JP5582076B2 - Control device for internal combustion engine - Google Patents

Description

  The present invention relates to a control device for a compression ignition type internal combustion engine represented by a diesel engine. In particular, the present invention provides an improved method for determining whether or not the combustion state has deteriorated with respect to the combustion to be inspected, and the deterioration of the combustion state when combustion is performed in the combustion chamber by a plurality of fuel injections. Sometimes related to measures to improve the state of combustion.

  Whether a diesel engine (hereinafter sometimes simply referred to as an engine) used as an automobile engine or the like has adequately obtained combustion stability, generated torque, fuel consumption rate, etc. in the combustion chamber. In order to determine the above, it has been proposed to evaluate the combustion state (Patent Document 1 and Patent Document 2 below).

  Specifically, this combustion state evaluation method includes a heat generation rate waveform that is a change in the heat generation rate (heat generation amount per unit rotation angle of the crankshaft) in the combustion chamber, and a fuel injection rate (unit of crankshaft). The fuel injection rate waveform, which is a change in the fuel injection amount per rotation angle), was used to evaluate the combustion state in the combustion chamber by determining whether these waveforms were ideal waveforms. .

  For example, in Patent Document 1, a heat generation rate associated with combustion in a combustion chamber is calculated based on an output signal of an in-cylinder pressure sensor, and a heat generation rate waveform that indicates a change in the heat generation rate is used. It is disclosed that the combustion state is evaluated by obtaining the peak value of. Further, in Patent Document 2, from the heat generation rate sequentially obtained based on the pressure in the combustion chamber, the ignition timing of the fuel, the peak value of the heat generation rate, and the integral value of the heat generation rate (the absolute amount obtained by accumulating the generated heat amount). It is disclosed that the combustion state is evaluated by obtaining the above. When it is determined that the combustion state has deteriorated, the combustion state is improved by correcting the fuel injection mode.

JP 2006-183466 A JP-A-11-173201

  As described above, conventionally, the heat generation rate waveform or the like is used to sequentially monitor the combustion state in the combustion chamber, that is, the amount of heat generated in the combustion chamber (the absolute amount of heat generated in the combustion chamber). The combustion state was evaluated while monitoring. For example, when pilot injection and main injection are executed as fuel injection forms from an injector, a heat release rate waveform is created for each combustion of fuel injected in each fuel injection, and the ideal for each combustion created in advance is created. The combustion state was evaluated by comparison (pattern matching) with a typical heat release rate waveform. For this reason, the man-hour required for the evaluation of a combustion state was great.

  Also, in order to determine whether the combustion state has deteriorated by comparing the ideal heat generation rate waveform with the actual heat generation rate waveform, the actual heat generation rate waveform is compared with the actual heat generation rate waveform. It is necessary to predetermine a criterion for determining whether the occurrence rate waveform is different and determining that the combustion state is deteriorated for each of the combustion in the pilot injection and the combustion in the main injection. However, when comparing waveforms, it is difficult to set the criteria, and it is necessary to set the criteria while analyzing various combustion patterns. It took a lot of effort.

  Furthermore, it is necessary to individually define the evaluation criteria for the combustion state for each type of engine and each fuel injection amount. In other words, ideal heat release rate waveforms in pilot injection and main injection are set individually for each type of engine and each fuel injection amount, and actual pilot injection and main injection are set for this ideal heat release rate waveform. It is necessary to define a criterion for each engine type and each fuel injection amount, such as how the heat generation rate waveform in the injection can be determined to be determined that the combustion state is deteriorated. Thus, a systematic combustion state evaluation standard common to various engines and fuel injection amounts has not yet been established, and this systematic combustion state evaluation standard (combustion state evaluation standard) Proposal of a quantified index) is required. That is, the quantification of the reference value for evaluating the combustion state has been demanded.

  The present invention has been made in view of the above points, and an object of the present invention is to easily evaluate a combustion state in a compression self-ignition internal combustion engine in which combustion in a combustion chamber is performed by a plurality of fuel injections. Another object of the present invention is to provide a control device for an internal combustion engine capable of improving the combustion state when it is determined that the combustion state is deteriorated based on the evaluation.

-Principle of solving the problem-
The solution principle of the present invention taken to achieve the above object is that the maximum amount of heat generated per unit volume of fuel in a period including each combustion period performed by multiple fuel injections, and the period Comparison with the amount of heat generated per unit volume of the fuel when the fuel is actually burning in the combustion chamber, and the maximum value of the amount of heat generated per unit volume of the fuel during the inspection target period and the inspection target period By comparing with the amount of heat generated per unit volume of fuel when the fuel is actually burning in the combustion chamber, it is determined whether or not the combustion state in the combustion chamber has deteriorated, and it is determined that the combustion state has deteriorated. In such a case, a correction operation such as the fuel injection amount is performed.

-Solution-
Specifically, the present invention relates to a compression self-ignition internal combustion engine in which a plurality of fuel injections are performed from a fuel injection valve into a combustion chamber according to a fuel injection amount command value, and combustion is performed by self-ignition of these injected fuels. An engine control device is assumed. Based on the deviation amount of the total combustion actual heat generation efficiency with respect to the following total combustion reference heat generation efficiency and the deviation amount of the inspection target combustion actual heat generation efficiency with respect to the inspection target combustion reference heat generation efficiency for the control device of the internal combustion engine. Combustion deterioration determination means for determining whether or not the deterioration of the combustion subject to inspection is provided. The total combustion reference heat generation efficiency is the maximum value of the amount of heat generated per unit volume of fuel during a predetermined total combustion period including at least a part of the combustion period of each fuel by the plurality of fuel injections. The total combustion actual heat generation efficiency is a value obtained by dividing the amount of heat actually generated in the total combustion period by the sum of the fuel injection amounts commanded by the fuel injection amount command value for each of the plurality of fuel injections. It is. The inspection target combustion reference heat generation efficiency is the amount of heat generated per unit volume of fuel in a predetermined inspection target period including at least a part of the combustion period to be inspected among the combustions by the plurality of fuel injections. It is the maximum value. The inspection target combustion actual heat generation efficiency is a value obtained by dividing the amount of heat actually generated in the inspection target period by the fuel injection amount commanded by the fuel injection amount command value in order to perform combustion as the inspection target. .

  Here, the “predetermined total combustion period including at least a part of the combustion period of each fuel by multiple fuel injections” means, for example, the entire period from the start of combustion to the end of combustion of fuel injected multiple times This is a concept that includes both the case where the period is set as the total combustion period and the case where a part of the period from the start of combustion of the fuel to the end of combustion is set as the total combustion period. In this case, one of the periods from the start of combustion of the injected fuel to the end of combustion is compared to the reference heat generation efficiency when the entire period from the start of combustion of the injected fuel to the end of combustion is set as the total combustion period. The reference heat generation efficiency when the period of the part is set as the total combustion period is set smaller.

  In addition, the “predetermined inspection target period including at least a part of the combustion period to be inspected” refers to, for example, the case where the entire period from the start of combustion of the injected fuel to the end of combustion is set as the inspection target period. It is a concept that includes both cases where a part of the period from the start of combustion of fuel to the end of combustion is set as the inspection target period. In this case, one of the periods from the start of combustion of the injected fuel to the end of combustion is compared to the reference heat generation efficiency when the entire period from the start of combustion of the injected fuel to the end of combustion is set as the inspection target period. The reference heat generation efficiency when the period of the section is set as the inspection target period is set smaller.

  When ideal combustion is performed in the combustion chamber, the amount of heat generated per unit volume of fuel during the total combustion period is the maximum value (total combustion reference heat generation efficiency), and the maximum value is the fuel injection amount or fuel injection. Even if the timing is different, it is unchanged if the amount of fuel burned in the total combustion period is constant. In this case, the amount of heat generated per unit volume of the fuel during the inspection target period is the maximum value (inspection target combustion reference heat generation efficiency), and the maximum value is the above inspection target even if the fuel injection amount and the fuel injection timing are different. If the amount of fuel burned in the period is constant, it will not change. Therefore, the amount of heat generated per unit volume of fuel during actual combustion during the total combustion period (the value obtained by dividing the amount of heat actually generated during the total combustion period divided by the fuel injection amount commanded by the fuel injection amount command value). It is judged how much the generated total combustion actual heat generation efficiency deviates from the total combustion reference heat generation efficiency, and the amount of heat generated per unit volume of fuel in actual combustion during the inspection period (inspection How much the actual heat generation efficiency of the inspection target combustion obtained from the amount of heat actually generated in the target period divided by the fuel injection amount commanded by the fuel injection amount command value) from the inspection target combustion reference heat generation efficiency By determining whether there is a divergence, it is possible to determine whether or not the combustion state in the combustion chamber has deteriorated. According to such a determination method, it is not necessary to individually define the evaluation criteria of the combustion state for each type of internal combustion engine and for each fuel injection amount, and a systematic system common to various internal combustion engines and each fuel injection amount. It is possible to establish an evaluation standard for a proper combustion state. For this reason, it is possible to quantify the evaluation criteria of the combustion state, and it is possible to simplify the evaluation operation.

  In addition, since it is possible to determine the presence or absence of deterioration of the combustion state in the combustion chamber by comparing the reference heat generation efficiency and the actual heat generation efficiency (comparison between numerical values), comparison of conventional heat generation rate waveforms (pattern) In contrast to the case where the combustion state is evaluated by matching), the combustion state can be evaluated by a relatively simple calculation, and the determination criteria for determining whether the combustion state has deteriorated can be easily set.

  Further, the total combustion period may be set as the entire period of the combustion period, or may be set as a part of the combustion period.

  When the total combustion period is set as the entire period of the combustion period, the total combustion reference heat generation efficiency is defined as the amount of heat generated per unit volume of fuel in the entire period of the combustion period of each fuel by the plurality of fuel injections. While the total combustion actual heat generation efficiency is set to the amount of heat actually generated during the entire combustion period of each fuel by the plurality of fuel injections for each of the plurality of fuel injections. A value obtained by dividing the sum of the fuel injection amounts commanded by the injection amount command value.

  On the other hand, when the total combustion period is set as a part of the combustion period, the total combustion reference heat generation efficiency is set to the unit volume of fuel in the entire period of each fuel combustion period by the plurality of fuel injections. The total combustion actual heat generation efficiency is defined as a value obtained by multiplying the maximum amount of heat generated per unit of heat a plurality of times. A value obtained by dividing the fuel injection amount by the sum of fuel injection amounts commanded by the fuel injection amount command value.

  Moreover, as an inspection object period, you may set as all the periods of the combustion period made into inspection object, and may set it as a part of period of the combustion period.

  When the inspection target period is set as the entire period of the combustion period to be inspected, the inspection reference combustion reference heat generation efficiency is generated per unit volume of fuel in the entire period of the inspection target combustion period. While setting the maximum amount of heat, the fuel injection amount command for performing the combustion with the amount of heat actually generated during the entire combustion period to be inspected as the inspection target combustion actual heat generation efficiency. The value is divided by the fuel injection amount commanded by the value.

  On the other hand, when the inspection target period is set as a part of the combustion period to be inspected, the inspection reference combustion reference heat generation efficiency is determined per unit volume of fuel in the entire combustion period to be inspected. On the other hand, the inspection target combustion actual heat generation efficiency is defined by a value obtained by multiplying the maximum value of the generated heat amount by a predetermined ratio. In order to carry out, it is set to a value divided by the fuel injection amount commanded by the fuel injection amount command value.

  As described above, when the total combustion period and the inspection target period are set as a part of the combustion period, the actual heat generation efficiency is calculated for a part of the combustion period, thus simplifying the calculation. Can be planned. In addition, when the total combustion period and the inspection target period are set to a relatively early period of the combustion period, the acquisition timing of the actual heat generation efficiency can be obtained early, and whether there is any deterioration in combustion in the combustion chamber. Judgment can be made early.

  Examples of the configuration for improving the combustion state when it is determined that the combustion state in the combustion chamber has deteriorated include the following.

  When at least main injection (second injection) and sub-injection (first injection) performed prior to the main injection are executed as fuel injection from the fuel injection valve into the combustion chamber, The deviation amount of the total combustion actual heat generation efficiency from the total combustion reference heat generation efficiency does not exceed a predetermined threshold, and the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the sub-injection is the inspection target combustion reference heat. Correcting means is provided for increasing the fuel injection amount in the sub-injection when the generation efficiency is lower and the deviation amount exceeds a predetermined threshold value.

  Further, as the fuel injection from the fuel injection valve into the combustion chamber, at least when the main injection and the sub-injection performed prior to the main injection are executed, the total combustion reference heat generation efficiency The deviation amount of the actual combustion heat generation efficiency does not exceed a predetermined threshold value, and the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the sub-injection is lower than the inspection target combustion reference heat generation efficiency. When the deviation amount exceeds a predetermined threshold and the actual combustion heat generation efficiency of the fuel to be inspected in the combustion of the fuel injected by the main injection exceeds the reference heat generation efficiency of the inspection target combustion, Correcting means is provided for correcting the fuel injection amount to be increased and correcting the fuel injection amount in the main injection to be decreased.

  In such a situation, because the in-cylinder temperature at the injection timing of the sub-injection is not sufficiently obtained, a part of the fuel injected by the sub-injection cannot be burned during the combustion period, and is injected by the main injection. It can be estimated that the fuel is burned during the combustion period. Accordingly, the fuel injection amount in the sub-injection is increased and corrected, and the fuel injection amount in the main injection is corrected and decreased by the correction amount substantially the same as the increase correction amount. In other words, by increasing the fuel injection amount in the sub-injection, the heat amount during the combustion period in the sub-injection is sufficiently secured, and by reducing the fuel injection amount in the main injection, the output torque is increased excessively. To prevent.

  Further, as the fuel injection from the fuel injection valve into the combustion chamber, at least when the main injection and the sub-injection performed prior to the main injection are executed, the total combustion reference heat generation efficiency The deviation amount of the actual combustion heat generation efficiency does not exceed a predetermined threshold value, and the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the sub-injection is lower than the inspection target combustion reference heat generation efficiency. The amount of deviation exceeds a predetermined threshold, the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the main injection is lower than the inspection target combustion reference heat generation efficiency, and the amount of deviation exceeds the predetermined threshold. When it exceeds, correction means is provided for correcting both the fuel injection amount in the sub-injection and the fuel injection amount in the main injection to increase.

  In such a situation, because the in-cylinder temperature at the injection timing of the sub-injection is not sufficiently obtained, a part of the fuel injected by the sub-injection cannot be combusted during the combustion period, and the main injection It can be estimated that a part of the injected fuel cannot be burned during the combustion period (it cannot be burned during the period when the fuel injected by the main injection should be completed). Therefore, the fuel injection amount in the sub injection is corrected to increase. In other words, by increasing the fuel injection amount in the sub-injection, the heat amount during the combustion period in the sub-injection is sufficiently secured, the ignition delay of the fuel injected in the main injection is eliminated, and the fuel is injected in the main injection. In order to ensure proper combustion within the period when combustion of the remaining fuel is to be completed. As a result, the output torque is appropriately obtained.

  In addition, as the fuel injection from the fuel injection valve into the combustion chamber, at least when the main injection and the sub-injection performed prior to the main injection are executed, the total combustion actual heat generation efficiency is total. Combustion reference heat generation efficiency is below and the amount of deviation exceeds a predetermined threshold, and the actual combustion heat generation efficiency to be inspected in the combustion of fuel injected by the sub-injection is less than the inspection reference combustion reference heat generation efficiency. And the deviation amount exceeds a predetermined threshold value, the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the main injection is lower than the inspection target combustion reference heat generation efficiency, and the deviation amount is When a predetermined threshold value is exceeded, there is provided correction means for correcting both the fuel injection amount in the sub-injection and the fuel injection amount in the main injection.

  In such a situation, it can be determined that each fuel injection amount in the sub-injection and main injection is insufficient. That is, it can be determined that the fuel injection amount commanded by the fuel injection amount command value may not be ensured. Therefore, by increasing the fuel injection amount in the sub-injection, the heat amount during the combustion period in the sub-injection is sufficiently ensured, and by increasing the fuel injection amount in the main injection, the output torque is secured. Like that.

  Further, when the fuel injection from the fuel injection valve into the combustion chamber is performed at least in the main injection and the sub-injection performed prior to the main injection, the total combustion actual heat generation efficiency is total. Combustion reference heat generation efficiency is below and the amount of deviation exceeds a predetermined threshold, and the actual combustion heat generation efficiency to be inspected in the combustion of fuel injected by the sub-injection is less than the inspection reference combustion reference heat generation efficiency. And the deviation amount exceeds a predetermined threshold value, and the deviation amount of the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the main injection exceeds the predetermined threshold value. If not, correction means for correcting the fuel injection amount in the sub-injection is provided.

  In such a situation, since the in-cylinder temperature at the injection timing of the secondary injection is not sufficiently obtained, it can be estimated that a part of the fuel injected by the secondary injection cannot be combusted during the combustion period. Therefore, the fuel injection amount in the sub injection is corrected to increase. That is, by sufficiently correcting the fuel injection amount in the sub-injection, a sufficient amount of heat is ensured during the combustion period in the sub-injection.

  In addition, as the fuel injection from the fuel injection valve into the combustion chamber, at least when the main injection and the sub-injection performed prior to the main injection are executed, the total combustion actual heat generation efficiency is total. When the combustion reference heat generation efficiency is exceeded and the deviation amount exceeds a predetermined threshold value, correction means for correcting the decrease in both the fuel injection amount in the sub-injection and the fuel injection amount in the main injection is provided. Provided.

  In such a situation, it can be determined that each fuel injection amount in the sub-injection and the main injection is excessive. That is, it can be determined that there is a possibility that fuel injection is performed in excess of the fuel injection amount commanded by the fuel injection amount command value. Accordingly, the amount of heat generated in the combustion chamber is optimized by correcting the decrease in both the fuel injection amount in the sub-injection and the fuel injection amount in the main injection.

  According to the present invention, it is no longer necessary to individually define the evaluation criteria for the combustion state for each type of internal combustion engine and for each fuel injection amount, and systematic combustion states common to various internal combustion engines and each fuel injection amount. It becomes possible to establish the evaluation criteria. Further, the combustion state can be evaluated by a relatively simple calculation compared to the case where the combustion state is evaluated by comparison (pattern matching) between the heat release rate waveforms.

It is a figure which shows schematic structure of the engine which concerns on embodiment, and its control system. It is sectional drawing which shows the combustion chamber of a diesel engine, and its peripheral part. It is a block diagram which shows the structure of control systems, such as ECU. It is a wave form diagram which shows the change of the heat release rate (heat generation amount per unit rotation angle of a crankshaft) and the change of a fuel injection rate (fuel injection amount per unit rotation angle of a crankshaft) at the time of a combustion stroke, respectively. It is a figure which shows an example of the heat release rate waveform and fuel injection rate waveform for demonstrating the evaluation method of a combustion state. FIG. 6A shows the experimental results when combustion is performed in the combustion chamber with various fuel injection amounts. FIG. 6A shows the heat release rate waveform and the fuel injection rate waveform for each fuel injection amount. ) Is a diagram showing the relationship between the fuel injection amount and the heat generation efficiency (the amount of heat generated per unit volume of fuel). FIG. 7A shows the experimental results when combustion is performed in the combustion chamber at various fuel injection pressures. FIG. 7A shows the heat release rate waveform and the fuel injection rate waveform for each fuel injection pressure. ) Is a diagram showing the relationship between the fuel injection pressure and the heat generation efficiency. FIG. 8A shows the experimental results when combustion is performed in the combustion chamber at various fuel injection timings. FIG. 8A shows the heat release rate waveform and the fuel injection rate waveform at each fuel injection timing. ) Is a diagram showing a relationship between fuel injection timing and heat generation efficiency. FIG. 9A shows the experimental results when combustion is performed in the combustion chamber at various oxygen excess rates. FIG. 9A shows the heat release rate waveform and the fuel injection rate waveform for each oxygen excess rate. ) Is a diagram showing the relationship between the oxygen excess rate and the heat generation efficiency. It is a figure which shows an example of the heat release rate waveform and fuel injection rate waveform for demonstrating the combustion state evaluation method which concerns on the modification 1. FIG. It is a figure which shows an example of the heat release rate waveform and fuel injection rate waveform for demonstrating the combustion state evaluation method which concerns on the modification 2. FIG. It is a figure which shows an example of the heat release rate waveform and fuel injection rate waveform for demonstrating the combustion state evaluation method which concerns on the modification 3. FIG. It is a figure which shows an example of the heat release rate waveform and fuel injection rate waveform for demonstrating the combustion state evaluation method which concerns on the modification 4. FIG. It is a figure which shows an example of the heat release rate waveform and fuel injection rate waveform for demonstrating the combustion state evaluation method which concerns on the modification 5. FIG.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the present embodiment, a case where the present invention is applied to a common rail in-cylinder direct injection multi-cylinder (for example, in-line 4-cylinder) diesel engine (compression self-ignition internal combustion engine) mounted on an automobile will be described.

-Engine configuration-
First, a schematic configuration of a diesel engine (hereinafter simply referred to as an engine) according to the present embodiment will be described. FIG. 1 is a schematic configuration diagram of an engine 1 and its control system according to the present embodiment. Moreover, FIG. 2 is sectional drawing which shows the combustion chamber 3 of a diesel engine, and its peripheral part.

  As shown in FIG. 1, the engine 1 according to the present embodiment is configured as a diesel engine system having a fuel supply system 2, a combustion chamber 3, an intake system 6, an exhaust system 7 and the like as main parts.

  The fuel supply system 2 includes a supply pump 21, a common rail 22, an injector (fuel injection valve) 23, a shutoff valve 24, a fuel addition valve 26, an engine fuel passage 27, an addition fuel passage 28, and the like.

  The supply pump 21 pumps fuel from the fuel tank, makes the pumped fuel high pressure, and supplies it to the common rail 22 via the engine fuel passage 27. The common rail 22 has a function as a pressure accumulation chamber that holds (accumulates) the high-pressure fuel supplied from the supply pump 21 at a predetermined pressure, and distributes the accumulated fuel to the injectors 23. The injector 23 includes a piezoelectric element (piezo element) therein, and is configured by a piezo injector that is appropriately opened to supply fuel into the combustion chamber 3. Details of the fuel injection control from the injector 23 will be described later.

  The supply pump 21 supplies a part of the fuel pumped from the fuel tank to the fuel addition valve 26 via the addition fuel passage 28. The added fuel passage 28 is provided with the shutoff valve 24 for shutting off the added fuel passage 28 and stopping fuel addition in an emergency.

  Further, the fuel addition valve 26 is configured so that the fuel addition amount to the exhaust system 7 becomes a target addition amount (addition amount at which the exhaust A / F becomes the target A / F) by the addition control operation by the ECU 100. The valve opening timing is controlled so that the fuel addition timing becomes a predetermined timing. That is, a desired fuel is injected and supplied from the fuel addition valve 26 to the exhaust system 7 (from the exhaust port 71 to the exhaust manifold 72) at an appropriate timing.

  The intake system 6 includes an intake manifold 63 connected to an intake port 15a formed in the cylinder head 15 (see FIG. 2), and an intake pipe 64 that constitutes an intake passage is connected to the intake manifold 63. Further, an air cleaner 65, an air flow meter 43, and a throttle valve (intake throttle valve) 62 are arranged in this intake passage in order from the upstream side. The air flow meter 43 outputs an electrical signal corresponding to the amount of air flowing into the intake passage via the air cleaner 65.

  Further, the intake system 6 is provided with a swirl control valve (swirl speed variable mechanism) 66 for making the swirl flow (horizontal swirl flow) in the combustion chamber 3 variable (see FIG. 2). . Specifically, as the intake port 15a, two systems, a normal port and a swirl port, are provided for each cylinder. Of these, a normal valve 15a shown in FIG. A swirl control valve 66 is disposed. An actuator (not shown) is connected to the swirl control valve 66, and the flow rate of air passing through the normal port 15a can be changed according to the opening of the swirl control valve 66 adjusted by driving the actuator. Yes. The larger the opening of the swirl control valve 66, the greater the amount of air taken into the cylinder from the normal port 15a. For this reason, the swirl generated by the swirl port (not shown in FIG. 2) becomes relatively weak, and the inside of the cylinder becomes low swirl (a state where the swirl speed is low). Conversely, the smaller the opening of the swirl control valve 66, the smaller the amount of air drawn into the cylinder from the normal port 15a. For this reason, the swirl generated by the swirl port is relatively strengthened, and the inside of the cylinder becomes a high swirl (a state where the swirl speed is high).

  The exhaust system 7 includes an exhaust manifold 72 connected to the exhaust port 71 formed in the cylinder head 15, and exhaust pipes 73 and 74 constituting an exhaust passage are connected to the exhaust manifold 72. In addition, a maniverter (exhaust gas purification device) 77 including a NOx storage catalyst (NSR catalyst: NOx Storage Reduction catalyst) 75 and a DPNR catalyst (Diesel Particle-NOx Reduction catalyst) 76 is disposed in the exhaust passage. Hereinafter, the NSR catalyst 75 and the DPNR catalyst 76 will be described.

The NSR catalyst 75 is an NOx storage reduction catalyst. For example, alumina (Al ₂ O ₃ ) is used as a support, and potassium (K), sodium (Na), lithium (Li), cesium (Cs), for example, is supported on this support. Alkali metal such as barium (Ba), alkaline earth such as calcium (Ca), rare earth such as lanthanum (La) and yttrium (Y), and noble metal such as platinum (Pt) were supported. It has a configuration.

The NSR catalyst 75 occludes NOx in a state where a large amount of oxygen is present in the exhaust gas, has a low oxygen concentration in the exhaust gas, and a large amount of reducing component (for example, an unburned component (HC) of the fuel). In the existing state, NOx is reduced to NO ₂ or NO and released. NO NOx released as NO ₂ or NO, the N ₂ is further reduced due to quickly reacting with HC or CO in the exhaust. Further, HC and CO are oxidized to H ₂ O and CO ₂ by reducing NO ₂ and NO. That is, by appropriately adjusting the oxygen concentration and HC component in the exhaust gas introduced into the NSR catalyst 75, HC, CO, and NOx in the exhaust gas can be purified. In the present embodiment, the oxygen concentration and HC component in the exhaust gas can be adjusted by the fuel addition operation from the fuel addition valve 26.

  On the other hand, the DPNR catalyst 76 is, for example, a porous ceramic structure carrying a NOx storage reduction catalyst, and PM in the exhaust gas is collected when passing through the porous wall. Further, when the air-fuel ratio of the exhaust gas is lean, NOx in the exhaust gas is stored in the NOx storage reduction catalyst, and when the air-fuel ratio becomes rich, the stored NOx is reduced and released. Further, the DPNR catalyst 76 carries a catalyst that oxidizes and burns the collected PM (for example, an oxidation catalyst mainly composed of a noble metal such as platinum).

  Here, the structure of the combustion chamber 3 of a diesel engine and its peripheral part is demonstrated using FIG. As shown in FIG. 2, a cylinder block 11 constituting a part of the engine body is formed with a cylindrical cylinder bore 12 for each cylinder (four cylinders), and a piston 13 is formed inside each cylinder bore 12. Is accommodated so as to be slidable in the vertical direction.

  The combustion chamber 3 is formed above the top surface 13 a of the piston 13. That is, the combustion chamber 3 is defined by the lower surface of the cylinder head 15 attached to the upper part of the cylinder block 11 via the gasket 14, the inner wall surface of the cylinder bore 12, and the top surface 13 a of the piston 13. A cavity (concave portion) 13 b is formed in a substantially central portion of the top surface 13 a of the piston 13, and this cavity 13 b also constitutes a part of the combustion chamber 3.

  As for the shape of the cavity 13b, the concave dimension is small in the central portion (on the cylinder center line P), and the concave dimension is increased toward the outer peripheral side. That is, as shown in FIG. 2, when the piston 13 is in the vicinity of the compression top dead center, the combustion chamber 3 formed by the cavity 13b is a narrow space having a relatively small volume at the center portion, and is directed toward the outer peripheral side. Thus, the space is gradually enlarged (expanded space).

  The piston 13 has a small end portion 18a of a connecting rod 18 connected by a piston pin 13c, and a large end portion of the connecting rod 18 is connected to a crankshaft which is an engine output shaft. As a result, the reciprocating movement of the piston 13 in the cylinder bore 12 is transmitted to the crankshaft via the connecting rod 18, and the engine output is obtained by rotating the crankshaft. Further, a glow plug 19 is disposed toward the combustion chamber 3. The glow plug 19 functions as a start-up assisting device that is heated red when an electric current is applied immediately before the engine 1 is started and a part of the fuel spray is blown onto the glow plug 19 to promote ignition and combustion.

  The cylinder head 15 is formed with the intake port 15a for introducing air into the combustion chamber 3 and the exhaust port 71 for exhausting exhaust gas from the combustion chamber 3, and intake air for opening and closing the intake port 15a. An exhaust valve 17 that opens and closes the valve 16 and the exhaust port 71 is provided. The intake valve 16 and the exhaust valve 17 are disposed to face each other with the cylinder center line P interposed therebetween. That is, the engine 1 is configured as a cross flow type. The cylinder head 15 is provided with the injector 23 that directly injects fuel into the combustion chamber 3. The injector 23 is disposed at a substantially upper center of the combustion chamber 3 in a standing posture along the cylinder center line P, and injects fuel introduced from the common rail 22 toward the combustion chamber 3 at a predetermined timing. It has become.

  Furthermore, as shown in FIG. 1, the engine 1 is provided with a supercharger (turbocharger) 5. The turbocharger 5 includes a turbine wheel 52 and a compressor wheel 53 that are connected via a turbine shaft 51. The compressor wheel 53 is disposed facing the intake pipe 64, and the turbine wheel 52 is disposed facing the exhaust pipe 73. For this reason, the turbocharger 5 performs a so-called supercharging operation in which the compressor wheel 53 is rotated using the exhaust flow (exhaust pressure) received by the turbine wheel 52 to increase the intake pressure. The turbocharger 5 in the present embodiment is a variable nozzle type turbocharger, and a variable nozzle vane mechanism (not shown) is provided on the turbine wheel 52 side. By adjusting the opening of the variable nozzle vane mechanism, the engine 1 supercharging pressure can be adjusted.

  An intake pipe 64 of the intake system 6 is provided with an intercooler 61 for forcibly cooling the intake air whose temperature has been raised by supercharging in the turbocharger 5.

  The throttle valve 62 provided further downstream than the intercooler 61 is an electronically controlled on-off valve whose opening degree can be adjusted steplessly. It has a function of narrowing down the area and adjusting (reducing) the supply amount of the intake air.

  Further, the engine 1 is provided with an exhaust gas recirculation passage (EGR passage) 8 that connects the intake system 6 and the exhaust system 7. The EGR passage 8 is configured to reduce the combustion temperature by recirculating a part of the exhaust gas to the intake system 6 and supplying it again to the combustion chamber 3, thereby reducing the amount of NOx generated. In addition, the EGR passage 8 is opened and closed steplessly by electronic control, and the exhaust gas passing through the EGR passage 8 (recirculating) is cooled by an EGR valve 81 that can freely adjust the exhaust flow rate flowing through the passage. An EGR cooler 82 is provided. The EGR passage 8, the EGR valve 81, the EGR cooler 82, and the like constitute an EGR device (exhaust gas recirculation device).

-Sensors-
Various sensors are attached to each part of the engine 1, and signals related to the environmental conditions of each part and the operating state of the engine 1 are output.

  For example, the air flow meter 43 outputs a detection signal corresponding to the flow rate of intake air (intake air amount) upstream of the throttle valve 62 in the intake system 6. The intake air temperature sensor 49 is disposed in the intake manifold 63 and outputs a detection signal corresponding to the temperature of the intake air. The intake pressure sensor 48 is disposed in the intake manifold 63 and outputs a detection signal corresponding to the intake air pressure. The A / F (air-fuel ratio) sensor 44 outputs a detection signal that continuously changes in accordance with the oxygen concentration in the exhaust gas downstream of the manipulator 77 of the exhaust system 7. Similarly, the exhaust temperature sensor 45 outputs a detection signal corresponding to the temperature of the exhaust gas (exhaust temperature) downstream of the manipulator 77 of the exhaust system 7. The rail pressure sensor 41 outputs a detection signal corresponding to the fuel pressure stored in the common rail 22. The throttle opening sensor 42 detects the opening of the throttle valve 62.

-ECU-
As shown in FIG. 3, the ECU 100 includes a CPU 101, a ROM 102, a RAM 103, a backup RAM 104, and the like. The ROM 102 stores various control programs, maps that are referred to when the various control programs are executed, and the like. The CPU 101 executes various arithmetic processes based on various control programs and maps stored in the ROM 102. The RAM 103 is a memory that temporarily stores calculation results in the CPU 101, data input from each sensor, and the like. The backup RAM 104 is a non-volatile memory that stores data to be saved when the engine 1 is stopped, for example.

  The CPU 101, the ROM 102, the RAM 103, and the backup RAM 104 are connected to each other via the bus 107, and are connected to the input interface 105 and the output interface 106.

  The input interface 105 is connected with the rail pressure sensor 41, the throttle opening sensor 42, the air flow meter 43, the A / F sensor 44, the exhaust temperature sensor 45, the intake pressure sensor 48, and the intake temperature sensor 49. Further, the input interface 105 includes a water temperature sensor 46 that outputs a detection signal corresponding to the cooling water temperature of the engine 1, an accelerator opening sensor 47 that outputs a detection signal corresponding to the depression amount of the accelerator pedal, and an output shaft of the engine 1. Connected are a crank position sensor 40 that outputs a detection signal (pulse) every time the (crankshaft) rotates by a certain angle, an external air pressure sensor 4A that detects the pressure of outside air, an in-cylinder pressure sensor 4B that detects in-cylinder pressure, and the like. Has been.

  On the other hand, the output interface 106 is connected to the supply pump 21, the injector 23, the fuel addition valve 26, the throttle valve 62, the swirl control valve 66, the EGR valve 81, and the like. In addition, an actuator (not shown) provided in the variable nozzle vane mechanism of the turbocharger 5 is also connected to the output interface 106.

  Then, the ECU 100 executes various controls of the engine 1 based on outputs from the various sensors described above, calculated values obtained by arithmetic expressions using the output values, or various maps stored in the ROM 102. .

  For example, the ECU 100 executes pilot injection (sub-injection) and main injection (main injection) as fuel injection control of the injector 23.

  The pilot injection is an operation for injecting a small amount of fuel in advance prior to the main injection from the injector 23. The pilot injection is an injection operation for suppressing the ignition delay of fuel due to the main injection and leading to stable diffusion combustion, and is also referred to as sub-injection. Further, the pilot injection in the present embodiment has not only a function of suppressing the initial combustion speed by the main injection described above but also a preheating function of increasing the in-cylinder temperature. That is, after the pilot injection is performed, the fuel injection is temporarily interrupted, and the compressed gas temperature (in-cylinder temperature) is sufficiently increased until the main injection is started to reach the fuel self-ignition temperature (for example, 1000 K). In this way, the ignitability of the fuel injected by the main injection is ensured satisfactorily.

  The main injection is an injection operation (torque generation fuel supply operation) for generating torque of the engine 1. The injection amount in the main injection is basically determined so as to obtain the required torque according to the operation state such as the engine speed, the accelerator operation amount, the coolant temperature, the intake air temperature, and the like. For example, the higher the engine speed (the engine speed calculated based on the detection value of the crank position sensor 40), the larger the accelerator operation amount (the accelerator pedal depression amount detected by the accelerator opening sensor 47). As the accelerator opening becomes larger, the required torque value of the engine 1 is higher, and accordingly, the fuel injection amount in the main injection is also set higher. In addition, when the pre-injection in the cylinder is sufficiently performed by the pilot injection, the fuel injected by the main injection is immediately exposed to a temperature environment equal to or higher than the auto-ignition temperature, and the thermal decomposition proceeds. Will start burning immediately.

  Specifically, fuel ignition delay in a diesel engine includes physical ignition delay and chemical ignition delay. The physical ignition delay is the time required for evaporation / mixing of the fuel droplets and depends on the gas temperature of the combustion field. On the other hand, chemical ignition delay is the time required for chemical bonding and decomposition of fuel vapor and oxidation heat generation. In the situation where the cylinder is sufficiently preheated as described above, the physical ignition delay can be minimized, and as a result, the ignition delay can be minimized. Therefore, as a combustion mode of the fuel injected by the main injection, premixed combustion is hardly performed, and most of it is diffusion combustion. As a result, controlling the injection timing of the main injection is substantially equivalent to controlling the start timing of diffusion combustion as it is, and the controllability of combustion can be greatly improved. That is, by controlling the ignition timing and heat generation amount by controlling the fuel injection timing and fuel injection amount in the main injection by minimizing the proportion of premixed combustion of the fuel injected in the main injection, Controllability can be greatly improved.

  In addition to the pilot injection and main injection described above, after injection and post injection are performed as necessary. After injection is an injection operation for increasing the exhaust gas temperature. Specifically, after injection is performed at a timing at which most of the combustion energy of the supplied fuel is obtained as thermal energy of the exhaust gas without being converted into torque of the engine 1. The post-injection is an injection operation for directly introducing fuel into the exhaust system 7 to increase the temperature of the manipulator 77. For example, when the accumulated amount of PM trapped in the DPNR catalyst 76 exceeds a predetermined amount (for example, detected by detecting a differential pressure before and after the manipulator 77), post injection is performed. .

  Further, the ECU 100 controls the opening degree of the EGR valve 81 according to the operating state of the engine 1 to adjust the exhaust gas recirculation amount (EGR amount) toward the intake manifold 63. The EGR amount is set according to an EGR map stored in advance in the ROM 102. Specifically, this EGR map is a map for determining the EGR amount (EGR rate) using the engine speed and the engine load as parameters. This EGR map is created in advance by experiments, simulations, or the like. That is, by applying the engine speed calculated based on the detection value of the crank position sensor 40 and the opening of the throttle valve 62 (corresponding to the engine load) detected by the throttle opening sensor 42 to the EGR map. An EGR amount (opening degree of the EGR valve 81) is obtained.

  Further, the ECU 100 executes the opening degree control of the swirl control valve 66. In order to control the opening degree of the swirl control valve 66, the amount of movement of the fuel spray injected into the combustion chamber 3 per unit time (or per unit crank rotation angle) in the circumferential direction in the cylinder is changed. Is called.

-Fuel injection pressure-
The fuel injection pressure when executing the fuel injection is determined by the internal pressure of the common rail 22. As the common rail internal pressure, generally, the target value of the fuel pressure supplied from the common rail 22 to the injector 23, that is, the target rail pressure, increases as the engine load (engine load) increases and the engine speed (engine speed) increases. It will be expensive. That is, when the engine load is high, the amount of air sucked into the combustion chamber 3 is large. Therefore, a large amount of fuel must be injected from the injector 23 into the combustion chamber 3, and therefore the injection from the injector 23 is performed. The pressure needs to be high. Further, when the engine speed is high, the injection period is short, so the amount of fuel injected per unit time must be increased, and therefore the injection pressure from the injector 23 needs to be increased. . Thus, the target rail pressure is generally set based on the engine load and the engine speed. The target rail pressure is set according to a fuel pressure setting map stored in the ROM 102, for example. That is, by determining the fuel pressure according to this fuel pressure setting map, the valve opening period (injection rate waveform) of the injector 23 is controlled, and the fuel injection amount during the valve opening period can be defined.

  In the present embodiment, the fuel pressure is adjusted between 30 MPa and 200 MPa according to the engine load and the like.

  Regarding the fuel injection parameters such as the pilot injection and the main injection, the optimum values differ depending on the temperature conditions of the engine 1 and the intake air.

  For example, the ECU 100 adjusts the fuel discharge amount of the supply pump 21 so that the common rail pressure becomes equal to the target rail pressure set based on the engine operating state, that is, the fuel injection pressure matches the target injection pressure. To measure. Further, the ECU 100 determines the fuel injection amount and the fuel injection form based on the engine operating state. Specifically, the ECU 100 calculates the engine rotation speed based on the detection value of the crank position sensor 40, obtains the amount of depression of the accelerator pedal (accelerator opening) based on the detection value of the accelerator opening sensor 47, The total fuel injection amount (the sum of the injection amount in pilot injection and the injection amount in main injection) is determined based on the engine speed and the accelerator opening.

-Setting of target fuel pressure-
Next, a method for setting the target fuel pressure will be described. In the diesel engine 1, it is important to meet various requirements such as improvement of exhaust emission by reducing NOx generation amount and smoke generation amount, reduction of combustion noise during combustion stroke, and sufficient securing of engine torque. As a method for simultaneously satisfying these requirements, it is effective to appropriately control the change state of the heat generation rate in the cylinder during the combustion stroke (change state represented by the heat generation rate waveform).

  The solid line of the waveforms shown in the upper part of FIG. 4 shows an ideal heat generation rate waveform related to the combustion of fuel injected in pilot injection and main injection, with the horizontal axis representing the crank angle and the vertical axis representing the heat generation rate. ing. TDC in the figure indicates the crank angle position corresponding to the compression top dead center of the piston 13. The waveform shown in the lower part of FIG. 4 shows the waveform of the injection rate of fuel injected from the injector 23 (fuel injection amount per unit rotation angle of the crankshaft).

  As the heat release rate waveform, for example, combustion of fuel injected by main injection is started from the vicinity of the compression top dead center (TDC) of the piston 13, and a predetermined piston position after the compression top dead center of the piston 13 (for example, The heat generation rate reaches a maximum value (peak value) at 10 degrees after compression top dead center (ATDC 10 °), and a predetermined piston position after compression top dead center (for example, 25 degrees after compression top dead center ( At the time of ATDC 25 °), the combustion of the fuel injected in the main injection ends. If combustion of the air-fuel mixture is performed in such a state where the heat generation rate changes, for example, 50% of the air-fuel mixture in the cylinder burns at 10 degrees after compression top dead center (ATDC 10 °). Completed status. That is, the combustion center of gravity is 10 degrees after compression top dead center (ATDC 10 °), and about 50% of the total heat generation amount in the expansion stroke is generated by ATDC 10 °, and the engine 1 is operated with high thermal efficiency. Is possible.

  The relationship between the crank angle and the fuel injection rate waveform when the combustion center of gravity is reached is the period from when the fuel injection stop signal is transmitted to the injector 23 until the fuel injection is completely stopped (see FIG. 4, the combustion center of gravity is located in the period T).

  In such a situation in which combustion with an ideal heat generation rate waveform is performed, the cylinder is sufficiently preheated by pilot injection, and the fuel injected in the main injection is immediately self-ignited by this preheating. The thermal decomposition proceeds due to exposure to a temperature environment higher than the temperature, and combustion starts immediately after injection.

  The waveform indicated by the two-dot chain line α in FIG. 4 is a heat generation rate waveform when the fuel injection pressure is set higher than the appropriate value, and both the combustion rate and the peak value of the heat generation rate are too high. Therefore, there is a concern about an increase in combustion noise and an increase in the amount of NOx generated. On the other hand, a waveform indicated by a two-dot chain line β in FIG. 4 is a heat generation rate waveform when the fuel injection pressure is set lower than an appropriate value, and the timing at which the combustion rate is low and the peak of the heat generation rate appears. There is a concern that sufficient engine torque cannot be secured due to the large shift to the retard side.

-Evaluation method of combustion state-
Next, a combustion state evaluation method (combustion state deterioration determination method) that is a feature of the present embodiment will be described.

(Explanation of the principle of evaluation method)
When the pilot injection and the main injection are sequentially performed toward the combustion chamber 3 and most of each fuel burns well to generate heat, that is, the oxygen concentration and the oxygen excess rate in the combustion chamber 3 are Sufficiently secured (for example, the oxygen concentration is 17% or more and the excess oxygen ratio is 1.5 or more), and the in-cylinder temperature has reached the self-ignition temperature of the fuel (for example, when the pilot injection is performed) The in-cylinder temperature is 750K or higher, and the in-cylinder temperature at the time of main injection is 1000K or higher), and an appropriate amount of fuel according to the fuel injection amount command value from the ECU 100 is injected from the injector 23. In this case, the entire combustion period of the fuel (the period from the start of the combustion period of fuel injected by pilot injection to the end of the combustion period of fuel injected by main injection; hereinafter, the total combustion period Amount of heat generated per unit volume of fuel in hereinafter) is always the value of the constant (constant different fuel injection amount and fuel injection timing, etc.). In this case, the amount of heat generated per unit volume of the fuel during the combustion period of fuel injected by pilot injection (hereinafter referred to as pilot combustion period) is always a constant value, and further, the fuel injected by main injection The amount of heat generated per unit volume of fuel during this combustion period (hereinafter referred to as the main combustion period) is always a constant value. In other words, the maximum value of the amount of heat generated per unit volume of fuel during each combustion period (the majority of the fuel contributes to the generation of heat when good combustion is performed. The amount of heat generated is always a constant value.

  The amount of heat generated per unit volume of the fuel in each of the combustion periods (total combustion period, pilot combustion period, main combustion period) when the fuel is actually burning in the combustion chamber 3 is good. If the combustion state deteriorates for some reason, the amount of heat generated per unit volume of the fuel deviates from the maximum value (for example, the above value). Less than the maximum). In the present invention, the presence or absence of deterioration of the combustion state is determined by utilizing this principle.

  Specifically, for each of the amount of heat generated per unit volume of fuel during the total combustion period, the amount of heat generated per unit volume of fuel during the pilot combustion period, and the amount of heat generated per unit volume of fuel during the main combustion period, The maximum value of the amount of heat generated per unit volume of fuel (hereinafter referred to as “reference heat generation efficiency”) is defined. Then, the amount of heat generated per unit volume of the actual fuel (hereinafter referred to as “actual heat generation efficiency”) is compared with the above “reference heat generation efficiency”, and the difference between them (actual heat generation relative to the above reference heat generation efficiency) The presence or absence of deterioration of the combustion state in the combustion chamber 3 (presence or absence of deterioration of the combustion state during the pilot combustion period and presence or absence of deterioration of the combustion state during the main combustion period) is determined based on the amount of deviation in efficiency) (Determining whether there is combustion deterioration by the combustion deterioration determining means).

  Hereinafter, the maximum value of the heat generation amount per unit volume of fuel during the total combustion period is referred to as “total combustion reference heat generation efficiency”, and the maximum value of the heat generation amount per unit volume of fuel during the pilot combustion period is referred to as “pilot”. It is referred to as “combustion reference heat generation efficiency”, and the maximum value of the amount of heat generated per unit volume of fuel in the main combustion period is referred to as “main combustion reference heat generation efficiency”. The amount of heat generated per unit volume of the actual fuel during the total combustion period is referred to as “total combustion actual heat generation efficiency”, and the amount of heat generated per unit volume of the actual fuel during the pilot combustion period is referred to as “pilot combustion actual heat”. The amount of heat generated per unit volume of the actual fuel during the main combustion period is referred to as “main combustion actual heat generation efficiency”.

  The amount of heat generated per unit volume of fuel here refers to the fuel injected from the injector 23 until the end of the combustion period to be inspected (hereinafter referred to as the inspection target period) (according to the fuel injection amount command value). (Amount of fuel) is a value obtained by dividing the amount of heat generated by combustion during the inspection target period by the amount of fuel corresponding to the fuel injection amount command value. In other words, it is the average value of the amount of heat generated per unit volume of fuel in the inspection target period. Further, in order to calculate the amount of heat generated per unit volume of the fuel, it is necessary to determine the amount of fuel corresponding to the fuel injection amount command value. That is, it is necessary that the fuel injection with this fuel amount be completed. For this reason, the end of the inspection target period is set as a timing after the point in time when fuel injection of fuel that performs combustion in the inspection target period is completed. Specifically, when the pilot combustion period is set as the inspection target period, the end of the inspection target period is set as a timing after the time point when the pilot injection is completed. In this case, the end of the inspection target period is set as a timing before the start time of the main combustion period. Similarly, when the main combustion period is set as the inspection target period, the end of the inspection target period is set as a timing after the time when the main injection is completed.

  Further, the total combustion actual heat generation efficiency is calculated by adding the heat generation amount during the pilot combustion period and the heat generation amount during the main combustion period to the fuel injection amount corresponding to the fuel injection amount command value for the pilot injection and the main combustion amount. It is obtained by dividing by the sum (total value) of the fuel injection amount corresponding to the fuel injection amount command value for injection. Similarly, the pilot combustion actual heat generation efficiency is obtained by dividing the heat generation amount during the pilot combustion period by the fuel injection amount corresponding to the fuel injection amount command value for the pilot injection. The main combustion actual heat generation efficiency is obtained by dividing the heat generation amount in the main combustion period by the fuel injection amount corresponding to the fuel injection amount command value for the main injection.

  In the following description, in order to facilitate understanding of the present invention, it is assumed that one pilot injection and one main injection are performed, and the inspection target period is the entire period of the pilot combustion period (pilot An explanation will be given of a combustion state evaluation method in the case where two periods are set, that is, a period from the start point to the end point of combustion) and an entire period of the main combustion period (a period from the start point to the end point of main combustion). Further, the case where the heat generation rate in the main combustion period occurs after the heat generation rate in the pilot combustion period becomes “0” will be described as an example. When the end point of the inspection target period is set to a predetermined crank angle position instead of the above combustion end point, or when the inspection target period is set as a part of the period from the combustion start point to the combustion end point The evaluation method of the combustion state in each of these will be described later.

  FIG. 5 is a diagram showing a heat release rate waveform and a fuel injection rate waveform for explaining a combustion state evaluation method. As shown in FIG. 5, when the pilot injection is executed, the combustion of the fuel is started with a slight delay (ignition delay) after the start of the injection (timing T1 in FIG. 5), and the period until the combustion center of gravity is reached. In that case, the heat generation rate gradually increases. Then, after reaching the combustion center of gravity, the heat generation rate gradually decreases, and when the combustion of most of the fuel is completed, the heat generation rate becomes “0” (timing T2 in FIG. 5). Also, when the main injection is executed, the combustion of the fuel is started with a slight delay (ignition delay) after the start of the injection (timing T2 in FIG. 5; in this case, the combustion of the fuel injected by the pilot injection) The end point of time coincides with the start point of combustion of the fuel injected in the main injection), and during the period until the center of gravity of combustion is reached, the heat generation rate gradually increases. Then, after reaching the combustion center of gravity, the heat generation rate gradually decreases, and when the combustion of most of the fuel is completed, the heat generation rate becomes “0” (timing T3 in FIG. 5). For example, the timing T1 (start timing of pilot combustion) is 6 degrees before compression top dead center (BTDC 6 °), and the timing T2 (start timing of main combustion) is 3 degrees after compression top dead center (ATDC3). The timing T3 (end timing of main combustion) is 25 degrees after compression top dead center (ATDC 25 °).

  When evaluating the combustion state in such combustion, the amount of heat generated per unit volume of fuel in the total combustion period (period T1 to timing T3 in FIG. 5) is within a predetermined range (based on the total combustion reference heat generation efficiency). And the amount of heat generated per unit volume of fuel during the pilot combustion period (the period from timing T1 to timing T2 in FIG. 5) is within the predetermined range (the above-mentioned pilot range). The fuel generation per unit volume during the main combustion period (the period from timing T2 to timing T3 in FIG. 5), or not, within the allowable range set in advance based on the combustion reference heat generation efficiency The amount of heat is within a predetermined range (allowable range set in advance based on the main combustion reference heat generation efficiency) And so as to evaluate the combustion state by respectively determining whether present in).

  The combustion start timing (timing T1 and timing T2) and the combustion end timing (timing T3) are acquired based on the change in the in-cylinder pressure detected by the in-cylinder pressure sensor 4B. Further, the ignition delay period after fuel injection may be calculated from the in-cylinder environment (sensing values of various sensors), thereby obtaining the combustion start timing (timing T1 and timing T2). Furthermore, timings obtained in advance by reference combustion (combustion based on the ideal heat generation rate waveform described above) may be set as the timings T1, T2, and T3.

  First, as described above, when ideal combustion is performed, the amount of heat generated per unit volume of fuel over the entire combustion period becomes the maximum value. That is, the oxygen concentration and oxygen excess rate in the combustion chamber 3 are sufficiently ensured, the in-cylinder temperature has reached the self-ignition temperature of the fuel, and an appropriate amount of fuel corresponding to the fuel injection amount command value is obtained. When injected from the injector 23, most of the injected fuel burns well. For this reason, the amount of heat generated per unit volume of the fuel in each combustion period (total combustion period, pilot combustion period, main combustion period) becomes a maximum value. In other words, the total combustion actual heat generation efficiency substantially matches the total combustion reference heat generation efficiency, the pilot combustion actual heat generation efficiency approximately matches the pilot combustion reference heat generation efficiency, and the main combustion actual heat generation efficiency is the main combustion reference heat generation efficiency. The efficiency is almost the same.

As a specific value, in the case of light oil, the maximum value of heat generated per unit volume of fuel (reference heat generation efficiency) is 30 J / mm ³ . This value is an experimentally obtained value. In addition, since the calorific value per unit mass of light oil is 42.94 kJ / g and the density of light oil is 0.834 × 10 ⁻³ g / mm ³ , the maximum value of generated heat per unit volume is theoretically Although the above is 35.8 J / mm ³ , the actual fuel (light oil) does not contribute to heat generation in the combustion stroke in the combustion chamber 3 (for example, fuel that burns in the exhaust stroke, Therefore, the maximum value of heat generated per unit volume of the actual fuel (reference heat generation efficiency) is 30 J / mm ³ . That is, the general engine 1 is operating at an execution rate of 83.8% (= 30 / 35.8).

Incidentally, since the reference heat generation efficiency can be defined as described above, the amount of generated heat (the maximum value of the generated heat amount) when ideal combustion is performed is obtained based on the reference heat generation efficiency and the fuel injection amount. (Maximum value of heat generation (J) = reference heat generation efficiency (J / mm ³ ) × fuel injection amount (mm ³ )). Therefore, based on the maximum value of this generated heat amount (the generated heat amount obtained from the reference heat generation efficiency and the fuel injection amount; hereinafter referred to as the reference heat generation amount), the actual heat generation amount relative to this reference heat generation amount It is also possible to determine the presence or absence of combustion deterioration in the combustion chamber 3 based on the amount of deviation, and the present invention includes such a determination method within the scope of the technical idea. That is, “comparing the reference heat generation efficiency with the actual heat generation efficiency and determining the presence or absence of deterioration of combustion in the combustion chamber based on the amount of deviation (the claims)” The value obtained by multiplying the fuel injection amount (reference heat generation amount) with the value obtained by multiplying the actual heat generation efficiency by the fuel injection amount (actual heat generation amount), and combustion in the combustion chamber based on these deviations It is synonymous with “determining the presence or absence of deterioration”. Specifically, when the fuel injection amount is 20 mm ³ , the reference heat generation amount is 600 J, and the presence or absence of deterioration in combustion in the combustion chamber 3 based on the amount of deviation of the actual heat generation amount from this reference heat generation amount Will be judged.

The inventor of the present invention conducted an experiment to confirm that the reference heat generation efficiency was 30 J / mm ³ .

FIG. 6 shows that ideal combustion (oxygen concentration and excess oxygen ratio in the combustion chamber 3 is sufficiently ensured in the combustion chamber 3 by varying the fuel injection amounts (injection amounts of pilot injection and main injection). The experiment results when the in-cylinder temperature reaches the self-ignition temperature of the fuel and combustion is performed when an amount of fuel corresponding to the fuel injection amount command value is injected from the injector 23 are shown. . 6A shows a heat generation rate waveform and a fuel injection rate waveform for each fuel injection, and FIG. 6B shows a fuel injection amount (fuel injection amount in pilot injection) and heat generation efficiency (fuel in the total combustion period). And the amount of heat generated per unit volume). The solid line in FIG. 6 indicates the case where the pilot injection amount is 16 mm ³ and the main injection amount is 19 mm ³ , the broken line indicates the case where the pilot injection amount is 12 mm ³ and the main injection amount is 23 mm ³ , and the alternate long and short dash line indicates the pilot injection amount Is 8 mm ³ and the main injection amount is 27 mm ³ . As is apparent from FIG. 6B, even if the fuel injection amount of each injection is different, the amount of heat generated per unit volume (reference heat generation efficiency) when ideal combustion is performed is about 30 J / It is mm ³ .

FIG. 7 shows experimental results when ideal combustion is performed in the combustion chamber 3 at various fuel injection pressures (rail pressures). FIG. 7A shows a heat generation rate waveform and a fuel injection rate waveform for each fuel injection pressure, and FIG. 7B shows a relationship between the fuel injection pressure and the heat generation efficiency. FIG. 7A shows the experimental results when the fuel injection pressure is set higher in the order of the one-dot chain line, the broken line, and the solid line. As is clear from FIG. 7B, even if the fuel injection pressure is different, the amount of heat generated per unit volume of fuel (reference heat generation efficiency) when ideal combustion is performed is about 30 J / mm ³ . It has become.

FIG. 8 shows an experiment in which ideal combustion is performed in the combustion chamber 3 by varying the fuel injection timing (injection timing of the second pilot injection when two pilot injections are executed). Results are shown. FIG. 8A shows a heat generation rate waveform and a fuel injection rate waveform for each fuel injection timing, and FIG. 8B shows a relationship between the fuel injection timing and the heat generation efficiency. FIG. 8A shows an experimental result when the injection timing of the second pilot injection is advanced in the order of the one-dot chain line, the broken line, and the solid line. As is apparent from FIG. 8B, even if the fuel injection timing is different, the amount of heat generated per unit volume of fuel (reference heat generation efficiency) when ideal combustion is performed is about 30 J / mm ³ . It has become.

Further, FIG. 9 shows experimental results when ideal combustion is performed in the combustion chamber 3 at various oxygen excess rates. FIG. 9A shows a heat generation rate waveform and a fuel injection rate waveform for each oxygen excess rate, and FIG. 9B shows a relationship between the oxygen excess rate and the heat generation efficiency. FIG. 9A shows the experimental results when the oxygen excess rate is increased in the order of the one-dot chain line, the broken line, and the solid line. As is apparent from FIG. 9B, even if the oxygen excess rate is different, the amount of heat generated per unit volume of fuel when the oxygen excess rate is in an appropriate range and ideal combustion is performed ( The standard heat generation efficiency is about 30 J / mm ³ .

Thus, in the case of light oil, the maximum value of the amount of heat generated per unit volume of fuel over the entire combustion period is about 30 J / mm ³ . That is, if the amount of heat generated per unit volume of the fuel over the entire period from the start of combustion to the end of combustion in the actual combustion of fuel in the combustion chamber 3 is about 30 J / mm ³ , the combustion is injected. It can be determined that the most part of the fuel is an ideal combustion.

Using this principle, in this embodiment, each actual heat generation efficiency (total combustion actual heat generation efficiency, pilot combustion actual heat generation efficiency, main combustion actual heat generation efficiency) is converted into each reference heat generation efficiency (total combustion standard). Whether the heat generation efficiency, pilot combustion reference heat generation efficiency, main combustion reference heat generation efficiency; 30 J / mm ³ ) are within a preset allowable range (hereinafter simply referred to as “permissible range”) The combustion state is evaluated based on whether or not (the amount of deviation from the reference heat generation efficiency is within an allowable range). As the allowable range, when the reference heat generation efficiency is 30 J / mm ³ , for example, a range of “25 J / mm ³ ≦ actual heat generation efficiency ≦ 30 J / mm ³ ” is set. In this case, the threshold value of the deviation amount of the actual heat generation efficiency from the reference heat generation efficiency is “0 J / mm ³ ” on the positive side and “−5 J / mm ³ ” on the negative side.

  As described above, FIG. 5 is a diagram showing a heat generation rate waveform and a fuel injection rate waveform for explaining the combustion state evaluation method. In this case, the total combustion period is a period from timing T1 to timing T3 in the figure. The total amount of heat generated by the combustion of the fuel during this period is detected, and the detected total amount of generated heat is determined as the fuel amount corresponding to the fuel injection amount command value (the fuel injection amount corresponding to the fuel injection amount command value in pilot injection) The total combustion actual heat generation efficiency is calculated by dividing by the sum of the fuel injection amount corresponding to the fuel injection amount command value in the main injection and the sum of the fuel injection amounts). The total amount of heat generated during the total combustion period is obtained based on the in-cylinder pressure detected by the in-cylinder pressure sensor 4B.

  Similarly, the pilot combustion period is a period from timing T1 to timing T2 in the figure. The amount of heat generated by the combustion of the fuel during this period is detected, and the detected amount of generated heat is determined by a fuel amount corresponding to the fuel injection amount command value (a fuel injection amount corresponding to the fuel injection amount command value in pilot injection). The pilot combustion actual heat generation efficiency is calculated by dividing. The amount of heat generated during the pilot combustion period is also obtained based on the in-cylinder pressure detected by the in-cylinder pressure sensor 4B.

  The main combustion period is a period from timing T2 to timing T3 in the figure. The amount of heat generated by the combustion of the fuel during this period is detected, and the detected amount of generated heat is determined by the amount of fuel corresponding to the fuel injection amount command value (fuel injection amount corresponding to the fuel injection amount command value in main injection). By dividing, the main combustion actual heat generation efficiency is calculated. The amount of heat generated during the main combustion period is also obtained based on the in-cylinder pressure detected by the in-cylinder pressure sensor 4B.

-Corrective action according to the evaluation result of the combustion state-
When the actual heat generation efficiency calculated in this way is within the allowable range, ideal combustion is performed in the combustion chamber 3, and it is not necessary to correct the fuel injection mode. to decide. That is, when all of the total combustion actual heat generation efficiency, the pilot combustion actual heat generation efficiency, and the main combustion actual heat generation efficiency are within the allowable range, ideal combustion is performed in the combustion chamber 3. The fuel injection mode is not corrected.

  On the other hand, if any of the actual heat generation efficiencies deviates from the allowable range, the fuel injection mode is corrected (correction operation of the fuel injection mode by the correction unit). This will be specifically described below.

(When total combustion actual heat generation efficiency is within the allowable range)
When the total combustion actual heat generation efficiency is within the allowable range, it can be determined that the fuel injection amounts in the pilot injection and the main injection are appropriately obtained. However, even if the total combustion actual heat generation efficiency is within the allowable range, the pilot combustion actual heat generation efficiency and the main combustion actual heat generation efficiency may deviate from the allowable range. In this case, the following correction operation is performed.

  First, the pilot combustion actual heat generation efficiency may be lower than the allowable range, and the main combustion actual heat generation efficiency may be higher than the allowable range. In this case, if the in-cylinder temperature at the injection timing of the pilot injection is not sufficiently obtained, a part of the fuel injected by the pilot injection cannot be burned in the pilot combustion period, and is burned in the main combustion period. Can be estimated.

  Accordingly, in this case, the pilot injection amount is corrected to increase, and the main injection amount is corrected to decrease by a correction amount substantially the same as the increase correction amount. That is, by correcting the pilot injection amount to increase, the heat amount during the pilot combustion period is sufficiently secured, and the main injection amount is corrected to decrease (the fuel amount is corrected by decreasing the amount of pilot injection combusted during the main combustion period). By offsetting), an excessive increase in output torque is prevented.

  The correction operation in this case is executed for the cylinder that reaches the next combustion stroke with respect to the combustion stroke in which the actual heat generation efficiency is lower than the allowable range. Further, the fuel injection amount correction operation may be performed in the next combustion stroke in the same cylinder.

  The following formula (1) is given as an example of a calculation formula for the increase correction amount of the pilot injection amount and the decrease correction amount of the main injection amount.

Fuel correction amount = Current pilot injection command fuel injection amount × {(1- (Pilot combustion actual heat generation efficiency / Pilot combustion reference heat generation efficiency)} (1)
The pilot injection amount is increased and corrected by the correction amount calculated in this way, and the main injection amount is decreased and corrected. As a result, it is possible to ensure a sufficient amount of heat during the pilot combustion period and to appropriately obtain the output torque.

  On the other hand, although the total combustion actual heat generation efficiency is within the allowable range, the pilot combustion actual heat generation efficiency and the main combustion actual heat generation efficiency may both be lower than the allowable range. In this case, because the in-cylinder temperature at the injection timing of the pilot injection is not sufficiently obtained, a part of the fuel injected by the pilot injection cannot be burned during the pilot combustion period, and further, the fuel injected by the main injection It can be presumed that a part of is not combusted in the main combustion period (period in which combustion of fuel injected by main injection should be completed; period up to 25 degrees after compression top dead center (ATDC 25 °)).

  Therefore, in this case, the pilot injection amount is corrected to be increased. That is, by correcting the pilot injection amount to be increased, a sufficient amount of heat during the pilot combustion period is secured, the ignition delay of the fuel injected in the main injection is eliminated, and within the main combustion period (25 after compression top dead center). (Within a period up to ATDC 25 °) so that proper main combustion is performed. As a result, the output torque is appropriately obtained.

  The correction operation in this case is also executed for the cylinder that reaches the next combustion stroke with respect to the combustion stroke in which the actual heat generation efficiency is lower than the allowable range. Further, the fuel injection amount correction operation may be performed in the next combustion stroke in the same cylinder.

  In addition, as a countermeasure when the pilot combustion actual heat generation efficiency and the main combustion actual heat generation efficiency are both lower than the above allowable range even though the total combustion actual heat generation efficiency is within the allowable range as described above. The fuel injection pressure (rail pressure) may be reduced. According to this, by reducing the volume of the combustion field of fuel injected by pilot injection and increasing the density of normal cetane (linear molecular structure capable of low-temperature oxidation reaction) present in this combustion field, By increasing the density of thermal energy in the combustion field, the combustion field can be heated to a high temperature, that is, the cylinder can be preheated sufficiently, and the ignition delay of the fuel injected in the main injection can be eliminated. .

(When total combustion actual heat generation efficiency is below the allowable range)
When the total combustion actual heat generation efficiency is less than or equal to the allowable range, it can be determined that at least one of the fuel injection amounts in the pilot injection and the main injection is insufficient. In this case, the following correction operation is performed.

  First, when both the pilot combustion actual heat generation efficiency and the main combustion actual heat generation efficiency are lower than the allowable range, the pilot injection amount and the main injection amount are both corrected to increase. That is, by increasing the pilot injection amount, a sufficient amount of heat is ensured during the pilot combustion period, and by increasing the main injection amount, the output torque is ensured. The calculation of the increase correction amount is performed by the same calculation operation as the above equation (1).

  Although the pilot injection amount increase correction and the main injection amount increase correction are performed, the pilot combustion actual heat generation efficiency and the main combustion actual heat generation efficiency are improved (so as to approach the reference heat generation efficiency). If not improved, it is determined that the cause of the fact that the pilot combustion actual heat generation efficiency and the main combustion actual heat generation efficiency are both lower than the allowable range is an abnormality in the intake system 6, and the pilot injection amount and A correction operation for increasing the amount of oxygen introduced into the combustion chamber 3 is performed while the main injection amount is corrected to decrease (return to the fuel injection amount before the increase correction). For example, the supercharging amount is increased by decreasing the EGR gas amount by decreasing the opening of the EGR valve 81 or by controlling the variable nozzle vane mechanism of the supercharger 5.

  On the other hand, when the total combustion actual heat generation efficiency is below the allowable range, the main combustion actual heat generation efficiency is within the allowable range, whereas the pilot combustion actual heat generation efficiency is lower than the allowable range. In this case, the pilot injection amount is corrected to increase. That is, the amount of heat during the pilot combustion period is sufficiently secured by correcting the pilot injection amount to be increased.

  Even in this case, if the pilot combustion actual heat generation efficiency is not improved (improved so as to approach the reference heat generation efficiency) despite the pilot injection amount increase correction, the pilot combustion actual heat The cause of the generation efficiency being lower than the allowable range is determined to be an abnormality in the intake system 6, and the pilot injection amount is corrected to decrease (return to the fuel injection amount before the increase correction) and the combustion chamber 3 A correction operation is performed to increase the amount of oxygen introduced into the. For example, the supercharging amount is increased by decreasing the EGR gas amount by decreasing the opening of the EGR valve 81 or by controlling the variable nozzle vane mechanism of the supercharger 5.

(When the total combustion actual heat generation efficiency is above the allowable range)
When the total combustion actual heat generation efficiency is equal to or greater than the allowable range, for example, when the total combustion reference heat generation efficiency is 30 J / mm ³ , the total combustion actual heat generation efficiency is 32 J / mm ^3. It is determined that the amount of fuel actually injected is larger than the injection amount command value, and the pilot injection amount and the main injection amount are corrected to decrease.

  As described above, in the present embodiment, the presence or absence of deterioration of the combustion state is determined by comparing the reference heat generation efficiency and the actual heat generation efficiency in the total combustion period and each inspection target period (pilot combustion period and main combustion period). Like to do. These reference heat generation efficiency and actual heat generation efficiency can be obtained quantitatively even if the type of engine and the fuel injection amount are different. For this reason, in this embodiment, it is not necessary to individually define the evaluation criteria of the combustion state for each type of engine and each fuel injection amount, and systematic combustion common to various engines and various fuel injection amounts. It is possible to establish a condition evaluation standard. As a result, the evaluation criteria for the combustion state can be quantified, and the evaluation operation can be simplified.

  Further, since the reference heat generation efficiency and the actual heat generation efficiency are compared (comparing numerical values), it is determined whether or not the combustion state in the combustion chamber 3 has deteriorated. Combustion conditions can be evaluated by relatively simple calculations, compared to those that evaluate combustion conditions by comparing each other (pattern matching), and determination criteria for determining the presence or absence of deterioration of combustion conditions can be set easily. Become.

  In addition, the reference heat generation efficiency and the actual heat generation efficiency are obtained as an average value of the amount of heat generated per unit volume of the fuel in the total combustion period and each inspection target period. As a result, it is possible to obtain high accuracy in determining whether the combustion state has deteriorated.

  Furthermore, according to the present embodiment, it is possible to optimize the fuel injection amount in the pilot injection. That is, it is possible to eliminate the need for the fine injection amount learning (also called the fine Q learning) that has been conventionally performed in order to optimize the fine injection amount. This conventional minute injection amount learning is performed with a very small amount equivalent to the pilot injection amount when there is no injection when the command injection amount to the injector becomes zero (for example, when the accelerator opening becomes “0” during traveling). Fuel is injected toward a specific cylinder (a cylinder where the piston is near compression top dead center) (hereinafter, this fuel injection is referred to as “single injection”), and the amount of change in engine speed associated with this single injection ( Engine operation state change amount), and the engine operation state change amount data when the single injection of a predetermined amount is accurately executed and the engine operation state change amount when the single injection is actually performed. In comparison, the learning value of the pilot injection amount setting map is corrected in accordance with the deviation amount. In other words, learning execution opportunities are limited and useless fuel injection is required. According to the present embodiment, since the reference heat generation efficiency and the actual heat generation efficiency can be compared during normal operation of the engine 1, the minute injection amount (pilot injection amount) can be optimized. The minute injection amount learning can be made unnecessary. In addition, detecting the pressure change in the injector as a method for measuring the fuel injection amount has been proposed in the past, but in this case, since the combustion state in the combustion chamber is not recognized, its reliability is low. Met. In the present embodiment, since the fuel injection amount is adjusted by evaluating the combustion state in the combustion chamber 3, it is possible to adjust the fuel injection amount with high accuracy.

-Modification-
In the above-described embodiment, one pilot injection and one main injection are performed, and after the heat generation rate in the pilot combustion period becomes “0”, heat generation in the main combustion period is performed. The case where the rate has occurred was explained. Below, the case where the combustion state is evaluated for other combustion modes will be described.

(Modification 1)
In this modification, when the heat generation rate waveform in pilot injection and the heat generation rate waveform in main injection overlap, that is, until the combustion of fuel injected in pilot injection ends, the main injection is performed. When the combustion of the fuel is started, the combustion state of the fuel injected by the pilot injection and the combustion state of the fuel injected by the main injection are evaluated.

  FIG. 10 is a diagram showing a heat release rate waveform and a fuel injection rate waveform for explaining a combustion state evaluation method in such a case.

  In this example, the end of the pilot combustion period is set as the main injection execution start time, and each of the reference heat generation efficiencies (total combustion reference heat generation efficiency, pilot combustion reference heat generation efficiency, main combustion reference heat generation efficiency) Setting and calculation of each actual heat generation efficiency (total combustion actual heat generation efficiency, pilot combustion actual heat generation efficiency, main combustion actual heat generation efficiency) are performed.

In this case, since the combustion of the fuel injected by the pilot injection continues after the main injection execution start time, the pilot combustion reference heat generation efficiency in the pilot combustion period is set to a value lower than 30 J / mm ^3. Will be. For example, it is set as 20 J / mm ³ . This value is defined in advance by experiments, simulations, or the like.

On the other hand, in the main combustion period, part of the fuel injected by the pilot injection is also burned, so the main combustion reference heat generation efficiency in this main combustion period is set to a value higher than 30 J / mm ^3. Will be. For example, it is set as 32 J / mm ³ . This value is also defined in advance through experiments, simulations, and the like.

  Other evaluation methods and the combustion improvement operation after the evaluation are the same as those in the above-described embodiment.

(Modification 2)
In this modification, when two pilot injections and one main injection are executed, the combustion state of the fuel injected by the pilot injection is evaluated and the combustion state of the fuel injected by the main injection is evaluated. An evaluation is performed.

  FIG. 11 is a diagram showing a heat release rate waveform and a fuel injection rate waveform for explaining a combustion state evaluation method in such a case.

  Also in this example, the end of the pilot combustion period is set as the main injection execution start time, and the above reference heat generation efficiency (total combustion reference heat generation efficiency, pilot combustion reference heat generation efficiency, main combustion reference heat generation efficiency) And actual heat generation efficiency (total combustion actual heat generation efficiency, pilot combustion actual heat generation efficiency, main combustion actual heat generation efficiency) are calculated.

In this case, since the combustion of the fuel injected by the pilot injection (particularly, the second pilot injection) continues even after the main injection execution start time, the pilot combustion reference heat generation efficiency in this pilot combustion period is 30 J / mm. It will be set as a value lower than ³ . For example, it is set as 20 J / mm ³ . This value is defined in advance by experiments, simulations, or the like.

On the other hand, in the main combustion period, part of the fuel injected by the pilot injection is also burned, so the main combustion reference heat generation efficiency in this main combustion period is set to a value higher than 30 J / mm ^3. Will be. For example, it is set as 32 J / mm ³ . This value is also defined in advance through experiments, simulations, and the like.

  Other evaluation methods and the combustion improvement operation after the evaluation are the same as those in the above-described embodiment.

  It is also possible to evaluate the combustion state of the fuel injected in each of the two pilot injections. In this case, the end of the first pilot combustion period is set as the second pilot injection execution start time, and each reference heat generation efficiency (total combustion reference heat generation efficiency, first pilot combustion reference heat generation efficiency, second pilot combustion Setting of reference heat generation efficiency, main combustion reference heat generation efficiency) and each actual heat generation efficiency (total combustion actual heat generation efficiency, first pilot combustion actual heat generation efficiency, second pilot combustion actual heat generation efficiency, main combustion Actual heat generation efficiency) will be calculated.

In this case, since the combustion of the fuel injected in the first pilot injection continues after the second pilot injection execution start time, the first pilot combustion reference heat generation efficiency in this first pilot combustion period is 30 J / mm. It will be set as a value lower than ³ . For example, it is set as 20 J / mm ³ . This value is defined in advance by experiments, simulations, or the like.

  Other evaluation methods and the combustion improvement operation after the evaluation are the same as those in the above-described embodiment.

(Modification 3)
The inspection target period in this modification is a case where the end point is set at a predetermined crank angle position, and the total combustion reference heat generation efficiency and the main combustion reference heat generation efficiency are set to values smaller than the above 30 J / mm ^3. It is to set. For example, a time point 18 degrees after compression top dead center (ATDC 18 °) (a time point on the more advanced side than the time point when main combustion is completed) is set as the end point of the inspection target period.

  In FIG. 12, the start time of the inspection target period is set as the combustion start time of fuel injected by pilot injection (timing T1 in FIG. 12), and the end time of the inspection target period is 18 degrees after compression top dead center (ATDC 18 °; FIG. 12 is a diagram showing a heat release rate waveform and a fuel injection rate waveform for explaining a combustion state evaluation method in the case of timing T4) in FIG.

Even when good combustion is performed in the combustion chamber 3 (see the heat generation rate waveform shown in FIG. 12), the fuel is still burned after the end of the inspection target period (after timing T4) (main timing). In this case, the maximum value of the amount of heat generated per unit volume of fuel in the total combustion period and the main combustion period is 30 J / mm ³ (the entire period of the combustion period). It is set as a value lower than the reference heat generation efficiency in the case of the inspection target period (inspection target period shown in FIG. 5). This is because the heat generation efficiency can be obtained by dividing the amount of heat generated during the inspection target period by the amount of fuel corresponding to the fuel injection amount command value. Since the entire amount of fuel corresponding to the injection amount command value is not combusted, but part of it is combusted, the maximum value of heat generated per unit volume of fuel (reference heat generation efficiency) is 30 J / mm ^The value is lower than ³ . For example, it is set as 25 J / mm ³ . This value is set by multiplying the reference heat generation efficiency (30 J / mm ³ ) when the entire period of the combustion period is the inspection target period by a predetermined ratio. For example, it is obtained by multiplying the ratio of the heat generation amount in the inspection target period to the heat generation amount in the entire combustion period when ideal combustion is performed. Further, it may be obtained by experiments or simulations.

That is, ideal combustion in the combustion chamber 3 (the oxygen concentration and the oxygen excess rate in the combustion chamber 3 are sufficiently secured, the in-cylinder temperature has reached the self-ignition temperature of the fuel, and the fuel injection amount command value When the amount of fuel corresponding to the fuel is injected from the injector 23), the reference heat generation efficiency at the time when 18 degrees after the compression top dead center is reached is obtained in advance. The reference heat generation efficiency is compared with the actual heat generation efficiency, and the actual heat generation efficiency is within a preset allowable range for 25 J / mm ³ (for example, 20 J / mm ³ ≦ actual heat generation efficiency ≦ 25 J / mm ^{If it is 3} ), it can be judged that the combustion is an ideal combustion. In other words, the combustion state is evaluated based on whether or not the actual heat generation efficiency is within this allowable range (whether or not the deviation from the reference heat generation efficiency is within the allowable range). Become.

  The evaluation method and the combustion improvement operation after the evaluation in this example are the same as those in the above-described embodiment.

  In the case of this example, since the calculation of the actual heat generation efficiency can be started when the timing T4 is reached, the acquisition timing of the actual heat generation efficiency can be obtained at an early stage, and the presence or absence of combustion deterioration in the combustion chamber 3 It is possible to make an early determination.

(Modification 4)
The inspection target period in this modification is a case where the start time is set at a predetermined crank angle position, and the total combustion reference heat generation efficiency and the pilot combustion reference heat generation efficiency are set to values smaller than the above 30 J / mm ^3. It is to set. For example, a time point of 4 degrees before compression top dead center (BTDC 4 °) is set as the start point of the examination target period.

  In FIG. 13, the start time of the inspection target period is 4 degrees before compression top dead center (BTDC 4 °; timing T5 in FIG. 13), and the end time of the inspection target period is the combustion end time of the fuel injected by the main injection (FIG. 13). 13 is a diagram showing a heat generation rate waveform and a fuel injection rate waveform for explaining a combustion state evaluation method in the case of timing T3) in FIG.

Even when good combustion is performed in the combustion chamber 3 (see the heat generation rate waveform shown in FIG. 13), fuel combustion (pilot) has already occurred before the start of the inspection target period (before timing T5). In this case, the maximum amount of generated heat per unit volume of fuel during the total combustion period and pilot combustion period is set to a value lower than 30 J / mm ^3. Will be. For example, it is set as 28 J / mm ³ . This value is also set by multiplying the reference heat generation efficiency (30 J / mm ³ ) when a whole period of the combustion period is the inspection target period by a predetermined ratio. For example, it is obtained by multiplying the ratio of the heat generation amount in the inspection target period to the heat generation amount in the entire combustion period when ideal combustion is performed. Further, it may be obtained by experiments or simulations.

That is, ideal combustion in the combustion chamber 3 (the oxygen concentration and the oxygen excess rate in the combustion chamber 3 are sufficiently secured, the in-cylinder temperature has reached the self-ignition temperature of the fuel, and the fuel injection amount command value When the amount of fuel corresponding to the fuel is injected from the injector 23), the reference heat generation efficiency in the inspection target period is obtained in advance, and the reference heat generation efficiency and actual heat generation are obtained. comparing the efficiency, the actual heat generation efficiency preset within an allowable range with respect to 28 J / mm ³ (for example, 24J / mm ³ ≦ actual heat generation efficiency ≦ 28J / mm ³⁾ if I becomes, The combustion can be determined to be ideal combustion. In other words, the combustion state is evaluated based on whether or not the actual heat generation efficiency is within this allowable range (whether or not the deviation from the reference heat generation efficiency is within the allowable range). Become.

  The evaluation method and the combustion improvement operation after the evaluation in this example are the same as those in the above-described embodiment.

(Modification 5)
The inspection target period in this modification is a case where the start time point and the end time point are set at predetermined crank angle positions, and each reference heat generation efficiency (total combustion reference heat generation efficiency, pilot combustion reference heat generation efficiency, Main combustion reference heat generation efficiency) is set as a value smaller than 30 J / mm ³ . For example, a time point of 4 degrees before compression top dead center (BTDC 4 °) is set as the start point of the inspection target period, and a time point of 18 degrees after compression top dead center (ATDC 18 °) is set as the end point of the inspection target period. .

  In FIG. 14, the start time of the examination target period is 4 degrees before compression top dead center (BTDC 4 °; timing T5 in FIG. 14), and the end time of the examination target period is 18 degrees after compression top dead center (ATDC 18 °; FIG. 14). It is a figure which shows the heat release rate waveform and fuel injection rate waveform for demonstrating the evaluation method of the combustion state in the case of setting to timing T4).

Even when good combustion is performed in the combustion chamber 3 (see the heat generation rate waveform shown in FIG. 14), fuel combustion (pilot) has already occurred before the start of the inspection target period (before timing T5). Since the combustion of the fuel injected by the injection) has started and the combustion of the fuel (combustion of the fuel injected by the main injection) is still continued after the end of the inspection period (after timing T4), In this case, the maximum value of heat generation per unit volume of fuel (reference heat generation efficiency) is set to a value lower than 30 J / mm ³ . For example, it is set as 20 J / mm ³ . This value is also set by multiplying the reference heat generation efficiency (30 J / mm ³ ) when a whole period of the combustion period is the inspection target period by a predetermined ratio. For example, it is obtained by multiplying the ratio of the heat generation amount in the inspection target period to the heat generation amount in the entire combustion period when ideal combustion is performed. Further, it may be obtained by experiments or simulations.

That is, when ideal combustion is performed in the combustion chamber 3, the reference heat generation efficiency in the inspection target period is obtained in advance, and the reference heat generation efficiency is compared with the actual heat generation efficiency. If the actual heat generation efficiency is within a preset allowable range for 20 J / mm ³ (for example, 16 J / mm ³ ≦ actual heat generation efficiency ≦ 20 J / mm ³ ), the combustion is ideal. It can be judged that it is combustion. In other words, the combustion state is evaluated based on whether or not the actual heat generation efficiency is within this allowable range (whether or not the deviation from the reference heat generation efficiency is within the allowable range). Become.

  The evaluation method and the combustion improvement operation after the evaluation in this example are the same as those in the above-described embodiment.

  In the above-described embodiment and each modification, the end timing of the pilot combustion period (the pilot combustion inspection period) is set to a timing at which the heat generation rate in the pilot combustion becomes “0”. The compression top dead center (TDC) of the piston 13 may be set. According to this, when the piston 13 reaches the compression top dead center (TDC), the volume of the combustion chamber 3 is minimized, the in-cylinder temperature due to the compression of air becomes the highest temperature, and the in-cylinder preheating efficiency is the highest. Since it is in a high state, it is possible to evaluate the combustion state accurately reflecting the state of in-cylinder preheating by pilot combustion by setting the period up to this timing as the inspection target period of pilot combustion, which is effective.

-Modification of reference value and actual value-
In the above-described embodiment and each modification, the maximum value of the amount of generated heat per unit volume of fuel in the inspection target period is set as the reference heat generation efficiency, and this is set as the reference value for evaluating the combustion state. In addition, the actual amount of heat generated per unit volume of fuel during the inspection target period was defined as the actual heat generation efficiency, and this was the actual value for evaluating the combustion state.

  Instead, in this modification, the “reference heat generation amount” obtained by multiplying the reference heat generation efficiency by the fuel injection amount commanded by the fuel injection amount command value is used to evaluate the combustion state. It is defined as a reference value, and the combustion state is evaluated by comparing the reference heat generation amount with the heat amount actually generated in the inspection target period (actual heat generation amount).

  In the case of this example, since the reference heat generation amount is calculated based on the reference heat generation efficiency, it is calculated as a quantitative value corresponding to the fuel injection amount regardless of the type of engine. For this reason, it is not necessary to prescribe the combustion condition evaluation criteria individually for each type of engine and each fuel injection amount, and systematic combustion state evaluation criteria common to various engines and various fuel injection amounts are not required. It becomes possible to establish.

-Other embodiments-
The embodiment and each modification described above have described the case where the present invention is applied to an in-line four-cylinder diesel engine mounted on an automobile. The present invention is applicable not only to automobiles but also to engines used for other purposes. Further, the number of cylinders and the engine type (separate type engine, V-type engine, horizontally opposed engine, etc.) are not particularly limited.

  Moreover, in the said embodiment and modification, the start time of the test object period was prescribed | regulated as the start time of a combustion period. The present invention is not limited to this, and the fuel injection start time may be defined as the start time of the inspection target period. For example, the timing TP in FIG. 5 is defined as the start timing of the inspection target period for combustion of fuel injected by pilot injection, or the timing TM is defined as the start timing of the inspection target period for combustion of fuel injected by main injection. You may do it.

  Moreover, although the said embodiment and modification demonstrated the engine 1 which applied the piezo injector 23 which changes a fuel-injection rate by becoming a valve opening state of full open only during an electricity supply period, this invention is a variable injection-rate injector. It is also possible to apply to engines that apply

  In addition, although the NSR catalyst 75 and the DPNR catalyst 76 are provided as the manipulator 77 in the above-described embodiment and modification, the NSR catalyst 75 and a DPF (Diesel Particle Filter) may be provided.

  Further, in the above embodiment and the modification, the presence or absence of combustion deterioration is determined based on the amount of heat generated per unit volume of the fuel, but the presence or absence of combustion deterioration is determined based on the amount of heat generated per unit mass of fuel. It is also possible to determine. In other words, since there is a correlation between the volume and the mass of the fuel (mass = density × volume), “the amount of heat generated per unit volume of fuel (claims)” is “the amount of heat generated per unit mass of fuel” It is synonymous with.

  INDUSTRIAL APPLICABILITY The present invention is applicable to combustion control for optimizing the amount of heat generated in a combustion chamber in a common rail in-cylinder direct injection multi-cylinder diesel engine mounted on an automobile.

1 engine (internal combustion engine)
23 Injector (fuel injection valve)
3 Combustion chamber 4B In-cylinder pressure sensor 5 Supercharger 8 Exhaust gas recirculation passage 81 EGR valve 100 ECU

Claims (11)

In a control device for a compression self-ignition internal combustion engine in which fuel injection is performed a plurality of times from a fuel injection valve into a combustion chamber according to a fuel injection amount command value, and combustion is performed by self-ignition of these injected fuels.
The total combustion reference heat generation efficiency which is the maximum value of the amount of heat generated per unit volume of the fuel in a predetermined total combustion period including at least a part of each of the fuel combustion periods by the plurality of fuel injections, and the total combustion period And compared with the total combustion actual heat generation efficiency, which is a value obtained by dividing the amount of heat actually generated by the fuel injection amount commanded by the fuel injection amount command value for each of the plurality of fuel injections. ,
Inspection target combustion reference heat generation efficiency which is the maximum value of the amount of heat generated per unit volume of fuel in a predetermined inspection target period including at least a part of the combustion period to be inspected among each combustion by the plurality of fuel injections The actual combustion heat generation efficiency, which is a value obtained by dividing the amount of heat actually generated in the inspection target period by the fuel injection amount commanded by the fuel injection amount command value in order to perform combustion as the inspection target. Compare and
Deterioration of combustion to be inspected based on the deviation amount of the total combustion actual heat generation efficiency with respect to the total combustion reference heat generation efficiency and the deviation amount of the inspection target combustion actual heat generation efficiency with respect to the inspection target combustion reference heat generation efficiency A control device for an internal combustion engine, characterized in that combustion deterioration determining means for determining the presence or absence of combustion is provided. The control apparatus for an internal combustion engine according to claim 1,
The total combustion period is set as the entire period of the combustion period of each fuel by the plurality of fuel injections,
The total combustion reference heat generation efficiency is the maximum value of the amount of heat generated per unit volume of the fuel in the entire combustion period of each fuel by the plurality of fuel injections, while the total combustion actual heat generation efficiency is The amount of heat actually generated during the entire combustion period of each fuel by multiple fuel injections is divided by the total amount of fuel injections commanded by the fuel injection amount command value for each of the multiple fuel injections. A control device for an internal combustion engine, characterized in that it is a value. The control apparatus for an internal combustion engine according to claim 1,
The total combustion period is set as a part of the combustion period of each fuel by the plurality of fuel injections,
The total combustion reference heat generation efficiency is defined by a value obtained by multiplying the maximum value of the amount of heat generated per unit volume of fuel during the entire combustion period of each fuel by the multiple fuel injections by a predetermined ratio. On the other hand, the total combustion actual heat generation efficiency is calculated based on the fuel injection amount commanded by the fuel injection amount command value for each of the plurality of fuel injections. A control device for an internal combustion engine, wherein the control device is a value obtained by dividing the sum by the total amount. The control apparatus for an internal combustion engine according to claim 1,
The above inspection period is set as the entire period of the combustion period to be inspected,
While the inspection target combustion reference heat generation efficiency is the maximum value of the amount of heat generated per unit volume of the fuel during the entire combustion period to be inspected, the inspection target combustion actual heat generation efficiency is the same as the inspection target. An internal combustion engine having a value obtained by dividing the amount of heat actually generated during the entire combustion period by the fuel injection amount commanded by the fuel injection amount command value in order to perform the combustion to be inspected Control device device. The control apparatus for an internal combustion engine according to claim 1,
The inspection period is set as a part of the combustion period to be inspected,
The inspection target combustion reference heat generation efficiency is defined by a value obtained by multiplying the maximum value of the amount of generated heat per unit volume of fuel in the entire combustion period to be inspected by a predetermined ratio, The inspection target combustion actual heat generation efficiency is a value obtained by dividing the amount of heat actually generated in the inspection target period by the fuel injection amount commanded by the fuel injection amount command value in order to perform combustion as the inspection target. An internal combustion engine control device apparatus. In the control device for an internal combustion engine according to any one of claims 1 to 5,
As fuel injection from the fuel injection valve into the combustion chamber, at least when main injection and sub-injection performed prior to the main injection are executed,
The deviation amount of the total combustion actual heat generation efficiency with respect to the total combustion reference heat generation efficiency does not exceed a predetermined threshold, and the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the sub-injection is the inspection target combustion standard. Control of an internal combustion engine, characterized in that a correction means is provided for increasing and correcting the fuel injection amount in the sub-injection when the heat generation efficiency is lower and the deviation amount exceeds a predetermined threshold value. apparatus. In the control device for an internal combustion engine according to any one of claims 1 to 5,
As fuel injection from the fuel injection valve into the combustion chamber, at least when main injection and sub-injection performed prior to the main injection are executed,
The deviation amount of the total combustion actual heat generation efficiency with respect to the total combustion reference heat generation efficiency does not exceed a predetermined threshold, and the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the sub-injection is the inspection target combustion standard. The heat generation efficiency is below and the amount of deviation exceeds a predetermined threshold, and the actual combustion heat generation efficiency of the inspection target in the combustion of the fuel injected by the main injection is higher than the inspection target combustion reference heat generation efficiency. In this case, the control device for the internal combustion engine is provided with a correction means for correcting the increase in the fuel injection amount in the sub-injection and correcting the decrease in the fuel injection amount in the main injection. In the control device for an internal combustion engine according to any one of claims 1 to 5,
As fuel injection from the fuel injection valve into the combustion chamber, at least when main injection and sub-injection performed prior to the main injection are executed,
The deviation amount of the total combustion actual heat generation efficiency with respect to the total combustion reference heat generation efficiency does not exceed a predetermined threshold, and the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the sub-injection is the inspection target combustion standard. The heat generation efficiency is lower than the predetermined threshold, and the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the main injection is lower than the inspection target combustion reference heat generation efficiency. In addition, the internal combustion engine is provided with correction means for correcting both the fuel injection amount in the sub-injection and the fuel injection amount in the main injection when the deviation amount exceeds a predetermined threshold. Engine control device. In the control device for an internal combustion engine according to any one of claims 1 to 5,
As fuel injection from the fuel injection valve into the combustion chamber, at least when main injection and sub-injection performed prior to the main injection are executed,
The total combustion actual heat generation efficiency is lower than the total combustion reference heat generation efficiency, and the amount of deviation exceeds a predetermined threshold, and the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the sub-injection is The inspection target combustion reference heat generation efficiency is lower than the inspection target combustion reference heat generation efficiency and the deviation amount exceeds a predetermined threshold, and the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the main injection is the inspection target combustion reference heat generation efficiency. And when the deviation exceeds a predetermined threshold value, there is provided correction means for correcting the increase in both the fuel injection amount in the sub-injection and the fuel injection amount in the main injection. A control device for an internal combustion engine. In the control device for an internal combustion engine according to any one of claims 1 to 5,
As fuel injection from the fuel injection valve into the combustion chamber, at least when main injection and sub-injection performed prior to the main injection are executed,
The total combustion actual heat generation efficiency is lower than the total combustion reference heat generation efficiency, and the amount of deviation exceeds a predetermined threshold, and the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the sub-injection is The inspection target combustion reference heat generation efficiency of the inspection target combustion actual heat generation efficiency in the combustion of the fuel injected by the main injection is less than the inspection target combustion reference heat generation efficiency and the deviation amount exceeds a predetermined threshold. A control device for an internal combustion engine, characterized in that a correction means for increasing the fuel injection amount in the sub-injection is provided when the amount of deviation from the engine does not exceed a predetermined threshold. In the control device for an internal combustion engine according to any one of claims 1 to 5,
As fuel injection from the fuel injection valve into the combustion chamber, at least when main injection and sub-injection performed prior to the main injection are executed,
When the total combustion actual heat generation efficiency exceeds the total combustion reference heat generation efficiency and the deviation amount exceeds a predetermined threshold, the fuel injection amount in the sub-injection and the fuel injection in the main injection A control device for an internal combustion engine, characterized in that a correction means for correcting the amount to decrease is provided.

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