JP2007332877A - Control unit of internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To accurately detect fuel properties through a simple structure in a control unit of an internal combustion engine. <P>SOLUTION: Whether a condition where cetane value of fuel is detectable is established or not is determined (step 100). When establishment of the condition is determined, control is performed to set the closing timing of an intake valve 52 later than usual (step 102). The magnitude of engine rotation fluctuation is successively detected (step 104). A cetane value is calculated based on the detected magnitude of engine rotation fluctuation (step 106). According to the above processing, since the actual compression ratio is reduced by delaying the closing of the intake valve 52, the temperature and pressure at about the compression top dead center are reduced. Therefore, the influence of fuel of low cetane value on engine rotation fluctuation can be amplified. Consequently, the cetane value can be accurately detected. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a control device for an internal combustion engine, and more particularly, to a control device for an internal combustion engine having a function of detecting a property of fuel.

  The properties of the fuel greatly affect the performance of the internal combustion engine and the exhaust gas. There are variations in fuel properties depending on the refining method of crude oil, the country of production, the region where the fuel is sold, and the like. In the case of a fuel for a diesel engine, one of the fuel properties is a cetane number representing good or bad ignitability. If a low cetane number fuel, that is, a fuel with poor ignitability is used, it tends to cause misfire. If misfire occurs, the emission of smoke and HC increases, and thus the emission tends to deteriorate, or the torque decreases and the torque fluctuation increases.

  In particular, the above problems are likely to occur under the recent severe exhaust gas regulations. This is because it is necessary to accurately control the state of combustion in order to satisfy strict exhaust gas regulations, so that the margin for changes in fuel properties is small.

  Japanese Patent Application Laid-Open No. 2004-308431 observes the transition of the engine speed after starting the engine to the idle speed, and is a heavy fuel with properties that are difficult to vaporize when there is a drop in the engine speed. An apparatus that discriminates the above is disclosed. According to this apparatus, fuel heavier than the intended fuel property is used, and if the engine speed drops after starting, it can be determined that the fuel is heavy.

JP 2004-308431 A JP 2001-98993 A JP 2003-269202 A

  However, in the above-described conventional apparatus, the fuel property cannot be detected if the engine speed after the start does not drop. For example, when a lighter fuel than the intended fuel property is used, the engine property does not drop after the start, so the fuel property cannot be detected.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a control device for an internal combustion engine that can accurately detect fuel properties with a simple configuration.

In order to achieve the above object, a first invention is a control device for an internal combustion engine,
In-cylinder temperature and pressure reducing means capable of creating a in-cylinder temperature and pressure drop state in which the temperature and / or pressure in the cylinder near the compression top dead center of the internal combustion engine is lower than normal,
Engine rotation fluctuation detecting means for detecting engine rotation fluctuation in the in-cylinder temperature pressure drop state;
Fuel property determination means for determining the property of the fuel used in the internal combustion engine based on the engine rotation fluctuation detected in the in-cylinder temperature pressure drop state;
It is characterized by providing.

The second invention is the first invention, wherein
The internal combustion engine is a diesel engine;
The property of the fuel is a cetane number or a value correlated with the cetane number.

The third invention is the first or second invention, wherein
The in-cylinder temperature pressure reducing means includes an actual compression ratio reducing means for reducing the actual compression ratio as compared with the normal time.

Moreover, 4th invention is set in 3rd invention,
A variable valve mechanism that varies the valve timing of the intake valve of the internal combustion engine;
The actual compression ratio reducing means reduces the actual compression ratio by changing the closing timing of the intake valve by controlling the variable valve mechanism.

According to a fifth invention, in any one of the first to fourth inventions,
An EGR device for recirculating exhaust gas of the internal combustion engine to an intake passage of the internal combustion engine;
The in-cylinder temperature pressure reducing means includes EGR gas temperature reducing means for reducing the temperature of the EGR gas as compared with the normal time.

According to a sixth invention, in any one of the first to fifth inventions,
The in-cylinder temperature / pressure reduction means creates the in-cylinder temperature / pressure drop state when the internal combustion engine is idling.

According to a seventh invention, in any one of the first to sixth inventions,
An EGR device for recirculating exhaust gas of the internal combustion engine to an intake passage of the internal combustion engine;
The in-cylinder temperature pressure reducing means includes
An actual compression ratio reducing means for reducing the actual compression ratio as compared to the normal time;
EGR gas temperature reduction means for lowering the temperature of the EGR gas as compared with normal time;
It is characterized by including.

  According to the first aspect of the present invention, it is possible to detect engine rotation fluctuations in a cylinder temperature and pressure drop state where the temperature and / or pressure in the cylinder near the compression top dead center of the internal combustion engine is lower than normal. . Based on the detected engine rotation fluctuation, the fuel property can be determined. According to the first aspect of the present invention, the influence of the fuel properties on the engine rotation fluctuation can be increased by intentionally creating the in-cylinder temperature pressure drop state and making the conditions strict. For this reason, it is possible to accurately determine the fuel property based on the engine rotation fluctuation. Therefore, the fuel property can be detected with high accuracy.

  According to the second invention, in the diesel engine, the cetane number or a value correlated with the cetane number can be detected with high accuracy. By using the value related to the detected cetane number, various operating parameters of the diesel engine can be corrected to appropriate values according to the cetane number of the fuel currently used. For this reason, misfire can be prevented from occurring even in situations where misfire is likely to occur, for example, when traveling at high altitudes or during transient operation. Therefore, it is possible to avoid the occurrence of adverse effects such as deterioration of emissions and torque reduction.

  According to the third aspect of the present invention, the temperature and / or pressure in the cylinder near the compression top dead center can be effectively reduced by reducing the actual compression ratio as compared with the normal time when detecting the fuel property. . For this reason, the fuel property can be detected with higher accuracy.

  According to the fourth invention, the actual compression ratio can be lowered by changing the closing timing of the intake valve by the variable valve mechanism. For this reason, the actual compression ratio can be easily reduced with a simple structure when detecting the fuel properties.

  According to the fifth aspect of the invention, when the fuel property is detected, the temperature and / or pressure in the cylinder near the compression top dead center is effectively reduced by lowering the temperature of the EGR gas recirculated by the EGR device as compared with the normal time. Can be lowered. For this reason, the fuel property can be detected with higher accuracy.

  According to the sixth aspect of the present invention, the in-cylinder temperature and pressure drop state can be created when the internal combustion engine is idling. Therefore, it is possible to more reliably prevent the temperature and / or pressure near the compression top dead center from becoming a problem in the operation of the internal combustion engine when detecting the fuel property.

  According to the seventh invention, at the time of detecting the fuel property, both the actual compression ratio is reduced as compared with the normal time, and the temperature of the EGR gas recirculated by the EGR device is decreased as compared with the normal time. The temperature and / or pressure in the cylinder near the compression top dead center can be effectively reduced. For this reason, the fuel property can be detected with higher accuracy.

  Embodiments of the present invention will be described below with reference to the drawings. In addition, the same code | symbol is attached | subjected to the element which is common in each figure, and the overlapping description is abbreviate | omitted.

Embodiment 1 FIG.
[Description of system configuration]
FIG. 1 is a diagram for explaining a system configuration according to the first embodiment of the present invention. The system shown in FIG. 1 includes a four-cycle diesel engine (compression ignition internal combustion engine) 10. It is assumed that the diesel engine 10 is mounted on a vehicle and used as a power source. Although the illustrated diesel engine 10 is an in-line four-cylinder type, in the present invention, the number of cylinders and the cylinder arrangement of the engine are not limited thereto.

  Each cylinder of the diesel engine 10 is provided with an injector 12 that injects fuel directly into the cylinder. The injectors 12 of each cylinder are connected to a common common rail 14. In the common rail 14, high-pressure fuel pressurized by the supply pump 16 is stored. Then, fuel is supplied from the common rail 14 to each injector 12. The injector 12 can inject fuel into the cylinder a plurality of times during one cycle.

  An exhaust passage 18 of the diesel engine 10 is branched by an exhaust manifold 20 and connected to an exhaust port 22 (see FIG. 2) of each cylinder. The diesel engine 10 according to this embodiment includes a turbocharger 24. The exhaust passage 18 is connected to the exhaust turbine of the turbocharger 24.

  An exhaust purification device 26 that purifies exhaust gas is provided in the exhaust passage 18 downstream of the turbocharger 24. As the exhaust purification device 26, for example, one of an oxidation catalyst, a NOx storage reduction type or selective reduction type NOx catalyst, a DPF (Diesel Particulate Filter), a DPNR (Diesel Particulate-NOx-Reduction system), or a combination thereof Etc. can be used.

  An air cleaner 30 is provided near the inlet of the intake passage 28 of the diesel engine 10. The air drawn through the air cleaner 30 is compressed by the intake compressor of the turbocharger 24 and then cooled by the intercooler 32. The intake air that has passed through the intercooler 32 is distributed by the intake manifold 34 to the intake ports 35 (see FIG. 2) of the respective cylinders.

  An intake throttle valve 36 is installed between the intercooler 32 and the intake manifold 34 in the intake passage 28. Further, an air flow meter 38 for detecting the amount of intake air is installed in the vicinity of the intake passage 28 downstream of the air cleaner 30.

  One end of the high pressure EGR passage 40 is connected to the exhaust passage 18 in the vicinity of the exhaust manifold 20. The other end of the high pressure EGR passage 40 is connected to the intake passage 28 in the vicinity of the intake manifold 34. An EGR cooler 42 is provided in the middle of the high-pressure EGR passage 40. The EGR cooler 42 can cool the exhaust gas passing through the EGR cooler 42 with the cooling water of the diesel engine 10. An EGR valve 44 that adjusts the amount of exhaust gas passing through the high-pressure EGR passage 40 is provided in the middle of the high-pressure EGR passage 40 and downstream of the EGR cooler 42.

  One end of a low pressure EGR passage 66 is connected to the exhaust passage 18 on the downstream side of the exhaust purification device 26. The other end of the low pressure EGR passage 66 is connected to the intake passage 28 upstream of the turbocharger 24. An EGR valve 68 that adjusts the amount of exhaust gas passing through the low pressure EGR passage 66 is provided in the middle of the low pressure EGR passage 66. Note that one end of the low pressure EGR passage 66 may be connected between the turbocharger 24 and the exhaust purification device 26.

  In the system shown in FIG. 1, a part of the exhaust gas can be recirculated to the intake passage 28 through the high pressure EGR passage 40 and the low pressure EGR passage 66, that is, external EGR (Exhaust Gas Recirculation) can be performed. In the system shown in FIG. 1, as described above, two high-pressure and low-pressure external EGR paths are provided, but in the first embodiment, the external EGR path is one of the normal ones. It may be.

  The system of the present embodiment further includes an accelerator opening sensor 48 that detects the amount of depression of the accelerator pedal (accelerator opening) and an ECU (Electronic Control Unit) 50. The ECU 50 is connected to the various sensors and actuators described above. The ECU 50 controls the operating state of the diesel engine 10 by driving each actuator according to a predetermined program based on the output of each sensor.

  FIG. 2 is a view showing a cross section of one cylinder of the diesel engine 10 in the system shown in FIG. Hereinafter, the diesel engine 10 will be further described with reference to FIG. As shown in FIG. 2, a crank angle sensor 62 that detects the rotation angle (crank angle) of the crankshaft 60 is attached in the vicinity of the crankshaft 60 of the diesel engine 10. The crank angle sensor 62 is connected to the ECU 50. According to the signal of the crank angle sensor 62, the engine rotation speed can also be detected.

  Further, the diesel engine 10 is provided with an intake variable valve mechanism 54 that varies the valve opening characteristics of the intake valve 52. The intake variable valve mechanism 54 can change the closing timing of the intake valve 52. The intake variable valve mechanism 54 may be capable of further changing the opening timing, the operating angle, the lift amount, etc. in addition to the closing timing of the intake valve 52. The specific mechanism of the intake variable valve mechanism 54 is not particularly limited. For example, a mechanical mechanism such as a mechanism that continuously varies the phase of a cam shaft (not shown) that drives the intake valve 52. In addition to a simple mechanism, an electromagnetically driven valve or a hydraulically driven valve that can be opened and closed at any timing can be used. The intake variable valve mechanism 54 is connected to the ECU 50.

  FIG. 3 is a diagram showing the lift characteristics of the intake valve 52. The broken line in FIG. 3 is the lift characteristic of the intake valve 52 at the normal time. According to the intake variable valve mechanism 54, the closing timing of the intake valve 52 can be made later than normal. The solid line in FIG. 3 is the lift characteristic when the intake valve 52 is closed late.

  The compression stroke in the diesel engine 10 substantially starts after the intake valve 52 is closed. For this reason, if the closing timing of the intake valve 52 is delayed, the substantial compression stroke is shortened, so that the actual compression ratio (substantial compression ratio) can be reduced.

  The diesel engine 10 shown in FIG. 2 is also provided with an exhaust variable valve mechanism 58 on the exhaust valve 56 side. However, in this embodiment, the exhaust variable valve mechanism 58 may not be provided. That is, the exhaust valve 56 may be driven by a normal valve mechanism.

[Features of Embodiment 1]
The combustion of the diesel engine 10 is greatly influenced by the cetane number of the fuel. When a fuel having a low cetane number, that is, a fuel with poor ignitability is used, misfire is likely to occur. In particular, misfires are more likely to occur during transient operation where the engine load and engine speed change, or when traveling on high altitudes with low atmospheric pressure. In the following, with reference to FIG.

  FIG. 4 is a diagram showing the relationship between the cetane number of fuel used, the ease of misfire, and atmospheric pressure. As shown in the figure, when a fuel having a low cetane number is used compared to a standard cetane number fuel, the ease of misfire increases. Moreover, even if the cetane number is the same, the lower the atmospheric pressure, the easier the misfire. This is due to the following reason.

  The ease of fuel ignition is largely due to the temperature and pressure in the cylinder at the time of fuel injection, that is, the temperature and pressure in the cylinder when the piston 64 is near the compression top dead center. Affected. The higher the temperature near the compression top dead center and the higher the pressure, the easier it is to ignite. That is, it becomes difficult to misfire. On the other hand, when the atmospheric pressure decreases, the density of air decreases and the amount of air in the cylinder decreases. For this reason, since the temperature and pressure in the vicinity of the compression top dead center are lowered, misfire is easily caused.

In the example shown in FIG. 4, when the atmospheric pressure P ₀ is flat, the ease of misfire is less than the allowable limit for not only standard cetane number fuel but also low cetane number fuel. In contrast, when the atmospheric pressure at high altitude travel is lowered to P ₁ is a standard cetane number of the fuel misfire ease is still equal to or less than the allowable limit, a misfire ease at low cetane number of the fuel Has exceeded the allowable limit. Thus, in general, the lower the cetane number of the fuel, the less room for misfire. In the case of a fuel whose cetane number is lower than the example shown in FIG. 4, the ease of misfire may exceed the allowable limit even at the atmospheric pressure P _{0 on} a flat ground.

  When a misfire or a state close to a misfire occurs, adverse effects such as deterioration of emissions, a decrease in torque, and an increase in torque fluctuation occur. For this reason, when a low cetane number fuel is used, the operation parameters of the diesel engine 10 (for example, the fuel injection timing, the number of injections when the fuel is injected in multiple times, the injection amount at each time, the valve timing) It is desirable to correct the EGR rate in a direction that makes misfires less likely to occur. For this purpose, it is necessary to accurately detect the cetane number of the fuel being used. Therefore, in this embodiment, the cetane number of the fuel is detected as follows.

(Method for detecting cetane number)
If a misfire or a state close to misfire (hereinafter, both are simply referred to as “misfire”) is likely to occur, the engine rotation fluctuation (engine speed fluctuation) increases. This is because, in one cycle, the torque in the cycle in which misfire has occurred is lower than that in the cycle in which misfire has occurred, so the engine speed drops immediately after the misfire. Further, when misfire occurs, exhaust gas containing unburned fuel is discharged. When the exhaust gas is recirculated by EGR, in addition to the fuel injected into the cylinder, the unburned fuel contained in the EGR gas burns excessively in the cylinder. For this reason, if a misfire occurs, an excessive torque may be generated in several cycles later, and the engine speed may increase instantaneously. For this reason, the engine rotation fluctuation increases as the misfire tends to occur.

  FIG. 5 is a diagram showing an example of engine rotation fluctuation when a standard cetane number fuel is used and when a low cetane number fuel is used. As shown in FIG. 5, the engine rotation speed periodically varies due to compression work and expansion work generated in each cylinder. And the lower the cetane number, the easier it is to misfire, so the engine rotation fluctuation becomes larger. The degree of engine rotation fluctuation can be determined from the height h of the engine rotational speed for each cycle and the difference Δh between the heights of adjacent mountains. Therefore, for example, the value of h or Δh can be measured over an appropriate period, and the average of these values can be used as the magnitude of engine rotation fluctuation.

  Here, as described above, the ease of ignition depends on both the temperature and pressure in the cylinder near the compression top dead center. That is, if the temperature near the compression top dead center is the same, the higher the pressure, the easier it is to ignite. If the pressure near the compression top dead center is the same, the higher the temperature, the easier it is to ignite. Therefore, in this embodiment, the ease of ignition combining the temperature and pressure near the compression top dead center will be referred to as “temperature and pressure near the compression top dead center”.

  FIG. 6 is a graph showing the magnitude of the engine rotation fluctuation calculated as described above on the vertical axis and the temperature and pressure near the compression top dead center on the horizontal axis for a plurality of fuels having different cetane numbers. FIG. The four graphs in FIG. 6 are assumed to have a high cetane number in the order of (1) to (4). Of these, (1) is a fuel having a standard cetane number, and (2) to (4) are fuels having a cetane number lower than the standard.

  As shown in FIG. 6, the lower the cetane number, the greater the engine rotational fluctuation. For this reason, if the relationship as shown in FIG. 6 is examined in advance and the magnitude of the engine rotational fluctuation of the diesel engine 10 is measured, the cetane number can be determined based on the magnitude of the engine rotational fluctuation. It is. On the other hand, even if the cetane number is the same, if the temperature / pressure in the vicinity of the compression top dead center is low, misfiring is likely to occur, and the engine rotational fluctuation becomes large.

  In the present embodiment, the cetane number is detected when the diesel engine 10 is idling. FIG. 6 is a graph at the time of idling.

TP _{0 in} FIG. 6 is the temperature and pressure near the compression top dead center during normal idling. Even when the temperature and pressure in the vicinity of the compression top dead center is TP ₀ , there is no change in the relationship that the engine rotational fluctuation increases as the cetane number decreases. However, the difference in the engine rotational fluctuation due to the difference in cetane number is small. That is, at the time of normal idling, the difference in the magnitude of engine rotation fluctuation is small between the case where the standard cetane number fuel is used and the case where the low cetane number fuel is used. For this reason, there is a problem that it is difficult to accurately detect the cetane number.

Here, in the diesel engine 10, as described above, the actual compression ratio can be reduced from the normal time by delaying the closing timing of the intake valve 52 by the intake variable valve mechanism 54. If the actual compression ratio is lowered, the temperature and pressure near the compression top dead center are lowered. TP _{1 in} FIG. 6 is the temperature and pressure in the vicinity of the compression top dead center at the time of idling when the actual compression ratio is lowered by the slow closing of the intake valve 52.

When the temperature and pressure near the compression top dead center decrease, the ignitability of the fuel deteriorates. For this reason, when the temperature and pressure in the vicinity of the compression top dead center are lowered from TP ₀ to TP ₁ , the engine in the case where the standard cetane number fuel is used and the case where the low cetane number fuel is used is used. The difference in the magnitude of the rotational fluctuation increases (see FIG. 6). For this reason, when the actual compression ratio is lowered than usual, the cetane number can be determined with higher accuracy.

  Therefore, in this embodiment, the cetane number of the fuel is detected by the following method. First, when the diesel engine 10 is idling, a state in which the actual compression ratio is lowered is created by delaying the closing timing of the intake valve 52. Next, engine rotation fluctuation is detected under this state. Then, based on the relationship as shown in FIG. 6 stored in advance, a cetane number corresponding to the detected magnitude of the engine rotation fluctuation is calculated. According to such processing, the cetane number can be detected with high accuracy.

[Specific Processing in Embodiment 1]
FIG. 7 is a flowchart of a routine executed by the ECU 50 in the present embodiment in order to realize the above function. Note that this routine is periodically executed at predetermined time intervals. According to the routine shown in FIG. 7, first, it is determined whether or not a condition capable of detecting the cetane number is satisfied (step 100). In the present embodiment, the cetane number is detected when the diesel engine 10 is performing stable idling. This is because at idling time, even if the engine rotational fluctuation becomes a little larger, it does not matter so much. Therefore, in step 100, whether or not the engine is in a stable idling state is determined based on signals from the crank angle sensor 62, the accelerator opening sensor 48, and the like.

  In addition, as a condition for detecting the cetane number, it may be added that the load of the auxiliary machinery is stable. In that case, in step 100 described above, for example, conditions such as the air conditioner being turned off and the operation of the device consuming a large amount of electric power are further determined. In the case where the cetane number is detected in a state where the loads of the auxiliary machinery are stable, it is possible to reliably prevent the engine rotation fluctuation due to the load fluctuation of the auxiliary machinery. For this reason, erroneous detection can be reliably prevented, and the cetane number can be detected with higher accuracy.

In step 100, if the condition for detecting the cetane number is not satisfied, the current processing cycle is terminated as it is. On the other hand, if it is confirmed that the condition for detecting the cetane number is satisfied, then the control for making the closing timing of the intake valve 52 later than the normal time is performed (step 102). Specifically, the intake variable valve mechanism 54 is controlled so that the lift characteristic of the intake valve 52 indicated by the broken line in FIG. 3 is realized. By the processing in step 102, the temperature and pressure near the compression top dead center are decreased from TP ₀ to TP _{1 in} FIG.

  Subsequently, the magnitude of the engine rotation fluctuation is calculated according to a predetermined method (step 104). Specifically, as described above with reference to FIG. 5, for example, the value of the peak height h of the engine rotation speed for each cycle or the difference Δh between the heights of adjacent peaks is the value of the crank angle sensor 62. Based on the signal, it is measured over an appropriate period, and an average value thereof is calculated as the magnitude of the engine rotation fluctuation.

Next, a cetane number is calculated based on the magnitude of the engine rotation fluctuation calculated in step 104 (step 106). Specifically, the following processing is performed. First, a value obtained by subtracting the magnitude of the engine speed fluctuation at the time of normal idling from the magnitude of the engine speed fluctuation calculated in step 104, that is, a value similar to R _{1 to} R _{4 in} FIG. 6 is calculated. Is done. This value R will be referred to as a rotation fluctuation expansion range. It is assumed that the magnitude of engine rotation fluctuation during normal idling is detected in advance and stored in ECU 50. It is assumed that the ECU 50 stores in advance the relationship between the cetane number of the fuel and the rotation fluctuation expansion width R. Such a relationship can be obtained from experimental data as shown in FIG. In step 106, the cetane number of the fuel currently used in the diesel engine 10 can be calculated based on the above relationship stored in the ECU 50. The calculated cetane number value is stored in the ECU 50.

In the above step 106, when the rotational fluctuation enlargement range R is smaller than R ₁ in FIG. 6, it can be determined that the high-octane fuel than the standard.

  According to the routine processing shown in FIG. 7 described above, the cetane number of the fuel currently used in the diesel engine 10 can be detected with high accuracy. The detected cetane number value can be used, for example, as follows. That is, the correction value when correcting various operation parameters during high altitude traveling or in a transient operation state can be set to an optimum value according to the detected cetane number.

  As an example, the advance correction of the fuel injection timing during the transient operation will be briefly described below. At the time of transient operation when the accelerator pedal is depressed and the required torque increases rapidly, a request to rapidly increase the fuel injection amount occurs to satisfy the required torque. However, even if the opening degree of the intake throttle valve 36 is increased after the accelerator pedal is depressed, there is a time delay until the air in the cylinder increases. Therefore, until the in-cylinder air sufficiently increases, the in-cylinder air amount is smaller than the target with respect to the increased fuel injection amount. For this reason, the temperature and pressure in the vicinity of the compression top dead center are lower than the original, and a situation in which misfire is likely to occur. Under such circumstances, there may be a case where control is performed to prevent misfire by making the fuel injection timing easier to make the combustion easier.

  On the other hand, if the fuel injection timing is advanced, combustion noise increases. For this reason, depending on the driving state of the diesel engine 10 or the running conditions of the vehicle, there is a case where control for suppressing the fuel injection timing from being advanced too much is performed at the same time so that the combustion noise does not become too large.

  In the case as described above, the advancement degree of the fuel injection timing and the degree of suppression thereof can be corrected to an optimum value according to the cetane number. For example, when it is detected that fuel with a low cetane number is used, the advance angle of the fuel injection timing is made larger than usual, or the suppression degree of the injection advance angle is made smaller than usual. As a result, the final fuel injection timing can be controlled to shift to the advance side from the normal time. Using the cetane number detected by the routine processing shown in FIG. 7, for example, by performing the control as described above, it is possible to effectively prevent misfire even when a low cetane number is used. Can be suppressed.

  Further, according to the present embodiment, at the time of idling, by intentionally creating a severe operating state in which the temperature and pressure near the compression top dead center are lowered, the influence of the low cetane number fuel on the engine rotation fluctuation is deliberately created. Can be bigger. For this reason, the cetane number can be detected with high accuracy.

  In addition, according to the present embodiment, the cetane number can be detected in advance before a situation in which an influence due to a low cetane number is likely to occur, that is, a situation such as high altitude traveling or a transient operation state. Therefore, the correction at the time of traveling at a high altitude or during transient operation as in the above example can be reliably performed.

  In the present embodiment, the cetane number is determined based on the engine rotation fluctuation. By doing in this way, a cetane number can be detected with a higher precision compared with the case where a cetane number is determined based on the fall of output torque, the vibration which arises in an engine, etc., for example. This is because the output torque and the engine vibration are greatly affected by conditions other than the ease of misfire, whereas the influence of the ease of misfire appears strongly in the engine rotation fluctuation.

  Further, in the present embodiment, when detecting the cetane number, the detection accuracy is improved by deliberately creating a situation in which misfire is likely to occur by reducing the temperature and pressure near the compression top dead center. Yes. On the other hand, as a method of creating a situation where misfire is likely to occur, it is conceivable to retard the fuel injection timing. However, the method of delaying the fuel injection timing has a small margin until the situation where the misfire frequently occurs. For this reason, when the fuel injection timing is delayed, in the worst case, misfires may occur frequently and the engine may be stopped.

  On the other hand, the method of reducing the temperature and pressure near the compression top dead center has a large margin until a situation where misfire frequently occurs is greater than the method of retarding the fuel injection timing. For this reason, according to the present embodiment, it is possible to reliably prevent a situation such as an engine stoppage during the control for detecting the cetane number.

  In the first embodiment described above, when the cetane number is detected, the actual compression ratio is reduced by delaying the closing timing of the intake valve 52. However, the method for reducing the actual compression ratio is such a method. It is not limited to. For example, the actual compression ratio may be lowered by advancing the closing timing of the intake valve 52 before the bottom dead center. Further, the method of reducing the actual compression ratio is not limited to the method using the intake variable valve mechanism 54, but the method using the variable compression ratio mechanism that changes the compression ratio by changing the height of the piston 64 or the height of the cylinder block. It may be.

  In the above-described first embodiment, the case where the cetane number is detected as the fuel property has been described as an example. However, the present invention can also be applied to the case where the fuel property other than the cetane number is detected.

  In the first embodiment described above, the case where the present invention is applied to the control of a diesel engine has been described. However, the present invention is not limited to a diesel engine, and is also applied to the control of another internal combustion engine such as a spark ignition engine. Is possible.

  In the first embodiment described above, the ECU 50 executes the process of step 102, so that the “in-cylinder temperature / pressure reducing means” in the first invention executes the process of step 104. The “engine property fluctuation detecting means” according to the first aspect of the present invention is realized by executing the processing of step 106 by the “engine speed fluctuation detecting means” according to the first aspect of the present invention. Further, the “actual compression ratio reducing means” in the third and fourth aspects of the present invention is realized by the ECU 50 executing the processing of step 102 described above.

Embodiment 2. FIG.
Next, the second embodiment of the present invention will be described with reference to FIG. 8. The description will focus on the differences from the first embodiment described above, and the same matters will be simplified or described. Omitted. The present embodiment can be realized by causing the ECU 50 to execute a routine shown in FIG. 8 described later instead of the routine shown in FIG. 7 described above, using the hardware configuration shown in FIGS. 1 and 2. .

[Features of Embodiment 2]
As described above, the system shown in FIG. 1 can perform external EGR through two paths of the high pressure EGR passage 40 and the low pressure EGR passage 66. Hereinafter, EGR performed through the high pressure EGR passage 40 is referred to as “high pressure EGR”, and EGR performed through the low pressure EGR passage 66 is referred to as “low pressure EGR”. In the system according to the present embodiment, during normal operation, the high pressure EGR and the low pressure EGR are performed at a predetermined ratio according to the operation state.

  In the case of high pressure EGR, the temperature of the EGR gas can be lowered by cooling with the EGR cooler 42. On the other hand, in the low pressure EGR, the exhaust gas that has undergone the expansion in the turbocharger 24 and the heat radiation in the exhaust purification device 26 is recirculated. For this reason, the temperature of EGR gas falls also in the case of low pressure EGR.

  During normal operation, generally, the temperature drop caused by passing through the EGR cooler 42 is greater than the temperature drop caused by passing through the turbocharger 24 and the exhaust purification device 26. Therefore, the EGR gas of the high pressure EGR has a lower temperature than the EGR gas of the low pressure EGR. For this reason, even if the EGR rate is the same, the intake air temperature decreases as the ratio of the high pressure EGR increases.

  On the other hand, during idling, the temperature drop caused by passing through the turbocharger 24 and the exhaust gas purification device 26 is greater than the temperature drop caused by passing through the EGR cooler 42. Therefore, the EGR gas of the low pressure EGR has a lower temperature than the EGR gas of the high pressure EGR. For this reason, even if the EGR rate is the same, the larger the ratio of the low pressure EGR, the lower the intake air temperature.

  When the intake air temperature decreases, the temperature and pressure near the compression top dead center decrease. As can be seen from FIG. 6, the lower the temperature and pressure near the compression top dead center, the more the difference in the magnitude of engine rotation fluctuation due to the difference in cetane number. For this reason, in detecting the cetane number by fluctuations in engine rotation, the detection accuracy can be further increased as the temperature and pressure near the compression top dead center are decreased. Therefore, in this embodiment, when detecting the cetane number at idling, in addition to the control for reducing the actual compression ratio from the normal time, the control for reducing the intake air temperature by increasing the ratio of the low pressure EGR from the normal time. It was decided to do.

[Specific Processing in Second Embodiment]
FIG. 8 is a flowchart of a routine executed by the ECU 50 in the present embodiment in order to realize the above function. Hereinafter, in FIG. 8, the same steps as those shown in FIG. 7 are denoted by the same reference numerals, and the description thereof is omitted or simplified.

In the routine shown in FIG. 8, step 102 in FIG. 7 is replaced with step 108. That is, according to the routine shown in FIG. 8, when detecting the cetane number, in addition to the slow closing control of the intake valve 52 similar to that in the first embodiment, the control for increasing the ratio of the low pressure EGR is performed (step S1). 108). As the control for increasing the ratio of the low pressure EGR, specifically, the opening degree of the EGR valve 68 is made larger than usual and the opening degree of the EGR valve 44 is made smaller than usual, thereby maintaining the same EGR rate. Increasing the proportion of low pressure EGR is performed. Thereby, since the ratio of the low temperature EGR gas by low pressure EGR increases, the temperature of EGR gas as a whole can be reduced. As a result, the intake air temperature is lowered, it is possible to further lower than the temperature and pressure TP ₁ of the compression top dead center near the time cetane number detected in the first embodiment.

In the case where the actual compression ratio is lowered by a method of changing the valve timing of the intake valve 52, there is a limit due to mechanical limitations. Therefore, depending on the type of the diesel engine 10, only lowering the actual compression ratio, even if it is not possible to lower the temperature and pressure TP ₁ of the compression top dead center vicinity in performing the cetane number detection sufficiently possible. According to this embodiment, even in such a case, by a combination of increased how the proportion of the low-pressure EGR, the temperature and pressure TP ₁ of the compression top dead center vicinity can be reduced sufficiently. For this reason, the cetane number can be detected with higher accuracy.

  The routine shown in FIG. 8 is the same as the routine shown in FIG. 7 except for the points described above. For this reason, further description of the routine shown in FIG. 8 is omitted.

  In the second embodiment described above, the case where the temperature of the EGR gas is lowered by increasing the ratio of the low pressure EGR has been described. However, the method can lower the temperature of the EGR gas than usual. If so, the same effects as described above can be obtained even when other methods are employed. For example, at the time of detecting the cetane number, the temperature of the EGR gas can be lowered by performing a control to increase the circulating amount of the cooling water to the EGR cooler 42 instead of the control to increase the ratio of the low pressure EGR.

  In the second embodiment described above, when detecting the fuel property (cetane number), the temperature near the compression top dead center is combined with the control for lowering the actual compression ratio and the control for lowering the temperature of the EGR gas. In the present invention, the temperature and pressure in the vicinity of the compression top dead center may be lowered only by the control for lowering the temperature of the EGR gas when the fuel property is detected. Furthermore, in the present invention, the method of reducing the temperature and pressure near the compression top dead center when detecting the fuel property is not limited to the actual compression ratio reduction or the EGR gas temperature reduction, but the temperature near the compression top dead center. Any method may be used as long as at least one of the pressure and the pressure can be reduced.

  In the second embodiment described above, the high pressure EGR passage 40, the EGR cooler 42, the EGR valve 44, the low pressure EGR passage 66, and the EGR valve 68 correspond to the “EGR device” in the fifth aspect of the invention. In addition, the “EGR gas temperature reducing means” according to the fifth aspect of the present invention is realized by the ECU 50 executing the process of step 108.

It is a figure for demonstrating the system configuration | structure of Embodiment 1 of this invention. It is a figure which shows the cross section of one cylinder of the diesel engine in the system shown in FIG. It is a figure which shows the lift characteristic of the intake valve in Embodiment 1 of this invention. It is a figure which shows the relationship between the cetane number of a fuel, the ease of misfire, and atmospheric pressure. It is a figure which shows the example of engine rotation fluctuation | variation by the case where the fuel of a standard cetane number is used, and the case where the fuel of a low cetane number is used. FIG. 6 is a graph showing a plurality of fuels having different cetane numbers, with the vertical axis representing the magnitude of engine rotation fluctuation and the horizontal axis representing the temperature and pressure near the compression top dead center. It is a flowchart of the routine performed in Embodiment 1 of the present invention. It is a flowchart of the routine performed in Embodiment 2 of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Diesel engine 12 Injector 14 Common rail 18 Exhaust passage 20 Exhaust manifold 22 Exhaust port 24 Turbo supercharger 26 Exhaust gas purification device 28 Intake passage 34 Intake manifold 36 Intake throttle valve 38 Air flow meter 40 High pressure EGR passage 44 EGR valve 46 Intake pressure sensor 47 Exhaust temperature sensor 48 Accelerator opening sensor 50 ECU
52 Intake valve 54 Intake variable valve mechanism 56 Exhaust valve 58 Exhaust variable valve mechanism 62 Crank angle sensor 64 Piston 66 Low pressure EGR passage 68 EGR valve

Claims (7)

In-cylinder temperature and pressure reducing means capable of creating a in-cylinder temperature and pressure drop state in which the temperature and / or pressure in the cylinder near the compression top dead center of the internal combustion engine is lower than normal,
Engine rotation fluctuation detecting means for detecting engine rotation fluctuation in the in-cylinder temperature pressure drop state;
Fuel property determination means for determining the property of the fuel used in the internal combustion engine based on the engine rotation fluctuation detected in the in-cylinder temperature pressure drop state;
A control device for an internal combustion engine, comprising: The internal combustion engine is a diesel engine;
2. The control device for an internal combustion engine according to claim 1, wherein the property of the fuel is a cetane number or a value correlated with the cetane number.   3. The control apparatus for an internal combustion engine according to claim 1, wherein the in-cylinder temperature pressure reducing means includes actual compression ratio reducing means for reducing an actual compression ratio as compared with a normal time. A variable valve mechanism that varies the valve timing of the intake valve of the internal combustion engine;
4. The control device for an internal combustion engine according to claim 3, wherein the actual compression ratio reducing means reduces the actual compression ratio by controlling the variable valve mechanism to change the closing timing of the intake valve. . An EGR device for recirculating exhaust gas of the internal combustion engine to an intake passage of the internal combustion engine;
5. The control device for an internal combustion engine according to claim 1, wherein the in-cylinder temperature pressure reducing means includes EGR gas temperature reducing means for reducing the temperature of the EGR gas as compared with a normal time. .   6. The control apparatus for an internal combustion engine according to claim 1, wherein the in-cylinder temperature pressure reducing means creates the in-cylinder temperature pressure drop state when the internal combustion engine is idling. An EGR device for recirculating exhaust gas of the internal combustion engine to an intake passage of the internal combustion engine;
The in-cylinder temperature pressure reducing means includes
An actual compression ratio reducing means for reducing the actual compression ratio as compared to the normal time;
EGR gas temperature reduction means for lowering the temperature of the EGR gas as compared with normal time;
The control apparatus for an internal combustion engine according to any one of claims 1 to 6, characterized by comprising:

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