in-cylinder pressure calculating means includes
The cylinder pressure generated at the reference crank angle is calculated as the basic value of the reference cylinder pressure under the condition that no external EGR gas is present in the cylinder gas and the air-fuel ratio of the cylinder gas is the stoichiometric air-fuel ratio. A basic value calculating means for
A reference fuel injection amount calculating means for calculating, as a reference fuel injection amount, a fuel injection amount when the air-fuel ratio of the cylinder gas becomes the stoichiometric air-fuel ratio under the condition that no external EGR gas is present in the cylinder gas; ,
Correction amount calculation means for calculating a correction amount of the reference in-cylinder pressure based on a difference between the calculated reference fuel injection amount and the actual fuel injection amount;
2. The control apparatus for an internal combustion engine according to claim 1, wherein the reference in-cylinder pressure is calculated by adding the correction amount to the basic value. An intake pressure detecting means for detecting an intake pressure taken into the cylinder as an intake pressure;
A rotation speed detection means for detecting the rotation speed of the internal combustion engine,
The reference fuel injection amount calculating means includes
The control device for an internal combustion engine according to claim 2, wherein the reference fuel injection amount is calculated based on the detected intake pressure and the rotational speed of the internal combustion engine.   The correction amount calculation unit calculates the correction amount of the reference in-cylinder pressure by multiplying a difference between the reference fuel injection amount and the actual fuel injection amount by a correction coefficient. 3. The control device for an internal combustion engine according to 3.

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