JP5578451B2 - Exhaust gas purification device for internal combustion engine - Google Patents

Description

  The present invention relates to an exhaust emission control device for an internal combustion engine.

  For example, in a diesel engine, a technique called EGR (Exhaust Gas Recirculation) in which exhaust gas is recirculated (recirculated) from an exhaust pipe to an intake pipe in order to suppress the amount of NOx in the exhaust is known. When performing EGR, it is required to control the valve opening of the EGR pipe so as to achieve an object such that the amount of NOx discharged from the engine becomes an appropriate amount.

  The EGR has two systems: a low pressure EGR pipe that circulates exhaust gas from the downstream side of the turbine of the turbocharger to the upstream side of the compressor, and a high pressure EGR pipe that circulates exhaust gas from the upstream side of the turbine to the downstream side of the compressor. There is a case. This configuration has an advantage that the recirculation amount by the low pressure EGR pipe can be compensated even when the exhaust gas recirculation amount by the high pressure EGR pipe is not sufficient at the time of high load.

  In the case of two systems of EGR, when it is necessary to increase the total amount of EGR, since the reaction rate of low-pressure EGR is slow, it is necessary to assist as much as possible on the high-pressure EGR side. Patent Document 1 listed below discloses a technique in which this control is related to a DPF (Diesel Particulate Filter) equipped in an exhaust pipe in order to collect particulate matter (PM). Specifically, in this document, when the amount of PM accumulated in the DPF is small and the DPF collecting ability is high, the ratio of the high pressure EGR in the total EGR is increased.

JP 2010-203282 A

  However, according to the knowledge of the present inventor, generally, the larger the amount of PM accumulated in the DPF, the more difficult the exhaust gas passes through the DPF, and the higher the pressure on the upstream side of the DPF, that is, the upstream side of the high-pressure EGR pipe. Conversely, the smaller the amount of PM accumulated in the DPF, the lower the pressure on the upstream side of the high-pressure EGR pipe. Therefore, when the amount of accumulated PM in the DPF is small, it is considered that the exhaust gas recirculation amount due to the high pressure EGR tends to be difficult to increase physically.

  However, the technique described in Patent Document 1 does not take this point into consideration, and controls the exhaust gas recirculation amount to be increased by the high pressure EGR when the PM accumulation amount of the DPF is small. Therefore, in the technique of Patent Document 1, when the amount of accumulated PM in the DPF is small, there is a possibility that the exhaust gas recirculation amount due to the high pressure EGR cannot actually be increased to the target value.

  Therefore, it is required to develop a technique for appropriately controlling the ratio between the high pressure EGR and the low pressure EGR in consideration of the property that it is difficult to increase the exhaust gas recirculation amount due to the high pressure EGR when the PM accumulation amount of the DPF is small.

  In the above discussion, it is not difficult to increase the high-pressure EGR recirculation amount when the PM deposition amount of the DPF is large. However, if the high-pressure EGR recirculation amount is increased, exhaust pressure to the turbine is deprived, which may result in insufficient supercharging. Therefore, this point needs to be taken into consideration when setting the target EGR recirculation amount.

  Accordingly, in view of the above, the problem to be solved by the present invention is that, in a configuration equipped with two systems of high pressure EGR and low pressure EGR, if the amount of PM accumulated in the DPF is small, the exhaust gas recirculation amount by the high pressure EGR is physically An internal combustion engine that appropriately controls the high-pressure EGR flow rate and the low-pressure EGR flow rate in consideration of the property that it is difficult to increase the flow rate and the property that there is a possibility of insufficient supercharging when the high-pressure EGR flow rate is increased when the PM accumulation amount is large An object of the present invention is to provide an exhaust purification device.

In order to achieve the above object, an exhaust gas purification apparatus for an internal combustion engine according to the present invention exhausts from upstream of a turbine of a supercharger in an exhaust passage of the internal combustion engine to downstream of a compressor of a supercharger in the intake passage of the internal combustion engine. A high-pressure recirculation passage for recirculating exhaust gas, a low-pressure recirculation passage for recirculating exhaust gas from downstream of the turbine in the exhaust passage to upstream of the compressor in the intake passage, and particulate matter in the exhaust provided to the exhaust passage. A collector for collecting, storage means for storing an exhaust gas recirculation amount physically securable in the high pressure recirculation passage according to the amount of particulate matter accumulated in the collector, and exhaust return of the high pressure recirculation passage when the flow rate is the amount of the deposit is not less than the reference accumulation amount wherein the deposition amount of the particulate matter in the collector in the case is a value adapted to the optimal control of the internal combustion engine, wherein The target exhaust gas recirculation amount in the high pressure recirculation passage is set in a range not exceeding the physically reservable exhaust gas recirculation amount stored in the storage means according to the product amount, and the target exhaust gas recirculation amount in the high pressure recirculation passage is set. Setting means for setting a target exhaust gas recirculation amount in the low pressure recirculation passage according to the setting, and the physically reservable exhaust gas recirculation amount stored in the storage means Is stored so that the amount of exhaust gas recirculation that can be secured is small, and when the accumulation amount is smaller than the reference accumulation amount, the setting means reduces the accumulation amount in the high-pressure recirculation passage. The target exhaust gas recirculation amount is set to be a small amount, and the target exhaust gas recirculation amount in the high pressure recirculation passage is set to be a larger amount as the accumulation amount is larger .

  As a result, the exhaust gas purification apparatus for an internal combustion engine according to the present invention stores the exhaust gas recirculation amount that can be physically secured in the high pressure recirculation passage, and the amount of particulate matter accumulated in the collector is less than a predetermined amount. The recirculation amount in the high-pressure recirculation passage is set within a range that does not exceed the exhaust gas recirculation amount that can be physically secured, and the recirculation amount in the low-pressure recirculation passage is also set accordingly. Therefore, when the accumulation amount in the collector is small, the reflux amount in the high-pressure reflux passage cannot secure the target value (therefore, the total reflux amount of the high pressure and the low pressure does not reach the target value), the emission deteriorates, etc. Is appropriately avoided.

The block diagram in one Example of the exhaust gas purification apparatus of the internal combustion engine of this invention. The flowchart which shows the example of the control processing regarding PM deposition amount estimation. The flowchart which shows the example of the calculation process of the high voltage | pressure EGR recirculation amount and the low pressure EGR recirculation amount. The flowchart which shows the example of a calculation process of an EGR opening degree. The figure which shows the example of the relationship between high pressure EGR recirculation amount and low pressure EGR recirculation amount, and PM deposition amount. The figure which shows the example of the relationship between high pressure EGR recirculation amount and high pressure EGR valve opening. The figure which shows the example of the relationship between the high pressure EGR recirculation amount at the time of normal time and a DPF reproduction | regeneration, low pressure EGR recirculation amount, and PM deposition amount.

  Embodiments of the present invention will be described below with reference to the drawings. First, FIG. 1 is a schematic view of an apparatus configuration in an embodiment of an exhaust purification apparatus 1 (hereinafter, apparatus 1) according to the present invention.

  The device 1 is an embodiment of a control device configured for an internal combustion engine (an engine, for example, a diesel engine) of an automobile vehicle. The apparatus 1 includes an engine 2, an intake pipe 3, an exhaust pipe 4, a supercharger 5 (turbocharger), a DPF 6, a low pressure EGR pipe 7, a high pressure EGR pipe 8, and an electronic control unit 9 (ECU: Electronic Control Unit).

  Air is supplied to the engine 2 through the intake pipe 3. Exhaust gas from the engine 2 is discharged outside the vehicle through the exhaust pipe 4. The intake pipe 3 includes an intake throttle 30, an air flow meter 31, an intercooler 32, a temperature sensor 33, and a pressure sensor 34. The intake air amount is adjusted by adjusting the opening of the intake throttle 30. The air flow meter 31 detects the intake air amount. The intake air is cooled by the intercooler 32 and more air can be sent to the engine 2. A temperature sensor 33 detects the temperature in the intake manifold. A pressure sensor 34 detects the pressure in the intake manifold.

  The exhaust pipe 4 is provided with a pressure sensor 40. The pressure sensor 40 detects the pressure in the exhaust manifold. The supercharger 5 includes a turbine 50 in the exhaust pipe 4 and a compressor 51 in the intake pipe 4, and the compressor 51 to which driving force is transmitted from the turbine 50 driven by the exhaust compresses the intake air so that more air is supplied. Is sent to the engine 2.

  The DPF 6 is a filter that collects PM discharged from the engine 2. For example, the DPF 6 may have a structure in which the inlet side and the outlet side are alternately clogged in a so-called honeycomb structure. PM contained in the exhaust discharged during operation of the engine 2 is collected inside or on the surface of the DPF wall when passing through the DPF 6. The DPF 6 may be a DPF with an oxidation catalyst on which an oxidation catalyst is supported.

  Whenever the estimated value of the PM amount accumulated in the DPF 6 is considered to exceed a predetermined amount, the DPF 6 is burned by raising the temperature of the DPF 6 by post injection after the main injection in the engine cylinder, for example. Just replay it. At this time, for example, as a method of estimating the PM deposition amount in the DPF 6, for example, a pressure difference (front-rear differential pressure) between the inlet side and the outlet side of the DPF 6 is measured, and the measured value and the previously obtained differential pressure-PM deposition are measured. What is necessary is just to estimate PM deposition amount from the map which shows the relationship between quantity.

  The DPF 6 includes a differential pressure sensor 60 and temperature sensors 61 and 62. The differential pressure sensor 60 measures the differential pressure across the DPF 6. The temperature sensor 61 measures the exhaust temperature upstream of the DPF 6. The temperature sensor 62 measures the exhaust temperature downstream of the DPF 6.

  The low pressure EGR pipe 7 and the high pressure EGR pipe 8 are pipes for exhaust gas recirculation (EGR) from the exhaust pipe to the intake pipe. The exhaust gas recirculation through the EGR pipe lowers the combustion temperature in the engine and reduces the amount of NOx emitted from the engine. The low pressure EGR pipe 7 recirculates exhaust gas from the downstream side of the turbine 50 of the supercharger 5 (further downstream of the DPF 6) to the upstream side of the compressor 51. The high pressure EGR pipe 8 recirculates the exhaust gas from the upstream side of the turbine 50 to the downstream side of the compressor 51.

  By providing two EGR systems in this way, at a high load, the required intake pressure by the turbocharger is ensured (the exhaust flow rate to the turbine side is ensured), and the high pressure EGR cannot secure the EGR amount that can be recirculated from the exhaust passage. Therefore, the EGR is executed with the low pressure EGR communicating with the upstream side of the intake passage from the compressor so as not to be affected by the increase of the intake pressure due to turbocharger supercharging. As a result, a sufficient EGR amount can be ensured even under conditions where the intake pressure is supercharged in a high load range.

  The low-pressure EGR pipe 7 and the high-pressure EGR pipe 8 are each provided with a low-pressure EGR valve 70 (low-pressure EGR valve) and a high-pressure EGR valve 80 (high-pressure EGR valve). The low-pressure EGR pipe 7 and the high-pressure EGR pipe 8 are provided with EGR coolers 71 and 81, respectively, to cool the recirculated exhaust gas so as to allow more exhaust gas recirculation.

  The ECU 9 has a normal computer structure composed of a CPU, a RAM, and the like, and manages various calculations and controls of the exhaust purification device 1. In FIG. 1, transfer of representative information between the ECU 9 and each part of the device 1 is shown by dotted lines. For example, the ECU 9 controls the fuel injection in the injector of the engine 2, the opening degree of the intake throttle 30, the opening degree of the low pressure EGR valve 70, the opening degree of the high pressure EGR valve 80, and the like.

  The ECU 9 also acquires measurement values of the air flow meter 31, the temperature sensor 33, the pressure sensors 34 and 40, the differential pressure sensor 60, the temperature sensors 61 and 62, and the like. The ECU 9 has a nonvolatile memory 90 and stores programs and data necessary for controlling the device 1.

  With the above configuration, the apparatus 1 mainly performs control related to the (target) flow rate and valve opening degree in the low pressure EGR pipe 7 and the high pressure EGR pipe 8 according to the processing procedure of FIGS. The processing contents shown in FIGS. 2 to 4 may be programmed in advance and stored in, for example, the memory 90, and the ECU 9 may call up and automatically process the processing contents. The processing in FIGS. 2 to 4 may be repeated at predetermined intervals while the engine 2 of the vehicle equipped with the device 1 is being driven.

  In the process of FIG. 2, first, in S10, the ECU 9 determines whether or not the increment value of the fresh air amount to the engine 2 is smaller than a predetermined threshold value. Here, the fresh air amount is a detected value of the air flow meter 31. Further, the increment value is an increment value from the fresh air amount in the immediately preceding (one previous) processing of the fresh air amount in the current processing when the processing of FIG. 2 is repeatedly performed at predetermined intervals. (Increment values in S20 and S30 described later are also the same). When the increment value of the fresh air amount is smaller than the predetermined threshold value (S10: YES), the process proceeds to S20, and when it is equal to or larger than the predetermined threshold value (S10: NO), the process of FIG.

  Next, in S20, the ECU 9 determines whether or not the increment value of the temperature difference before and after the DPF is smaller than a predetermined threshold value. Here, the temperature difference before and after the DPF is a difference between measured values of the temperature sensor 61 and the temperature sensor 62. When the incremental value of the temperature difference before and after the DPF is smaller than the predetermined threshold value (S20: YES), the process proceeds to S30, and when it is equal to or larger than the predetermined threshold value (S20: NO), the process of FIG.

  Next, in S30, the ECU 9 determines whether or not the increment value of the differential pressure across the DPF is smaller than a predetermined threshold value. Here, the differential pressure across the DPF is a value measured by the differential pressure sensor 60. When the incremental value of the differential pressure across the DPF is smaller than the predetermined threshold value (S30: YES), the process proceeds to S40, and when it is equal to or larger than the predetermined threshold value (S30: NO), the process of FIG.

  When the process proceeds to S40 by the above processing, the fresh air amount, the temperature difference across the DPF 6 and the pressure difference across the DPF 6 are stable. Such a situation is suitable for estimating the amount of PM deposited on the DPF 6. Therefore, in S40, the ECU 9 estimates the amount of PM accumulated in the DPF 6. As an example of the estimation method, as described above, the map showing the relationship between the differential pressure and the PM deposition amount obtained in advance and stored in the memory 90, the actual value of the differential pressure measured by the differential pressure sensor 60, From this, the PM deposition amount can be estimated.

  The numerical value that is the basis of the exhaust gas recirculation amount in each of the low-pressure EGR pipe 7 and the high-pressure EGR pipe 8 is a numerical value (adapted value) obtained by adaptation. Then, for example, a ratio between the low pressure EGR flow rate and the high pressure EGR flow rate may be determined, and the conforming value of all the EGR flow rates may be distributed at the ratio. Here, “fit” means tuning the ECU by repeating an engine control test so that the engine can be optimally controlled, as is well known.

  In the present invention, when the amount of accumulated PM in the DPF 6 is small, the pressure on the upstream side of the DPF 6, that is, the upstream side of the high-pressure EGR pipe 8 is difficult to increase. . When the amount of accumulated PM in the DPF 6 is small, the high-pressure EGR flow rate is reduced from the compatible value to a physically possible level (a value obtained by further subtracting the margin). Then, the low pressure EGR flow rate is increased by an amount corresponding to the decrease in the high pressure EGR flow rate, so that the total EGR flow rate is not changed from the conforming value. In the present invention, such a process is performed only when the PM deposition amount of the DPF 6 is equal to or less than a predetermined amount (in the following example, the PM deposition amount when the EGR flow rate is determined).

  When the PM deposition amount is larger than the predetermined amount, the physically possible high-pressure EGR flow rate becomes a large amount, but the high-pressure EGR amount is not increased beyond the conforming value, and the high-pressure EGR flow rate and the low-pressure EGR flow rate are Both values remain at the relevant values. The reason is that if the high-pressure EGR flow rate is too large as described above, the necessary supercharging pressure may not be ensured (the appropriate supercharging pressure may not be secured with the appropriate values for the high-pressure EGR flow rate and the low-pressure EGR flow rate). Is considered). A more specific example of the above processing procedure will be described with reference to FIG.

  In the process of FIG. 3, first, in S100, the ECU 9 determines whether or not the PM accumulation amount acquired by executing the process procedure of FIG. 2 is smaller than a predetermined amount. Here, the predetermined amount may be, for example, the PM deposition amount used when the conforming value of the EGR flow rate is obtained. When the PM accumulation amount is smaller than the predetermined amount (S100: YES), the process proceeds to S110, and when the PM accumulation amount is the predetermined amount or more (S100: NO), the process proceeds to S160.

  When the process proceeds to S110, the ECU 9 acquires the maximum flow rate that can be physically secured in the high-pressure EGR pipe 8. The maximum flow rate that can be physically secured in the high-pressure EGR pipe 8 is the maximum exhaust flow rate that flows through the high-pressure EGR pipe 8 with the high-pressure EGR valve 80 fully opened.

  This will be described with reference to FIG. In FIG. 5, the predetermined amount used in S100 is indicated by P0. The maximum flow rate that can be physically secured in the high-pressure EGR pipe 8 is indicated by a dotted line E. As the PM deposition amount increases, the pressure on the upstream side of the DPF 6 increases, so the maximum flow rate that can be physically secured in the high-pressure EGR pipe 8 increases.

  Therefore, the dotted line E has a property of increasing monotonously as the PM deposition amount increases. In FIG. 5, the dotted line E is described as a straight line, but the actual characteristics are not limited to this, and there may be a curve that increases monotonously. The characteristic of the dotted line E may be obtained in advance for a given apparatus configuration and stored in the memory 90, for example. And in S110, ECU9 should just call it.

  Next, in S120, the ECU 9 calculates a maximum flow rate that can be set as a target value in the high-pressure EGR pipe 8. The maximum flow rate that can be set as the target value is a numerical value obtained by subtracting the margin from the maximum flow rate that can be obtained (or called) in S110 and that can be physically secured. As a result, the maximum flow rate that can be set as the target value is given by the broken line A in FIG. 5 (however, the portion below P0 is a solid line). In FIG. 5, the margin is indicated by M.

  Next, in S130, the ECU 9 calculates a maximum flow rate that can be set as a target value in the high-pressure EGR pipe 8 corresponding to the current PM accumulation amount. This is a numerical value of the PM deposition amount at the current time point out of the maximum flow rate that can be set as the target value obtained in S120. In FIG. 5, the PM accumulation amount at the present time is indicated by P1. Therefore, A ′ in FIG. 5 is the maximum flow rate that can be set as the target value in the high-pressure EGR pipe 8 corresponding to the current PM deposition amount.

  Next, in S140, the ECU 9 sets a target flow rate in the high pressure EGR pipe 8. In this procedure, the maximum flow rate that can be set as the target value obtained in S140 may be set as the target value.

  Next, in S150, the ECU 9 sets a target flow rate in the low pressure EGR pipe 7. In FIG. 5, the adaptation value of the high pressure EGR reflux amount and the adaptation value of the low pressure EGR reflux amount are indicated by C and D, respectively. By S140, the target flow rate in the high-pressure EGR pipe 8 is set to A ′. That is, the target flow rate in the high-pressure EGR pipe 8 is set to a smaller value from the conforming value by the amount of C-A ′.

  In S150, the target flow rate in the low pressure EGR pipe 7 is increased from the compatible value by a decrease from the compatible value of the target flow rate in the high pressure EGR pipe 8, and is set as the target flow rate in the low pressure EGR pipe 7. Thereby, the total reflux amount (the sum of the high-pressure EGR reflux amount and the low-pressure EGR reflux amount) is kept the same as the conforming value.

  On the other hand, when the process proceeds to S160, that is, when the PM deposition amount is equal to or greater than the predetermined amount P0, the target flow rates in the high pressure EGR pipe 8 and the low pressure EGR pipe 7 are made the same as the respective conforming values for the reasons described above. That is, in S160, the ECU 9 sets the target flow rate of the high pressure EGR pipe 8 to the conforming value C. In S170, the ECU 9 sets the target flow rate of the low pressure EGR pipe 7 to the conforming value D. As a result, as shown in FIG. 5, the target flow rate of the high pressure EGR pipe 8 and the target flow rate of the low pressure EGR pipe 7 become solid lines H and L, respectively, in the region where the PM accumulation amount is equal to or greater than the predetermined amount P0. The above is the processing content of FIG.

  The trends due to the processing of FIG. 3 are summarized as shown in FIG. In the bar graph of FIG. 7, the left side is the high pressure EGR flow rate, and the right side is the low pressure EGR flow rate. A broken line frame represents the maximum flow rate E that can be physically secured in the high-pressure EGR pipe. When the PM accumulation amount increases, the high-pressure EGR flow rate (target value) H increases as E increases until P0, and after P0, it becomes a constant value at a suitable value. Further, the low pressure EGR flow rate L decreases until P0 and becomes a constant value after P0.

  3, when the PM accumulation amount is P0 or more, the high pressure EGR flow rate can be set to a physically possible numerical value, so that the actual high pressure EGR flow rate does not reach the target value. Further, when the PM accumulation amount is equal to or greater than P0, the EGR flow rate (adapted value) that does not cause insufficient supercharging can be obtained. As a result, when the PM deposition amount is equal to or less than P0, the tendency is opposite to the control described in Patent Document 1, and the high-pressure EGR flow rate is made smaller than the conforming value and the low-pressure EGR flow rate is made larger than the conforming value. Note that the matching value C is smaller by M from the dotted line E at P0 in FIG. 5, but this may be an example in which the margin M is such a numerical value.

  Next, FIG. 4 will be described. The apparatus 1 sets the opening degree of the high pressure EGR valve 80, for example, by the process of FIG. In the process of FIG. 4, first, in S200, the ECU 9 selects a map indicating the relationship between the flow rate and the valve opening. An example of the map is shown in FIG.

  The map shown in FIG. 6 shows the characteristics between the opening degree of the high pressure EGR valve 80 and the flow rate (recirculation amount) of the high pressure EGR pipe 8 for each PM accumulation amount of the DPF 6 (specifically FIG. 6). Shows the cases where the PM deposition amount is 10 g, 20 g, 30 g, and 40 g). Even when the same high-pressure EGR flow rate is achieved, for example, when the PM accumulation amount is 20 g and 30 g, the high-pressure EGR valve opening has a deviation indicated by an arrow. The map in FIG. 6 differs depending on the operating conditions (engine speed and engine load) of the engine 2. In S200, the above characteristic in the PM accumulation amount (and operation conditions) at that time is selected from FIG. The map in FIG. 6 may be obtained in advance and stored in the memory 90, for example.

  Next, in S210, the ECU 9 calculates a target opening. That is, the high pressure EGR valve opening at the target value of the high pressure EGR recirculation amount obtained in S140 is obtained for the characteristic selected in S200.

  When the high-pressure EGR valve opening is thus obtained, the ECU 9 may instruct the high-pressure EGR valve 80 so that, for example, the opening of the high-pressure EGR valve 80 becomes the obtained opening.

  Alternatively, after the command, feedback control may be performed so that the actual value of the high-pressure EGR recirculation amount converges to the target value set in S140. Specifically, for example, an estimated value of the high-pressure EGR recirculation amount is calculated (the method will be described later), and a difference between it and the target value of the high-pressure EGR recirculation amount obtained in S140 is calculated, and the difference value is input. An opening command value to the high pressure EGR valve is calculated by a feedback controller (designed in advance).

  When performing such feedback control, the high pressure EGR opening command obtained in S200 is the feed forward amount of the high pressure EGR valve opening (the input to the high pressure EGR valve 80 is the sum of the feed forward amount and the feedback amount). Becomes). The above feedback control and feedforward control may be programmed and stored in the memory 90, and the ECU 9 may automatically execute them.

An example of a method for estimating the high-pressure EGR reflux amount is as follows. First, the amount of air taken into the cylinder of the engine 2 is calculated. In this calculation, a well-known gas equation of state may be applied to the intake manifold. Thereby, the amount of air sucked into the cylinder is calculated by the following equation (e1).
Mcld = {η * Pim * Vcld} / {R * Tim} (e1)

  In equation (e1), Pim and Tim are the pressure value and temperature value (converted to absolute temperature) in the intake manifold detected by the pressure sensor 34 and the temperature sensor 33, Vcld is the cylinder volume of the engine 2, and R is the gas constant. It is. η is a numerical value reflecting the mass (molar mass) of gas sucked into the cylinder of the engine 2 and the intake efficiency of the cylinder, and may be set to an appropriate value (the intake efficiency of the cylinder is determined by the engine). It may be obtained from a two-dimensional map of rotation speed and Pim). Note that * indicates multiplication and / indicates division.

  Next, the total EGR reflux amount is calculated. The total EGR reflux amount is the sum of the high pressure EGR reflux amount and the low pressure EGR reflux amount. As is apparent from FIG. 1, the sum of the total EGR recirculation amount and the detected value of the air flow meter 31 is equal to the amount of air sucked into the cylinder. Therefore, the total EGR recirculation amount is calculated by subtracting the detected value of the air flow meter 31 from the air amount taken into the cylinder obtained above.

In addition, the high-pressure EGR reflux amount (estimated value) is calculated. In this calculation, the well-known Bernoulli theorem is applied to the high-pressure EGR pipe 8. Thereby, for example, as described in Japanese Patent Application Laid-Open No. 2010-84519, the high pressure EGR reflux amount is calculated by the following equation (e2).
Mhp = {(Pex−Pim) * 2 * g / γ} ^ (1/2) (e2)

  In the equation (e2), Pex is a pressure value in the exhaust manifold detected by the pressure sensor 40, Pim is a pressure value in the intake manifold detected by the pressure sensor 34, g is a gravitational acceleration, γ is a specific gravity of the recirculated gas, ^ (1/2) is the square root.

  Then, the low pressure EGR recirculation amount (estimated value) is calculated. As described above, the sum of the high pressure EGR reflux amount and the low pressure EGR reflux amount is the total EGR reflux amount. Therefore, the low pressure EGR reflux amount (estimated value) is calculated by subtracting the high pressure EGR reflux amount obtained above from the total EGR reflux amount obtained above. The above is an example of a method for estimating the high pressure EGR recirculation amount and the low pressure EGR recirculation amount.

  As described above, the setting of the high-pressure EGR valve opening degree or the feedback control of the high-pressure EGR flow rate has been described with reference to FIG. 4. Similarly, for the low-pressure EGR, for example, the feedback control of the low-pressure EGR flow rate may be performed. That is, for example, a difference between the estimated value of the low-pressure EGR flow rate described above and the target value of the low-pressure EGR flow rate obtained in S150 and S170 is calculated, and the feedback controller (designed in advance) using the difference value as an input. ) To calculate the opening command value to the low pressure EGR valve.

  As described above, the estimation means for estimating the exhaust gas recirculation amount in the high pressure recirculation passage, and the target exhaust gas in the high pressure recirculation passage set by the setting means by feeding back the exhaust gas recirculation amount in the high pressure recirculation passage estimated by the estimation means. And a feedback controller that controls the amount of recirculation so as to approach the recirculation amount. Further, an estimation means for estimating the exhaust gas recirculation amount in the low pressure recirculation passage, and a target exhaust gas recirculation amount in the low pressure recirculation passage set by the setting means by feeding back the exhaust gas recirculation amount in the low pressure recirculation passage estimated by the estimation means And a feedback controller that performs control so as to approach the distance.

  The above embodiments may be appropriately changed within the scope of the gist of the claims. For example, in the above, the high pressure EGR flow rate is a numerical value obtained by subtracting the margin from the physically possible maximum flow rate, but the present invention is not limited to this, and the high pressure EGR flow rate is the exhaust gas recirculation amount that can be physically secured. Any numerical value in the range not exceeding may be used, and the low pressure EGR flow rate may be set according to the high pressure EGR flow rate. In the above description, the predetermined amount P0 is the amount of PM deposited when the conforming value is obtained. However, the present invention is not limited to this, and any numerical value may be used. For example, it may be appropriately obtained by trial and error.

1 control device 2 engine (internal combustion engine)
3 Intake pipe (intake passage)
4 Exhaust pipe (exhaust passage)
7 Low pressure EGR pipe (low pressure reflux passage)
8 High pressure EGR pipe (High pressure reflux passage)
9 ECU

Claims (4)

A high-pressure recirculation passage for recirculating exhaust gas from the upstream of the turbocharger turbine in the exhaust passage of the internal combustion engine to the downstream of the compressor of the supercharger in the intake passage of the internal combustion engine;
A low pressure recirculation passage for recirculating exhaust gas from downstream of the turbine in the exhaust passage to upstream of the compressor in the intake passage;
A collector provided in the exhaust passage to collect particulate matter in the exhaust;
Storage means for storing an exhaust gas recirculation amount physically securable in the high-pressure recirculation passage according to the amount of particulate matter deposited in the collector;
If the exhaust gas recirculation amount of the high-pressure return passage is said amount deposited is not less than the reference accumulation amount is the deposition amount of the particulate matter in the collector when a value adapted to the optimal control of the internal combustion engine, A target exhaust gas recirculation amount in the high pressure recirculation passage is set in a range not exceeding the physically reservable exhaust gas recirculation amount stored in the storage unit according to the accumulation amount, and the target exhaust gas recirculation amount in the high pressure recirculation passage is set. Setting means for setting a target exhaust gas recirculation amount in the low pressure recirculation passage according to the setting of
Equipped with a,
The physically recyclable exhaust gas recirculation amount stored in the storage means is stored so as to have a property that the smaller the accumulation amount, the smaller the physically recirculated exhaust gas recirculation amount,
The setting means sets the target exhaust gas recirculation amount in the high-pressure recirculation passage to be a smaller amount as the accumulation amount is smaller when the accumulation amount is smaller than the reference accumulation amount, and the accumulation amount is larger. The exhaust gas purification apparatus for an internal combustion engine is characterized in that the target exhaust gas recirculation amount in the high pressure recirculation passage is set to be a large amount . When the accumulation amount is smaller than the reference accumulation amount , the setting means adapts the target exhaust gas recirculation amount in the high pressure recirculation passage to the optimum control of the exhaust recirculation amount in the high pressure recirculation passage as the accumulation amount decreases. The exhaust emission control device for an internal combustion engine according to claim 1 , wherein the exhaust gas purification device is set so as to decrease from the measured value. When the accumulation amount is smaller than the reference accumulation amount , the setting means determines that the sum of the target exhaust gas recirculation amount in the high pressure recirculation passage and the low pressure recirculation passage is exhaust gas in the high pressure recirculation passage and the low pressure recirculation passage. The exhaust purification device for an internal combustion engine according to claim 2 , wherein a target exhaust gas recirculation amount is set in the high pressure recirculation passage and the low pressure recirculation passage so as to be a sum of values suitable for the optimum control of the recirculation amount. The setting means sets the target exhaust gas recirculation amount in the high pressure recirculation passage and the low pressure recirculation passage when the accumulation amount is larger than the reference accumulation amount, respectively. The exhaust gas purification apparatus for an internal combustion engine according to any one of claims 1 to 3 , wherein the exhaust gas purification apparatus is set to a value suitable for the optimal control .

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