JP2012012968A - Engine control program and device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve target value following performance by a proper aspect in intake control including a saturation element with respect to an engine having an exhaust gas recirculator and a variable nozzle turbo.SOLUTION: In this engine control method, from a control amount of a nozzle opening of the variable nozzle turbo and a control amount of a valve opening of the exhaust gas recirculator, a target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust gas recirculator, and a first saturation compensation amount for compensating the nozzle opening of the variable nozzle turbo with respect to the saturation of the valve opening of the exhaust gas recirculator and a second saturation compensation amount for compensating the valve opening of the exhaust gas recirculator with respect to the saturation of the nozzle opening of the variable nozzle turbo, a command value of the nozzle opening of the variable nozzle turbo and a command value of the valve opening of the exhaust gas recirculator are calculated, and an intake control system of the engine having the exhaust gas recirculator and the variable nozzle turbo is controlled.

Description

  The present technology relates to engine control technology.

  In recent engines (for example, diesel engines), new air flow (MAF: Mass Air Flow) and intake air pressure (MAP: Manifold Air Pressure) are optimally controlled by the intake control system to reduce emissions and improve fuel efficiency. Has been.

  In general, as shown in FIG. 1, the intake control system of a diesel engine includes an intake pressure control system and a fresh air amount control system, and the intake pressure and the fresh air amount are controlled independently of each other. The intake pressure control system controls the intake pressure by controlling the nozzle diameter of a variable nozzle turbo VNT (Variable Nozzle Turbo) in order to reduce soot (PM) in the exhaust. On the other hand, the new air quantity control system controls the valve opening of an exhaust gas recirculation (EGR) that recirculates exhaust gas into the cylinder to reduce nitrogen oxide (NOx) in the exhaust gas. I control my volume.

  FIG. 2 shows a block diagram of the control system when such an intake pressure control system and a new air quantity control system are controlled independently. As shown in FIG. 2, the intake control system includes two parts, an upper fresh air amount control system and a lower intake pressure control system. The new air quantity control system controls the new air quantity by adjusting the valve opening of the EGR. On the other hand, the intake pressure control system controls the intake pressure by adjusting the nozzle opening of the VNT. Specifically, the planner to which the operating conditions (setting of the fuel injection amount and the engine speed) are input outputs the corresponding new air amount target value, intake pressure target value, EGR target value, and VNT target value. . Then, the fresh air amount controller outputs a control value according to the difference between the new air amount target value and the fresh air amount measurement value. Then, the sum of the control value and the EGR target value is input to the engine as the EGR valve opening. On the other hand, the intake pressure controller outputs a control value according to the difference between the intake pressure target value and the intake pressure measurement value. Then, the sum of the control value and the VNT target value is input to the engine as the VNT nozzle opening.

  In such an intake control system, each of the new air amount control system and the intake pressure control system independently calculates the EGR valve opening and the VNT nozzle opening so as to eliminate the deviation from the target value, The engine is operating. However, in addition to the direct elements Gp11 and Gp22, there are interference elements Gp12 and Gp21 as engine characteristics, and a change in one control amount affects both measured values and subsequent control amounts. For this reason, it is difficult for the two independent control systems to make the new air amount and the intake pressure follow the target at the same time.

  Therefore, a cooperative control system having non-interacting filters 5001 and 5003 as shown in FIG. 3 has been proposed. The non-interacting filter 5001 has the effect of canceling the interference element Gp12 and the non-interacting filter 5003 cancels the interference element Gp21, respectively, and causes the fresh air amount and the intake pressure to simultaneously follow the target values.

  For example, the engine characteristic Gp is expressed as follows.

そして、ゲインＫ及び時定数Ｔpを図４に示すような値に設定してシミュレーションを行うものとする。このとき、図２のような吸気圧制御系の場合における新気量（ＭＡＦ）及び吸気圧（ＭＡＰ）の変化を図５Ａ及び図５Ｂに示す。図５Ａ及び５Ｂにおいては、ステップ型の目標値に対して直達項及び干渉項との和である応答値は、アンダーシュートやオーバーシュートを含み、追従性が良くないことが分かる。一方、図３のような吸気制御系の場合における新気量（ＭＡＦ）及び吸気圧（ＭＡＰ）の変化を図６Ａ及び６Ｂに示す。図６Ａ及び６Ｂにおいては、同様のステップ型の目標値に対して直達項及び干渉項との和である応答値は、図５Ａ及び５Ｂに比して追従性が良くなっていることが分かる。

The simulation is performed with the gain K and the time constant Tp set to values as shown in FIG. At this time, changes in the fresh air amount (MAF) and the intake pressure (MAP) in the case of the intake pressure control system as shown in FIG. 2 are shown in FIGS. 5A and 5B. In FIGS. 5A and 5B, it can be seen that the response value which is the sum of the direct term and the interference term with respect to the step type target value includes undershoot and overshoot, and the followability is not good. On the other hand, changes in the fresh air amount (MAF) and the intake pressure (MAP) in the case of the intake control system as shown in FIG. 3 are shown in FIGS. 6A and 6B. 6A and 6B, it can be seen that the response value which is the sum of the direct term and the interference term with respect to the similar step-type target value has better followability than that of FIGS. 5A and 5B.

  However, generally, the changeable range of the valve opening and the VNT nozzle opening of the EGR, which is the control amount of the intake control system, is limited to the fully closed and fully open ranges because of its structure. Such a characteristic is called a “saturation characteristic”. FIG. 7 shows a control system in which saturation characteristics exist in the intake pressure control system of FIG. The saturation characteristics 5011 and 5013 are present immediately before the engine because the command value input to the engine is limited. For example, when the nozzle opening degree of the VNT is saturated as shown by a thick line in FIG. 7, a portion passing through Gp21 and Gp22 becomes a fixed value, and as a result, both the fresh air amount and the intake pressure cannot follow the target value. There is a problem. This problem is not limited to the cooperative control system as shown in FIG. 7, and the same problem occurs in other cooperative control systems such as optimal control.

  When the VNT nozzle opening is saturated in the intake control system as shown in FIG. 7, the response characteristics and the like are as shown in FIGS. 8A to 8D. FIG. 8A shows the change over time of the control amount for the EGR valve after the output value from the non-interacting filter 5003 is subtracted from the control amount from the fresh air amount controller. Here, since the VNT nozzle opening is saturated, the control amount for the EGR valve becomes the same value even if it passes through the saturation element. FIG. 8B shows a time change of the control value for the VNT nozzle after the output value from the non-interacting filter 5001 is subtracted from the control amount from the intake pressure controller. However, the dotted line represents the control amount itself and changes greatly downward. However, since the VNT target value from the planner is “5”, when this VNT target value is added, if the control amount for the VNT nozzle becomes “−5” or less, it is saturated at “0” due to the saturation characteristic. . In FIG. 8B, the control amount that is effective in relation to the VNT target value “5” is indicated by a solid line.

  When the nozzle opening of the VNT is saturated in this way, as shown in FIG. 8C, the value of the interference term indicated by the alternate long and short dash line is fixed due to the saturation, and the response value of the new air amount is obtained. A sudden overshoot has occurred. On the other hand, as shown in FIG. 8D, the value of the direct term does not decrease so much with respect to the intake pressure, and the overshoot is reduced.

  On the other hand, when the valve opening of the EGR is saturated in the intake pressure control system as shown in FIG. 7, the response characteristics and the like are as shown in FIGS. 9A to 9D. FIG. 9A shows a time change of the control amount for the EGR valve after the output value from the non-interacting filter 5003 is subtracted from the control amount from the new air amount controller. However, the dotted line represents the control amount itself and changes greatly downward. However, since the EGR target value from the planner is “2”, when the EGR target value is added to this EGR target value, if the control amount for the EGR valve becomes “−2” or less, it is saturated at “0” due to the saturation characteristic. . In FIG. 9A, the control amount that is effective in relation to the EGR target value “2” is indicated by a solid line. On the other hand, FIG. 9B shows the change over time of the control amount for the VNT nozzle after the output value from the non-interacting filter 5001 is subtracted from the control value from the intake pressure controller. Here, since the valve opening degree of the EGR is saturated, the control amount for the VNT nozzle becomes the same value even if the saturation characteristic is passed.

  Thus, when the valve opening of the EGR is saturated, as shown in FIG. 9C, undershoot occurs in the value of the interference term represented by the alternate long and short dash line for the fresh air amount, and the overall response value also undershoots. Occurs and the target value cannot be reached. Further, as shown in FIG. 9D, since the interference term represented by the alternate long and short dash line does not rise for the intake pressure, the response value cannot reach the target value.

  Conventionally, a technique called “anti-windup” is generally used for such saturation characteristics. FIG. 10 shows an example of a control system in which antiwindup is introduced. As shown in FIG. 10, a configuration is adopted in which the difference between the values before and after the saturation element is input to an engine model (that is, the antiwindup compensator 5101) and the output is added to the sensor value. As a result, it is possible to predict the output of the intake pressure and the fresh air amount that are expected when there is essentially no saturation.

  11A to 11D show response characteristics and the like when the configuration in which the anti-windup compensator 5101 is introduced and the VNT nozzle opening is saturated. FIG. 11A shows the time change of the control amount for the EGR valve after the output value from the non-interacting filter 5003 is subtracted from the control amount from the new air amount controller. Here, since the VNT nozzle opening is saturated, the control amount for the EGR valve becomes the same value even if it passes through the saturation element. FIG. 11B shows the change over time of the control amount for the VNT nozzle after the output value from the non-interacting filter 5001 is subtracted from the control amount from the intake pressure controller. However, the dotted line represents the control amount itself and changes greatly downward. However, since the VNT target value from the planner is “5”, when this VNT target value is added, if the control amount for the VNT nozzle becomes “−5” or less, it is saturated at “0” due to the saturation characteristic. . In FIG. 11B, the control value that is effective in relation to the VNT target value “5” is indicated by a solid line.

  FIG. 11C represents the time variation of the fresh air amount. For the fresh air volume, the lower limit is set to the value of the interference term indicated by the alternate long and short dash line due to the influence of the saturation element, and as a result, overshoot occurs in the response value of the fresh air volume represented by the solid line. . FIG. 11D represents the time change of the intake pressure. Here, since there is a portion where the gain of the direct term represented by the thin dotted line is reduced, a relatively good result is obtained for the response value of the intake pressure represented by the solid line.

  12A to 12D show response characteristics and the like when the configuration in which the antiwindup compensator 5101 is introduced and the valve opening of the EGR is saturated. FIG. 12A shows a time change of the control amount for the EGR valve after the output value from the non-interacting filter 5003 is subtracted from the control amount from the new air amount controller. However, the dotted line represents the control amount itself, and there is a portion that changes greatly downward. However, since the EGR target value from the planner is “2”, when the EGR target value is added to this EGR target value, if the control amount for the EGR valve becomes “−2” or less, it is saturated at “0” due to the saturation characteristic. . In FIG. 12A, the control amount that is effective in relation to the EGR target value “2” is indicated by a solid line. On the other hand, FIG. 12B shows a time change of the control amount for the VNT nozzle after the output value from the non-interacting filter 5001 is subtracted from the control amount from the intake pressure controller. Here, since the valve opening degree of the EGR is saturated, the control amount for the VNT nozzle becomes the same value even if the saturation characteristic is passed.

  FIG. 12C represents the time variation of the fresh air amount. Here, since a large undershoot has occurred in the value of the interference term indicated by the alternate long and short dash line, an undershoot also occurs in the response value of the fresh air amount indicated by the solid line, and the target value is reached. Is not reached. FIG. 12D represents the time change of the intake pressure. Here, since the direct term represented by the dotted line does not rise, the response value of the intake pressure represented by the solid line does not reach the target value as a result.

  The original purpose of the anti-windup compensator 5101 is to reduce the windup phenomenon resulting from excessive increase in the integral value of the deviation due to the delay in target value tracking due to saturation of the control amount (ie, the windup due to saturation). Therefore, as shown in FIG. 12D, the wind-up phenomenon for the intake pressure corresponding to the nozzle opening of the saturated VNT is suppressed, but the fresh air volume corresponding to the valve opening of the non-saturated EGR is suppressed. It can be seen that there is no improvement effect with respect to, and there is no expected effect in the 2-input 2-output system.

  In addition, a method for preventing the saturation phenomenon itself has been proposed. This method multiplies the difference before and after the saturation element by multiplying the inverse characteristic of the filter characteristic installed in the latter stage of the integrator to estimate the input that causes saturation, and negatively feeds back to the filter entrance, thereby reducing the saturation phenomenon itself. I try not to get up. In this method, the saturation phenomenon itself is certainly eliminated, but as a result, there is no change in the situation in which the tracking of the target value is delayed and the integrated value of the deviation is excessively increased, and there is no improvement effect on the non-saturation side.

  In any of the conventional methods described above, the difference before and after the saturation element is negatively fed back (FIG. 10 is positively fed back to the sensor value. However, since the sensor value is fed back negatively to the target value, it is actually negative feedback. ) To prevent an increase in control input due to saturation. However, it has been found that a 2-input 2-output cooperative control system is not always effective.

JP 2009-24550 A JP 2008-248863 A

  Accordingly, an object of the present technology is to provide a novel technique for improving target value followability in an appropriate manner in intake control including a saturation element for an engine having an exhaust circulator and a variable nozzle turbo.

  An engine control method according to one aspect of the present technology includes (A) a set value of a fuel injection amount for an engine having an exhaust circulator and a variable nozzle turbo, a set value of an engine speed, a measured value of an intake pressure of the engine, and A step of obtaining a measured value of the fresh air amount; (B) a target value of the intake air pressure and a target value of the fresh air amount corresponding to the set value of the fuel injection amount and the set value of the engine speed; A step of obtaining a target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator corresponding to the setting value and the setting value of the engine speed, and (C) the target value of the intake pressure and the new value A control amount calculation step for calculating a control amount of the nozzle opening of the variable nozzle turbo and a control amount of the valve opening of the exhaust circulator from the target value of the air volume, the measured value of the intake pressure, and the measured value of the new air volume; (D) Variable nozzle turbo Control amount of the valve opening degree and control amount of the valve opening degree of the exhaust circulator, the target value of the nozzle opening of the variable nozzle turbo, the target value of the valve opening degree of the exhaust circulator, and the valve opening degree of the exhaust circulator A first saturation compensation amount for compensating the nozzle opening of the variable nozzle turbo against saturation, and a second for compensating the valve opening of the exhaust circulator against saturation of the nozzle opening of the variable nozzle turbo. And a command value calculating step for calculating a command value for the nozzle opening of the variable nozzle turbo and a command value for the valve opening of the exhaust circulator.

  In intake control including a saturation element for an engine having an exhaust circulator and a variable nozzle turbo, the target value followability can be improved in an appropriate manner.

FIG. 1 is a schematic diagram of an engine. FIG. 2 is a block diagram for explaining a conventional control system of the engine. FIG. 3 is a block diagram for explaining another conventional control system. FIG. 4 is a diagram illustrating a parameter setting example. FIG. 5A is a diagram showing a response characteristic of fresh air amount by a conventional control system. FIG. 5B is a diagram showing response characteristics of intake pressure by a conventional control system. FIG. 6A is a diagram showing a response characteristic of fresh air amount according to another conventional control system. FIG. 6B is a diagram showing response characteristics of intake pressure by another conventional control system. FIG. 7 is a block diagram showing a control system of an engine having saturation characteristics. FIG. 8A is a diagram showing a time change of the EGR control amount when the VNT nozzle opening is saturated in the control system of FIG. FIG. 8B is a diagram showing a change over time in the VNT control amount when the VNT nozzle opening is saturated in the control system of FIG. 7. FIG. 8C is a diagram illustrating a response characteristic of the fresh air amount when the VNT nozzle opening is saturated in the control system of FIG. 7. FIG. 8D is a diagram showing the response characteristic of the intake pressure when the VNT nozzle opening is saturated in the control system of FIG. FIG. 9A is a diagram showing a time change of the EGR control amount when the EGR valve opening degree is saturated in the control system of FIG. FIG. 9B is a diagram showing a change over time in the VNT control amount when the EGR valve opening is saturated in the control system of FIG. 7. FIG. 9C is a diagram showing a response characteristic of the fresh air amount when the EGR valve opening is saturated in the control system of FIG. FIG. 9D is a graph showing the response characteristic of the intake pressure when the EGR valve opening is saturated in the control system of FIG. FIG. 10 is a block diagram of an engine control system when anti-windup is introduced. FIG. 11A is a diagram showing a time change of the EGR control amount when the VNT nozzle opening is saturated in the control system of FIG. FIG. 11B is a diagram illustrating a change over time in the VNT control amount when the VNT nozzle opening is saturated in the control system of FIG. 10. FIG. 11C is a diagram showing a response characteristic of the fresh air amount when the VNT nozzle opening is saturated in the control system of FIG. FIG. 11D is a diagram showing the response characteristic of the intake pressure when the VNT nozzle opening is saturated in the control system of FIG. FIG. 12A is a diagram showing a time change of the EGR control amount when the EGR valve opening degree is saturated in the control system of FIG. FIG. 12B is a diagram showing a time change of the VNT control amount when the EGR valve opening is saturated in the control system of FIG. FIG. 12C is a diagram showing a response characteristic of the fresh air amount when the EGR valve opening is saturated in the control system of FIG. FIG. 12D is a diagram showing a response characteristic of the intake pressure when the EGR valve opening degree is saturated in the control system of FIG. FIG. 13 is a diagram illustrating an engine and an engine control device according to the embodiment of the present technology. FIG. 14 is a block diagram of the engine control apparatus according to the first embodiment. FIG. 15A is a diagram showing a time change of the EGR control amount when the VNT nozzle opening is saturated in the control system of FIG. FIG. 15B is a diagram illustrating a change over time in the VNT control amount when the VNT nozzle opening is saturated in the control system of FIG. 14. FIG. 15C is a diagram showing a response characteristic of the fresh air amount when the VNT nozzle opening is saturated in the control system of FIG. FIG. 15D is a diagram showing an intake pressure response characteristic when the VNT nozzle opening is saturated in the control system of FIG. 14. FIG. 16A is a diagram showing a time change of the EGR control amount when the EGR valve opening degree is saturated in the control system of FIG. FIG. 16B is a diagram showing a time change of the VNT control amount when the EGR valve opening degree is saturated in the control system of FIG. FIG. 16C is a diagram showing a response characteristic of the fresh air amount when the EGR valve opening is saturated in the control system of FIG. FIG. 16D is a diagram showing the response characteristic of the intake pressure when the EGR valve opening degree is saturated in the control system of FIG. 14. FIG. 17 is a functional block diagram of the engine control apparatus according to the first embodiment. FIG. 18 is a diagram illustrating a processing flow of the engine control apparatus according to the first embodiment. FIG. 19 is a block diagram of an engine control apparatus according to the second embodiment. FIG. 20A is a diagram illustrating a time change of the EGR control amount when the VNT nozzle opening is saturated in the control system of FIG. FIG. 20B is a diagram illustrating a time change of the VNT control amount when the VNT nozzle opening degree is saturated in the control system of FIG. 19. FIG. 20C is a diagram showing a response characteristic of the fresh air amount when the VNT nozzle opening is saturated in the control system of FIG. FIG. 20D is a diagram showing the response characteristic of the intake pressure when the VNT nozzle opening is saturated in the control system of FIG. FIG. 21A is a diagram showing a time change of the EGR control amount when the EGR valve opening degree is saturated in the control system of FIG. FIG. 21B is a diagram illustrating a change over time in the VNT control amount when the EGR valve opening degree is saturated in the control system of FIG. 19. FIG. 21C is a diagram showing a response characteristic of the fresh air amount when the EGR valve opening degree is saturated in the control system of FIG. FIG. 21D is a diagram showing the response characteristic of the intake pressure when the EGR valve opening is saturated in the control system of FIG. FIG. 22 is a block diagram of an engine control apparatus according to the third embodiment. FIG. 23A is a diagram showing a time change of the EGR control amount when the VNT nozzle opening is saturated in the control system of FIG. FIG. 23B is a diagram showing a change over time in the VNT control amount when the VNT nozzle opening is saturated in the control system of FIG. 22. FIG. 23C is a diagram showing a response characteristic of the fresh air amount when the VNT nozzle opening is saturated in the control system of FIG. FIG. 23D is a diagram showing an intake pressure response characteristic when the VNT nozzle opening is saturated in the control system of FIG. 22. FIG. 24A is a diagram showing a time change of the EGR control amount when the EGR valve opening degree is saturated in the control system of FIG. FIG. 24B is a diagram showing a time change of the VNT control amount when the EGR valve opening degree is saturated in the control system of FIG. FIG. 24C is a diagram showing a response characteristic of the fresh air amount when the EGR valve opening degree is saturated in the control system of FIG. FIG. 24D is a diagram showing the response characteristic of the intake pressure when the EGR valve opening degree is saturated in the control system of FIG. FIG. 25 is a block diagram of an engine control apparatus according to the fourth embodiment. FIG. 26A is a diagram showing a time change of the EGR control amount when the VNT nozzle opening is saturated in the control system of FIG. FIG. 26B is a diagram illustrating a change over time in the VNT control amount when the VNT nozzle opening is saturated in the control system of FIG. 25. FIG. 26C is a diagram illustrating a response characteristic of the fresh air amount when the VNT nozzle opening is saturated in the control system of FIG. FIG. 26D is a diagram showing a response characteristic of the intake pressure when the VNT nozzle opening is saturated in the control system of FIG. FIG. 27 is a functional block diagram of an engine control apparatus according to the fourth embodiment. FIG. 28 is a diagram illustrating a processing flow of the engine control apparatus according to the fourth embodiment. FIG. 29 is a block diagram of an engine control apparatus according to the fifth embodiment. FIG. 30 is a block diagram of an engine control apparatus according to the sixth embodiment. FIG. 31 is a block diagram when the engine control apparatus is implemented by a computer. FIG. 32 is a functional block diagram of the engine control apparatus.

[Embodiment 1]
FIG. 13 shows a diesel engine as an example of an engine according to an embodiment of the present technology. The engine body 1 includes an exhaust circulator EGR that supplies exhaust gas from the engine body 1, and a variable nozzle turbo VNT that compresses fresh air by rotating the turbine with the pressure of the exhaust gas and supplies the compressed air to the engine body 1. And are connected. By adjusting the nozzle opening of the variable nozzle turbo VNT, the rotation of the turbine of the variable nozzle turbo VNT is adjusted, and the intake pressure (MAP) measured by the intake pressure (MAP) sensor is adjusted. On the other hand, the fresh air amount (MAF) measured by the fresh air amount (MAF) sensor is adjusted by adjusting the valve opening degree of the EGR valve provided in the exhaust gas circulator EGR.

  In the engine control apparatus 1000 according to the present embodiment, an intake pressure measurement value from the MAP sensor, a fresh air amount measurement value from the MAF sensor, a set value of the fuel injection amount given from the outside, and the same are given from the outside. And the set value of the engine speed to be input. Further, the engine controller 1000 outputs the valve opening of the EGR valve to the EGR valve, and the nozzle opening of the VNT nozzle is output to the VNT nozzle.

  FIG. 14 shows a block diagram of engine control apparatus 1000 according to the present embodiment. That is, the fuel injection amount set value and the engine speed set value are input, and the EGR valve opening target value and the VNT nozzle opening target value are associated with the fuel injection amount value and the engine speed value. EGR valve opening corresponding to the set value of the fuel injection amount and the set value of the engine speed from the planner 11 in which the combination of the value, the target value of the fresh air amount MAF and the target value of the intake pressure MAP are registered , The target value of the VNT nozzle opening, the target value of the fresh air amount MAF, and the target value of the intake pressure MAP are read out. Then, the difference between the target value of the fresh air amount MAF and the measured value of the fresh air amount MAF is input to the fresh air amount controller 12, and the new air amount controller 12 responds to this input by a well-known method. A control amount for the EGR valve opening is generated and output. Further, the difference between the target value of the intake pressure MAP and the measured value of the intake pressure MAP is input to the intake pressure controller 16, and in response to this input, the intake pressure controller 16 performs the VNT nozzle opening degree by a well-known method. Generate and output the control amount.

  The control amount of the EGR valve opening is reduced by the output of the decoupling filter 15 (transfer function Gp21 / Gp11) with respect to the control amount of the VNT nozzle opening, and a feedback control amount of the EGR valve opening is generated. Further, the control amount of the VNT nozzle opening is reduced by the output of the decoupling filter 14 (transfer function Gp12 / Gp22) with respect to the control amount of the EGR valve opening, and a feedback control amount of the VNT nozzle opening is generated. The

  Further, the feedback control amount of the EGR valve opening is a first saturation that generates a target value of the EGR valve opening and a first saturation compensation amount for compensating the EGR valve opening with respect to the saturation of the VNT nozzle opening. The value is added to the first saturation compensation amount that is the output of the compensator 19 (Gp21 / Gp11), and a command value for the EGR valve opening is generated. Further, the feedback control amount of the VNT nozzle opening includes a target value of the VNT nozzle opening and a second saturation compensator 18 (transfer function Gp12 /) for compensating the VNT nozzle opening against the saturation of the EGR valve opening. A command value for the VNT nozzle opening is generated by adding the second saturation compensation amount that is the output of Gp22).

  The command value for the EGR valve opening is input to the saturation element 13 and is limited between a preset upper limit value and lower limit value, and a final command value for the EGR valve opening is generated. The EGR valve of the engine 1 is controlled. Similarly, the command value for the VNT nozzle opening is input to the saturation element 17 and is limited between a preset upper limit value and lower limit value to generate a final command value for the VNT nozzle. This final command value Thus, the VNT nozzle of the engine 1 is controlled.

  The engine characteristics of the engine 1 are that a direct element Gp11 for outputting a fresh air amount MAF corresponding to the final command value of the EGR valve opening and an intake pressure MAP corresponding to the final command value of the EGR valve opening are output. Interference element Gp12, a direct delivery element Gp22 for outputting the intake pressure MAP corresponding to the final command value of the VNT nozzle opening, and a new air amount MAF corresponding to the final command value of the VNT nozzle opening The interference element Gp21 is assumed to be included. Therefore, when the sum of the output of the direct element Gp11 and the output of the interference element Gp21 is measured by the new air amount sensor, a measured value of the new air amount MAF is obtained. Further, when the sum of the output of the direct element Gp22 and the output of the interference element Gp12 is measured by the intake pressure sensor, a measured value of the intake pressure MAP is obtained.

  The first saturation compensator 19 is provided to compensate for the amount of components supplied to the fresh air amount side via the interference element Gp21 when the VNT nozzle opening is saturated. In order to compensate for the shortage when the VNT nozzle opening is saturated, the input / output difference of the saturation element 17 is used. Since the first saturation compensation amount is added before the saturation element 13, the direct element Gp11 acts excessively as it is. Therefore, in order to eliminate the effect, a transfer function of the form Gp21 / Gp11 is obtained.

  Further, the second saturation compensator 18 is provided to compensate for the amount of the component supplied to the intake pressure side via the interference element Gp12 when the EGR valve opening is saturated. In order to compensate for the shortage when the EGR nozzle opening is saturated, the input / output difference of the saturation element 13 is used. Since the second saturation compensation amount is added before the saturation element 17, the direct element Gp22 acts excessively as it is. Therefore, in order to eliminate the effect, a transfer function of the form Gp12 / Gp22 is obtained.

  When there are saturated elements in this way, the feedback function on the unsaturated side is multiplied by the transfer function obtained by dividing the interference element from the saturated side to the unsaturated side by the direct element on the unsaturated side to the difference before and after the saturated element. By adding to the quantity, the decrease in the action from the saturation side to the non-saturation side is compensated, and the target value followability of the response value on the non-saturation side is improved.

  15A to 15D show simulation results when the VNT nozzle opening is saturated. FIG. 15A represents the time change of the feedback control amount of the EGR valve opening. Since the EGR valve opening is not saturated, the feedback control amount of the EGR valve opening is effective as it is even after the saturation element 13. FIG. 15B represents the time change of the feedback control amount of the VNT nozzle opening. However, the dotted line represents the feedback control amount itself of the VNT nozzle opening, and changes greatly downward. However, since the VNT target value from the planner 11 is “5”, when added to this VNT target value, the feedback control amount of the VNT nozzle opening becomes “−5” or less, and “0” due to saturation characteristics. Saturates. In FIG. 15B, the feedback control amount that is effective in relation to the VNT target value “5” is indicated by a solid line.

  When the nozzle opening degree of the VNT is saturated in this way, as shown in FIG. 15C, overshoot is eliminated in the output from the direct element Gp11 (represented as a direct term) for the fresh air amount MAF as indicated by a thin dotted line. For this reason, the response value represented by the solid line has improved followability to the target value represented by the long dotted line. On the other hand, as shown in FIG. 15D showing the time change of the intake pressure MAP, a small overshoot has occurred in the response value of the intake pressure MAP represented by a solid line.

  16A to 16D show simulation results when the EGR valve opening is saturated. FIG. 16A shows the time change of the feedback control amount of the EGR valve opening. However, the dotted line represents the feedback control amount itself of the EGR valve opening and changes greatly downward. However, since the EGR target value from the planner 11 is “2”, when added to this EGR target value, the feedback control amount of the EGR valve opening becomes “−2” or less, and “0” due to saturation characteristics. Saturates. In FIG. 16A, the feedback control amount that is effective in relation to the EGR target value “2” is indicated by a solid line. On the other hand, FIG. 16B represents the time change of the feedback control amount of the VNT nozzle opening. Since the VNT nozzle opening is not saturated, the feedback control amount of the EGR valve opening is effective as it is even after the saturation element 13.

  As described above, when the valve opening of the EGR is saturated, as shown in FIG. 16C, for the fresh air amount MAF, an undershoot occurs in the output from the interference element Gp12 represented by the one-dot chain line, and the fresh air represented by the solid line. Undershoot also occurs in the response value of the amount MAF. On the other hand, as shown in FIG. 16D, with respect to the intake pressure MAP, the output from the direct element Gp22 represented by the thin dotted line is appropriately increased, and the response value represented by the solid line appropriately follows the target value represented by the long dotted line. is doing.

  Thus, it can be seen that the target value followability on the non-saturated side is improved.

  FIG. 17 shows a functional block diagram of the engine control apparatus 1000 for realizing the functions of such a block diagram.

  The engine control apparatus 1000 includes (A) a fuel injection amount detection unit 101 that acquires a set value of the fuel injection amount Q, (B) an engine speed detection unit 102 that acquires a set value of the engine speed RPM, and (C ) A sensor value acquisition unit 103 that acquires a combination X (= [MAF, MAP]) of a measured value of the intake pressure and a measured value of the fresh air amount from the intake pressure sensor 2 and the fresh air amount sensor 3, and (D) fuel injection Uref = [target value of EGR valve opening, target value of VNT nozzle opening]) and Xref (= [target value of MAF, target value of MAP] in association with the combination of the value of quantity and the value of engine speed ) Is registered, (E) the set value of the fuel injection amount Q output from the fuel injection amount detection unit 101, and the set value of the engine speed RPM output from the engine speed detection unit 102 And The target value generation unit 105 that reads out the corresponding Uref and Xref from the target value table 104, and (F) the new air amount and intake pressure measurement value X from the sensor value acquisition unit 103 and the new value from the target value generation unit 105. EGR valve opening and VNT nozzle opening feedback control amount Ufb (= [EGR valve opening feedback control amount, VNT nozzle opening feedback control amount]) is generated from the air volume and intake pressure target value Xref. Feedback control amount generation unit 107, (G) feedback control amount Ufb, target value Uref, and saturation compensation amount Ucomp described below (= [EGR valve opening saturation compensation amount, VNT valve opening saturation compensation amount]) And a command value generation unit 108 for generating a command value U = ([command value for EGR valve opening, command value for VNT nozzle opening]), and (H) a finger exceeding a predetermined upper limit value. The command value is set to the upper limit value, and the process of setting the command value below the predetermined lower limit value to the lower limit value is performed, and the final command value Usat (= [final command value of EGR valve opening, final value of VNT nozzle opening Command value]) and (I) a saturation compensation amount calculation unit 110 that generates a saturation compensation amount Ucomp from the command value U and the final command value Usat.

  Note that the EGR valve opening and the VNT nozzle opening of the engine 1 are controlled according to the output of the saturation processing unit 109.

  The operation of the engine control apparatus 1000 shown in FIG. 17 will be described with reference to FIG. . First, at the start of operation, the time is set to t = 1 (FIG. 18: step S1). The fuel injection amount detection unit 101, the engine speed detection unit 102, and the sensor value acquisition unit 103 then set the fuel injection amount set value Q [t], the engine speed set value RPM [t], and the sensor value X [t. ] Is acquired (step S3).

  Then, the target value generation unit 105 obtains the target values Xref [t] and Uref [t] corresponding to the fuel injection amount setting value Q [t] and the engine speed setting value RPM [t] as the target value table 104. It generates by reading from (step S5). Further, the feedback control amount generation unit 107 uses the feedback control amount Ufb [t] from the target value Xref [t] generated by the target value generation unit 105 and the sensor value X [t] acquired by the sensor value acquisition unit 103. (= F (X [t], Xref [t])) is generated (step S7). The feedback amount Ufb [t] is basically generated in the same manner as in the conventional case. Specifically, the control amount of the EGR valve opening obtained by inputting the difference between the target value of the fresh air amount MAF and the sensor value of the fresh air amount MAF to the fresh air amount controller 12, and the non-interacting filter 15 The difference from the output result is the feedback control amount of the EGR valve opening. Further, the difference between the control amount of the VNT nozzle opening obtained by inputting the difference between the target value of the intake pressure MAP and the sensor value of the intake pressure MAP to the intake pressure controller 16 and the output result of the non-interacting filter 14. Is the feedback control amount of the VNT nozzle opening.

  Then, the command value generation unit 108 outputs the output Uref [t] of the target value generation unit 105, the output Ufb [t] of the feedback control amount generation unit 107, and the saturation compensation amount Ucomp [t-1] one unit time ago. And the command value U [t] is calculated (step S9). That is, U [t] = Ufb [t] + Uref [t] + Ucomp [t−1] is calculated. As described above, U [t] is a combination of the valve opening of the EGR valve provided in the exhaust gas circulator EGR and the nozzle opening of the variable nozzle turbo VNT (= [EGR valve opening command Value, VNT nozzle opening command value]). Ucomp [t-1] will be described below.

  Thereafter, the saturation processing unit 109 performs saturation processing (Usat [t] = saturation (U [t])) (step S11). As described above, the saturation processing outputs the upper limit value as the final command value if the command value is equal to or greater than the predetermined upper limit value, and outputs the lower limit value as the final command value if the command value is less than or equal to the predetermined lower limit value. However, the command values of other values are output as they are. Such a process is performed for both the EGR valve opening and the VNT nozzle opening. Then, the saturation processing unit 109 outputs the final command value to the engine 1 (step S13).

  Further, the saturation compensation amount calculation unit 110 calculates the saturation compensation amount Ucomp [t] using the command value U [t] from the command value generation unit 108 and the final command value Usat [t] from the saturation processing unit 109. (Step S15). The saturation compensation amount Ucomp [t] (= [EGRcomp [t], VNTcomp [t]) is used at the next time t + 1.

  The first saturation compensator 19 shown in FIG. 14 is represented by a transfer function Gp21 / Gp11, and the second saturation compensator 18 is represented by a transfer function Gp12 / Gp22. Gp21 represents the degree to which the final command value of the VNT nozzle opening (that is, the command value effective for the engine 1) acts on the fresh air amount MAF, but this actually includes a delay component. Gp12 represents the degree to which the final command value of the EGR valve opening (that is, the command value effective for the engine 1) acts on the intake pressure MAP, but this actually includes a delay component. . Further, Gp11 represents the degree to which the final command value of the EGR valve opening degree acts on the fresh air amount MAF, but this also actually includes a delay component. Similarly, Gp22 represents the degree to which the final command value of the VNT nozzle opening acts on the intake pressure MAP, but this also actually includes a delay component.

Therefore, EGRcomp [t] and VNTcomp [t] are expressed as follows.
VNTcomp [t] = D12 / C12 × EGRcomp [t-1]
+ A22 / C12 × (EGR [t] −EGRsat [t])
-B22 / C12 × (EGR [t-1] -EGRsat [t-1])
EGRcomp [t] = D21 / C21 × VNTcomp [t-1]
+ A11 / C21 × (VNT [t] −VNTsat [t])
-B11 / C21 x (VNT [t-1] -VNTsat [t-1])

  Here, C12 and D12 are coefficients related to the interference element Gp12, and A22 and B22 are coefficients related to the direct element Gp22. These coefficients are set according to the actual characteristics of the engine 1. Similarly, C21 and D21 are coefficients related to the interference element Gp21, and A11 and B11 are coefficients related to the direct element Gp11. These coefficients are also set in accordance with the actual characteristics of the engine 1.

  As shown above, the second saturation compensation amount VNTcomp [t] is the difference between the first term representing the effect one unit time ago and the current command value EGR [t] and the final command value EGR [t]. Is the sum of the second term representing the influence of the second term and the third term representing the influence of the difference between the command value EGR [t-1] one unit time ago and the final command value EGR [t-1]. The first saturation compensation amount EGRcomp [t] is a first term representing the influence of one unit time ago and the first saturation representing the influence of the difference between the current command value VNT [t] and the final command value VNT [t]. This is the sum of the second term and the third term representing the effect of the difference between the command value VNT [t-1] one unit time ago and the final command value VNT [t-1]. The data one unit time before is stored in a memory or the like and is read and used. Further, the current value is stored in a memory or the like, and is read out and used after one unit time.

  After step S15, t is incremented by 1 (step S17), and the process returns to step S3. The process is repeated until the engine is stopped.

  By doing in this way, the block diagram shown in FIG. 14 is implement | achieved and the target value followable | trackability on a non-saturation side can be improved.

[Embodiment 2]
In the first embodiment, the target value followability on the non-saturation side is improved. However, in the actual intake control system of the engine 1, there is a case where it is desired to give priority to the new air amount MAF. In such a case, an engine control apparatus 1000 represented by a block diagram as shown in FIG. 19 is introduced.

  The difference from the block diagram in the first embodiment shown in FIG. 14 is that a third saturation compensator 20 (transfer function Gp11 / Gp21) is introduced in place of the second saturation compensator 18.

  Also in the present embodiment, the first saturation compensator 19 has a component to be supplied to the fresh air amount side via the interference element Gp21 when the VNT nozzle opening is saturated. Is provided. In order to compensate for the shortage when the VNT nozzle opening is saturated, the input / output difference of the saturation element 17 is used. Since the first saturation compensation amount is added before the saturation element 13, the direct element Gp11 acts excessively as it is, so that a transfer function in the form of Gp21 / Gp11 is used to eliminate the action. It becomes.

  Further, in the present embodiment, unlike the first embodiment, the third saturation compensator 20 has a component supplied to the fresh air amount side via the direct element Gp11 when the EGR valve opening degree is saturated. Since there is a shortage, it is provided to compensate for that. That is, the input / output difference of the saturation element 13 is used to compensate for the shortage when the EGR nozzle opening is saturated. Since the third saturation compensation amount is added before the saturation element 17, the interference element Gp21 acts excessively as it is, so that the transfer function in the form of Gp11 / Gp21 is used to eliminate the action. It becomes.

  In this way, the difference before and after the saturation element on the EGR side is multiplied by the transfer function obtained by dividing the direct element on the saturation side by the interference element from the saturation side to the saturation side, and the feedback control amount on the saturation side By adding to the above, the decrease on the direct delivery side of EGR is compensated for and the target value followability of the fresh air amount is improved.

  20A to 20D show simulation results and the like when the VNT nozzle opening is saturated. FIG. 20A represents the time change of the feedback control amount of the EGR valve opening. Since the EGR valve opening is not saturated, the feedback control amount of the EGR valve opening is effective as it is even after the saturation element 13. FIG. 20B represents the time change of the feedback control amount of the VNT nozzle opening. However, the dotted line represents the feedback control amount itself of the VNT nozzle opening, and changes greatly downward. However, since the VNT target value from the planner 11 is “5”, when added to this VNT target value, the feedback control amount of the VNT nozzle opening becomes “−5” or less, and “0” due to saturation characteristics. Saturates. In FIG. 15B, the feedback control amount that is effective in relation to the VNT target value “5” is indicated by a solid line.

  When the nozzle opening degree of the VNT is saturated in this way, as shown in FIG. 20C, overshoot is eliminated in the output (expressed as a direct term) from the direct element Gp11 represented by a thin dotted line for the fresh air amount MAF. For this reason, the response value represented by the solid line has improved followability with respect to the target value represented by the long dotted line as compared with the prior art. On the other hand, as shown in FIG. 20D, a small overshoot has occurred in the response value of the intake pressure MAP represented by the solid line. Since the first saturation compensator 19 is the same as that of the first embodiment, similar characteristics are obtained.

  On the other hand, FIGS. 21A to 21D show simulation results when the EGR valve opening is saturated. FIG. 21A represents the time change of the feedback control amount of the EGR valve opening. However, the dotted line represents the feedback control amount itself of the EGR valve opening and changes greatly downward. However, since the EGR target value from the planner 11 is “2”, when added to this EGR target value, the feedback control amount of the EGR valve opening becomes “−2” or less, and “0” due to saturation characteristics. Saturates. In FIG. 21A, the feedback control amount that is effective in relation to the EGR target value “2” is indicated by a solid line. On the other hand, FIG. 21B represents the time change of the feedback control amount of the VNT nozzle opening. Since the VNT nozzle opening is not saturated, the feedback control amount of the EGR valve opening is effective as it is even after the saturation element 13.

  In this way, when the valve opening of the EGR is saturated, as shown in FIG. 21C, the fresh air amount MAF is appropriately adjusted because there is no undershoot in the output from the interference element Gp12 represented by the alternate long and short dash line, The response value of the fresh air amount MAF represented by the solid line appropriately follows the target value represented by the thin dotted line. On the other hand, as shown in FIG. 21D, for the intake pressure MAP, the output from the direct element Gp22 represented by the thin dotted line is reduced, and the response value represented by the solid line is away from the target value represented by the long dotted line. .

  Thus, it can be seen that the target value followability of the fresh air amount is improved.

  A functional block diagram of the engine control apparatus 1000 for realizing the functions of such a block diagram is represented in FIG. 17 which is the same as the functional block diagram of the first embodiment. However, the processing contents of the saturation compensation amount calculation unit 110 are different. Similarly, the processing flow itself is the same as that shown in FIG. 18, but the calculation contents in step S15 are different.

Specifically, EGRcomp [t] and VNTcomp [t] are expressed as follows.
VNTcomp [t] = D11 / C11 × EGRcomp [t-1]
+ A21 / C11 × (EGR [t] −EGRsat [t])
-B21 / C11 × (EGR [t-1] -EGRsat [t-1])
EGRcomp [t] = D21 / C21 × VNTcomp [t-1]
+ A11 / C21 × (VNT [t] −VNTsat [t])
-B11 / C21 x (VNT [t-1] -VNTsat [t-1])

  As described above, A21, B21, C21, and D21 are coefficients related to the interference element Gp21, and A11, B11, C11, and D11 are coefficients related to the direct element Gp11. These coefficients are also set in accordance with the actual characteristics of the engine 1.

  As shown above, the second saturation compensation amount VNTcomp [t] is the difference between the first term representing the effect one unit time ago and the current command value EGR [t] and the final command value EGR [t]. Is the sum of the second term representing the influence of the second term and the third term representing the influence of the difference between the command value EGR [t-1] one unit time ago and the final command value EGR [t-1]. The first saturation compensation amount EGRcomp [t] is a first term representing the influence of one unit time ago and the first saturation representing the influence of the difference between the current command value VNT [t] and the final command value VNT [t]. This is the sum of the second term and the third term representing the effect of the difference between the command value VNT [t-1] one unit time ago and the final command value VNT [t-1]. The data one unit time before is stored in a memory or the like and is read and used. Further, the current value is stored in a memory or the like, and is read out and used after one unit time.

  By doing in this way, the block diagram shown in FIG. 19 is implement | achieved and the target value followability of fresh air quantity can be improved.

[Embodiment 3]
In the second embodiment, the target value followability of the new air amount is improved. However, in the actual intake control system of the engine 1, there is a case where it is desired to give priority to the intake pressure MAP. In such a case, an engine control device 1000 represented by a block diagram as shown in FIG. 22 is introduced.

  The difference from the block diagram in the first embodiment shown in FIG. 14 is that a fourth saturation compensator 21 (transfer function Gp22 / Gp12) is introduced instead of the first saturation compensator 19.

  In the present embodiment, unlike the first embodiment, the fourth saturation compensator 21 lacks the component supplied to the intake pressure side via the direct element Gp22 when the VNT nozzle opening is saturated. It is provided to compensate for that. In order to compensate for the shortage when the VNT nozzle opening is saturated, the input / output difference of the saturation element 17 is used. Since the fourth saturation compensation amount is added before the saturation element 13, the interference element Gp12 acts excessively as it is, so that a transfer function in the form of Gp22 / Gp12 is used to eliminate the action. It becomes.

  Further, the second saturation compensator 18 is provided to compensate for the amount of the component supplied to the intake pressure side via the interference element Gp12 when the EGR valve opening is saturated. In order to compensate for the shortage when the EGR nozzle opening is saturated, the input / output difference of the saturation element 13 is used. Since the second saturation compensation amount is added before the saturation element 17, the direct element Gp22 acts excessively as it is, so that the transfer function in the form of Gp12 / Gp22 is removed in order to eliminate this effect. It becomes.

  In this way, the difference before and after the saturation element on the VNT side is multiplied by the transfer function obtained by dividing the direct element on the saturation side by the interference element from the saturation side to the saturation side, and the feedback control amount on the saturation side By adding to the above, the decrease in the directly achieved VNT is compensated for and the target value followability of the intake pressure is improved.

  23A to 23D show simulation results when the VNT nozzle opening is saturated. FIG. 23A represents the time change of the feedback control amount of the EGR valve opening. Since the EGR valve opening is not saturated, the feedback control amount of the EGR valve opening is effective as it is even after the saturation element 13. FIG. 23B represents the time change of the feedback control amount of the VNT nozzle opening. However, the dotted line represents the feedback control amount itself of the VNT nozzle opening, and changes greatly downward. However, since the VNT target value from the planner 11 is “5”, when added to this VNT target value, the feedback control amount of the VNT nozzle opening becomes “−5” or less, and “0” due to saturation characteristics. Saturates. In FIG. 23B, the feedback control amount that is effective in relation to the VNT target value “5” is indicated by a solid line.

  When the nozzle opening of the VNT is saturated in this way, as shown in FIG. 23C, the overshoot increases for the fresh air amount MAF in the output from the direct element Gp11 represented by a thin dotted line (expressed as a direct term). . For this reason, a large overshoot is formed in the response value represented by the solid line. On the other hand, as shown in FIG. 23D showing the time change of the intake pressure MAP, the response value of the intake pressure MAP represented by the solid line is the target value represented by the thin dotted line by the appropriate output from the interference element Gp12 represented by the alternate long and short dashed line Follow up properly.

  On the other hand, FIGS. 24A to 24D show simulation results and the like when the EGR valve opening is saturated. FIG. 24A shows the time change of the feedback control amount of the EGR valve opening. However, the dotted line represents the feedback control amount itself of the EGR valve opening and changes greatly downward. However, since the EGR target value from the planner 11 is “2”, when added to this EGR target value, the feedback control amount of the EGR valve opening becomes “−2” or less, and “0” due to saturation characteristics. Saturates. In FIG. 24A, the feedback control amount that is effective in relation to the EGR target value “2” is indicated by a solid line. On the other hand, FIG. 24B represents the time change of the feedback control amount of the VNT nozzle opening. Since the VNT nozzle opening is not saturated, the feedback control amount of the EGR valve opening is effective as it is even after the saturation element 13.

  Thus, when the valve opening of the EGR is saturated, as shown in FIG. 24C, a large undershoot occurs in the output from the interference element Gp21 represented by the alternate long and short dash line for the fresh air amount MAF, which is represented by a solid line. The response value of the fresh air amount MAF does not follow the target value very much. On the other hand, as shown in FIG. 24D, with respect to the intake pressure MAP, the output from the direct element Gp22 represented by a thin dotted line acts appropriately, and the response value represented by the solid line appropriately follows the target value represented by the long dotted line. ing.

  Thus, it can be seen that the target value followability of the intake pressure is improved.

  A functional block diagram of the engine control apparatus 1000 for realizing the functions of such a block diagram is represented in FIG. 17 which is the same as the functional block diagram of the first embodiment. However, the processing contents of the saturation compensation amount calculation unit 110 are different. Similarly, the processing flow itself is the same as that shown in FIG. 18, but the calculation contents in step S15 are different.

Specifically, EGRcomp [t] and VNTcomp [t] are expressed as follows.
VNTcomp [t] = D12 / C12 × EGRcomp [t-1]
+ A22 / C12 × (EGR [t] −EGRsat [t])
-B22 / C12 × (EGR [t-1] -EGRsat [t-1])
EGRcomp [t] = D22 / C22 × VNTcomp [t-1]
+ A12 / C22 × (VNT [t] −VNTsat [t])
-B12 / C22 x (VNT [t-1] -VNTsat [t-1])

  As described above, A12, B12, C12, and D12 are coefficients related to the interference element Gp12, and A22, B22, C22, and D22 are coefficients related to the direct element Gp22. These coefficients are also set in accordance with the actual characteristics of the engine 1.

  As shown above, the second saturation compensation amount VNTcomp [t] is the difference between the first term representing the effect one unit time ago and the current command value EGR [t] and the final command value EGR [t]. Is the sum of the second term representing the influence of the second term and the third term representing the influence of the difference between the command value EGR [t-1] one unit time ago and the final command value EGR [t-1]. The first saturation compensation amount EGRcomp [t] is a first term representing the influence of one unit time ago and the first saturation representing the influence of the difference between the current command value VNT [t] and the final command value VNT [t]. This is the sum of the second term and the third term representing the effect of the difference between the command value VNT [t-1] one unit time ago and the final command value VNT [t-1]. The data one unit time before is stored in a memory or the like and is read and used. Further, the current value is stored in a memory or the like, and is read out and used after one unit time.

  By doing in this way, the block diagram shown in FIG. 22 is implement | achieved, and the target value followability of fresh air quantity can be improved.

[Embodiment 4]
In the first embodiment, the target value followability on the non-saturation side is improved, but it cannot be said that the saturation side is sufficient. Therefore, anti-windup compensators 31 and 32 as shown in FIG. 25 are introduced to the first embodiment. FIG. 25 shows a block diagram for the fourth embodiment, but the difference from FIG. 14 showing the block diagram of the first embodiment is (A) the input of the saturation element 13. The result of multiplying the difference between the command value of the EGR valve opening and the final command value of the EGR valve opening that is the output of the saturation element 13 by the direct element Gp11 representing the degree of the EGR valve opening acting on the fresh air amount MAF Is added to the measured value of the fresh air amount MAF to perform negative feedback, (B) the command value of the VNT nozzle opening that is the input of the saturation element 17 and the final command value of the VNT nozzle opening that is the output of the saturation element 17 The result obtained by multiplying the difference between the two and a direct element Gp22 representing the degree of the VNT nozzle opening acting on the intake pressure MAP is added to the measured value of the intake pressure MAP and negatively fed back. That is, when there is no saturation, the fresh air amount for the direct element Gp11 and the intake pressure for Gp22 are predicted and fed back.

  When such antiwindup is introduced, the response characteristics and the like change as shown in FIGS. 26A to 26D. 26A to 26D show an example in which the VNT nozzle opening is saturated.

  FIG. 26A represents the time change of the feedback control amount of the EGR valve opening. Since the EGR valve opening is not saturated, the feedback control amount of the EGR valve opening is effective as it is even after the saturation element 13. FIG. 26B represents the time change of the feedback control amount of the VNT nozzle opening. However, the dotted line represents the feedback control amount itself of the VNT nozzle opening degree, and there is a portion that changes greatly downward. However, since the VNT target value from the planner 11 is “5”, when added to this VNT target value, the feedback control amount of the VNT nozzle opening becomes “−5” or less, and “0” due to saturation characteristics. Saturates. In FIG. 26B, the feedback control amount that is effective in relation to the VNT target value “5” is indicated by a solid line.

  In this embodiment, as in FIG. 15C shown in the first embodiment, the fresh air amount MAF has no overshoot in the output from the direct element Gp11 represented by the thin dotted line as shown in FIG. 26C. Yes. For this reason, the response value represented by the solid line has improved followability to the target value represented by the long dotted line. On the other hand, as shown in FIG. 26D showing the time change of the intake pressure MAP, the output of the interference element G12 represented by the alternate long and short dash line and the output of the direct element Gp22 represented by the thin dotted line are appropriately adjusted, and the response of the intake pressure MAP represented by the solid line The value appropriately follows the target value represented by the thick dotted line.

  Thus, by introducing the anti-windup compensators 31 and 32, the target value followability is improved also on the saturation side.

  FIG. 27 shows a functional block diagram of the engine control apparatus 1000 for realizing the functions of such a block diagram.

  The engine control apparatus 1000 includes (A) a fuel injection amount detection unit 101 that acquires a set value of the fuel injection amount Q, (B) an engine speed detection unit 102 that acquires a set value of the engine speed RPM, and (C ) A sensor value acquisition unit 103 that acquires a combination X (= [MAF, MAP]) of the measured value of the intake pressure and the measured value of the fresh air amount from the intake pressure sensor 2 and the fresh air amount sensor 3, and (D) the sensor value. A combination X of measurement values from the acquisition unit 103 and an antiwindup compensation amount Xawu (= [compensation amount of fresh air amount, compensation amount of intake air pressure]) from the antiwindup calculation unit 112 described below are added. An adder 111 that generates a compensated measurement value X2 (= [compensated MAF, compensated MAP]), and (F) Uref = [EGR valve] in association with a combination of the fuel injection amount value and the engine speed value. Opening And target value table 104 in which Xref (= [target value of MAF, target value of MAP]) and (G) fuel injection amount detection unit 101 are registered. A target value generator 105 that receives the set value of the fuel injection amount Q and the set value of the engine speed RPM output from the engine speed detector 102 and reads the corresponding Uref and Xref from the target value table 104; (H) From the compensated measurement value X2 from the addition unit 111, the fresh air amount from the target value generation unit 105, and the target value Xref of the intake pressure, feedback control amounts Ufb (= [EGR valve opening feedback control amount, VNT nozzle opening feedback control amount]) and (I) feedback control From Ufb, target value Uref, and saturation compensation amount Ucomp (= [EGR valve opening saturation compensation amount, VNT valve opening saturation compensation amount]) described below, command value U = ([EGR valve opening command Value, VNT nozzle opening command value]) and (J) a command value equal to or higher than a predetermined upper limit value is set as the upper limit value, and a command value equal to or lower than the predetermined lower limit value is set as the lower limit value. And a saturation processing unit 109 that generates a final command value Usat (= [final command value of EGR valve opening, final command value of VNT nozzle opening]), and (K) command value U A saturation compensation amount calculation unit 110 that generates a saturation compensation amount Ucomp from the final command value Usat, and (L) an antiwindup calculation unit 112 that generates an antiwindup compensation amount Xawu from the command value U and the final command value Usat. Have.

  Note that the EGR valve opening and the VNT nozzle opening of the engine 1 are controlled according to the output of the saturation processing unit 109.

  The operation of the engine control apparatus 1000 shown in FIG. 27 will be described using FIG. . First, at the start of operation, the time is set to t = 1 (FIG. 28: step S31). The fuel injection amount detection unit 101, the engine speed detection unit 102, and the sensor value acquisition unit 103 then set the fuel injection amount set value Q [t], the engine speed set value RPM [t], and the sensor value X [t. ] Is acquired (step S33).

  Then, the target value generation unit 105 obtains the target values Xref [t] and Uref [t] corresponding to the fuel injection amount setting value Q [t] and the engine speed setting value RPM [t] as the target value table 104. It generates by reading from (step S35). The adding unit 111 adds the sensor value X [t] acquired by the sensor value acquiring unit 103 and the anti-windup compensation amount Xawu [t−1] generated by the anti-windup calculating unit 112 to compensate the measurement. A value X2 [t] is generated (step S37). For the anti-windup compensation amount Xawu [t-1], the value one unit time before is added. The calculation of the anti-windup compensation amount Xawu [t-1] will be described later.

  Further, the feedback control amount generation unit 107 uses the feedback control amount Ufb [t] from the target value Xref [t] generated by the target value generation unit 105 and the compensated measurement value X2 [t] generated by the addition unit 111. (= F (X2 [t], Xref [t])) is generated (step S39). Note that the feedback amount Ufb [t] is the same function as in the first embodiment. Specifically, the control amount of the EGR valve opening obtained by inputting the difference between the target value of the fresh air amount MAF and the compensated measured value of the fresh air amount MAF to the fresh air amount controller 12, and non-interference The difference from the output result of the filter 15 is the feedback control amount of the EGR valve opening. Further, the control amount of the VNT nozzle opening obtained by inputting the difference between the target value of the intake pressure MAP and the compensated measured value of the intake pressure MAP to the intake pressure controller 16, the output result of the non-interacting filter 14, and Is the feedback control amount of the VNT nozzle opening.

  Then, the command value generation unit 108 outputs the output Uref [t] of the target value generation unit 105, the output Ufb [t] of the feedback control amount generation unit 107, and the saturation compensation amount Ucomp [t-1] one unit time ago. And the command value U [t] is calculated (step S41). That is, U [t] = Ufb [t] + Uref [t] + Ucomp [t−1] is calculated. As described above, U [t] is a combination of the valve opening of the EGR valve provided in the exhaust gas circulator EGR and the nozzle opening of the variable nozzle turbo VNT (= [EGR valve opening command Value, VNT nozzle opening command value]). Ucomp [t-1] is the same as in the first embodiment.

  Thereafter, the saturation processing unit 109 performs saturation processing (Usat [t] = saturation (U [t])) (step S43). As described above, the saturation processing outputs the upper limit value as the final command value if the command value is equal to or greater than the predetermined upper limit value, and outputs the lower limit value as the final command value if the command value is less than or equal to the predetermined lower limit value. However, other command values are output as they are. Such a process is performed for both the EGR valve opening and the VNT nozzle opening. Then, the saturation processing unit 109 outputs the final command value to the engine 1 (step S45).

Further, the saturation compensation amount calculation unit 110 calculates the saturation compensation amount Ucomp [t] using the command value U [t] from the command value generation unit 108 and the final command value Usat [t] from the saturation processing unit 109. (Step S47). The saturation compensation amount Ucomp [t] (= [EGRcomp [t], VNTcomp [t]) is used at the next time t + 1. The calculation method itself is the same as in the first embodiment. However, since there is a relationship with the anti-windup compensation amount, only the calculation formula is shown again.
VNTcomp [t] = D12 / C12 × EGRcomp [t-1]
+ A22 / C12 × (EGR [t] −EGRsat [t])
-B22 / C12 × (EGR [t-1] -EGRsat [t-1])
EGRcomp [t] = D21 / C21 × VNTcomp [t-1]
+ A11 / C21 × (VNT [t] −VNTsat [t])
-B11 / C21 x (VNT [t-1] -VNTsat [t-1])

  Further, the anti-windup calculation unit 112 uses the command value U [t] from the command value generation unit 108 and the final command value Usat [t] from the saturation processing unit 109 to perform the antiwindup compensation amount Xawu [t]. Is calculated (step S49). This anti-windup compensation amount Xawu [t] (= (MAFawu [t], MAPawu [t])) is used at the next time t + 1.

  The antiwindup compensator 31 for the new air amount shown in FIG. 25 is represented by a transfer function Gp11, and the antiwindup compensator 32 for the intake pressure is represented by a transfer function Gp22. Such direct achievements Gp11 and Gp22 also include a delay component as described above.

Therefore, MAFawu [t] and MAPawu [t] are expressed as follows.
MAFawu [t] = D11 / C11 × MAFawu [t-1]
+ K11 / C11 × (EGR [t] −EGRsat [t])
MAPawu [t] = D22 / C22 × MAPawu [t-1]
+ K22 / C22 × (VNT [t] −VNTsat [t])

  Here, C11 and D11 are coefficients related to the direct element Gp11, and D22 and C22 are coefficients related to the direct element Gp22. These coefficients are set according to the actual characteristics of the engine 1. The same symbol as in the saturation compensation amount formula represents the same value. K11 and K12 are predetermined coefficients, and these coefficients are also set in accordance with the actual characteristics of the engine 1.

  As shown above, MAFawu [t] and MAPawu [t] are the difference between the first term representing the effect one unit time ago and the current command value EGR [t] and the final command value EGR [t]. It is a sum with the second term representing the influence of. The data one unit time before is stored in a memory or the like and is read and used. Further, the current value is stored in a memory or the like, and is read out and used after one unit time.

  After step S49, t is incremented by 1 (step S51), and the process returns to step S33. The process is repeated until the engine is stopped.

  By doing so, the block diagram shown in FIG. 25 can be realized, and the target value followability on the saturation side and the non-saturation side can be improved.

[Embodiment 5]
In the second embodiment, the target value followability is improved by giving priority to the fresh air amount, but the intake pressure is not sufficient. Therefore, anti-windup compensators 31 and 32 as shown in FIG. 29 are introduced to the second embodiment. FIG. 29 shows a block diagram of the fifth embodiment, but the difference from FIG. 19 showing the block diagram of the second embodiment is the same as that of the fourth embodiment. (A) The EGR valve opening degree in the engine 1 is the fresh air amount in the difference between the command value of the EGR valve opening degree that is the input of the saturation element 13 and the final command value of the EGR valve opening degree that is the output of the saturation element 13. A result obtained by multiplying the result obtained by multiplying the direct element Gp11 representing the degree of acting on the MAF to the measured value of the fresh air amount MAF and negative feedback; The measured value of the intake pressure MAP is the result of multiplying the difference from the final command value of the VNT nozzle opening, which is the output of the element 17, by the direct element Gp22 representing the degree to which the VNT nozzle opening in the engine 1 acts on the intake pressure MAP. It is a portion for negative feedback in addition. That is, the new air amount for the direct element Gp11 and the intake pressure for the direct element Gp22 when there is no saturation are predicted and fed back.

  By introducing such anti-windup, it is expected that the target value followability for intake pressure will also be improved.

  As for the functional block diagram and the processing flow, the changes made in the second embodiment may be made to those described in the fourth embodiment with respect to the first embodiment.

[Embodiment 6]
In the third embodiment, the target value followability is improved by giving priority to the intake pressure, but the fresh air amount is not sufficient. Therefore, anti-windup compensators 31 and 32 as shown in FIG. 30 are introduced to the third embodiment. FIG. 30 shows a block diagram of the sixth embodiment, but the difference from FIG. 22 showing the block diagram of the third embodiment is the same as that of the fourth embodiment. (A) The EGR valve opening degree in the engine 1 is the fresh air amount in the difference between the command value of the EGR valve opening degree that is the input of the saturation element 13 and the final command value of the EGR valve opening degree that is the output of the saturation element 13. A part of negative feedback by adding the result of multiplying the direct Gp11 representing the degree of action on the MAF to the measured value of the fresh air amount MAF, and (B) the command value of the VNT nozzle opening which is the input of the saturation element 17 and the saturation element The result obtained by multiplying the difference from the final command value of the VNT nozzle opening, which is an output of 17, by the direct Gp22 representing the degree to which the VNT nozzle opening in the engine 1 acts on the intake pressure MAP is added to the measured value of the intake pressure MAP. The Is a portion that moths Restorative feedback. That is, the new air amount for the direct element Gp11 and the intake pressure for the direct element Gp22 when there is no saturation are predicted and fed back.

  By introducing such anti-windup, it is expected that the target value follow-up performance for the new air volume will also be improved.

  As for the functional block diagram and the processing flow, the changes made in the third embodiment may be made to those described in the fourth embodiment with respect to the first embodiment.

  Although the embodiment of the present technology has been described above, the present technology is not limited to this. For example, in the processing flow, the processing steps are illustrated in series for convenience, but may be performed in parallel as long as the processing result does not change. For example, steps S47 and S49 can be performed in parallel. The functional block diagram is also divided into blocks for convenience of explanation, and does not necessarily match the actual program module configuration.

  The engine control apparatus 1000 described above is a computer apparatus, and as shown in FIG. 31, a RAM (Random Access Memory) 2501, a processor 2503, a ROM (Read Only Memory) 2507, and a sensor group 2515 are provided as a bus. 2519 is connected. A control program (and an operating system (OS: Operating System, if present)) for executing the processing in the present embodiment is stored in the ROM 2507 and is executed by the processor 2503. The data is read from the ROM 2507 to the RAM 2501. The processor 2503 acquires necessary measurement values by controlling a sensor group (intake pressure sensor 2 and fresh air amount sensor 3. In some cases, a fuel injection amount measurement unit, an engine speed measurement unit, etc.) as necessary. To do. Further, data in the middle of processing is stored in the RAM 2501. Note that the processor 2503 may include a ROM 2507 and may further include a RAM 2501. In the embodiment of the present technology, a control program for performing the above-described processing may be stored and distributed on a computer-readable removable disk and written to the ROM 2507 by a ROM writer. Such a computer device has various functions as described above by organically cooperating hardware such as the processor 2503, RAM 2501, and ROM 2507 described above and a control program (or OS in some cases). Is realized.

  However, it is also possible to mount the entire engine control device only by hardware. The above-described embodiment can be summarized as follows.

  The engine control method according to the present embodiment includes (A) a set value of fuel injection amount for an engine having an exhaust circulator and a variable nozzle turbo, a set value of engine speed, a measured value of engine intake pressure, and a fresh air amount. (B) a target value of intake pressure and a target value of fresh air corresponding to a set value of fuel injection amount and a set value of engine speed, a set value of fuel injection amount, and an engine Obtaining a target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator corresponding to the set value of the rotational speed; and (C) a target value of the intake pressure and a target of the fresh air amount From the measured value, the measured value of the intake pressure, and the measured value of the fresh air amount, the control amount of the nozzle opening of the variable nozzle turbo and the control amount of the valve opening of the exhaust circulator (for example, the feedback control amount in the embodiment) are calculated. Control amount calculation And (D) a variable nozzle turbo nozzle opening control amount and an exhaust circulator valve opening control amount, a variable nozzle turbo nozzle opening target value, and an exhaust circulator valve opening target value. And a first saturation compensation amount for compensating the nozzle opening of the variable nozzle turbo with respect to the saturation of the valve opening of the exhaust circulator and the valve of the exhaust circulator with respect to the saturation of the nozzle opening of the variable nozzle turbo. And a command value calculating step of calculating a command value of the nozzle opening of the variable nozzle turbo and a command value of the valve opening of the exhaust circulator from the second saturation compensation amount for compensating the opening.

  By introducing the first and second saturation compensation amounts as described above, the target value followability can be improved even if there is saturation.

  Further, in the engine control method described above, (E) a step of calculating an anti-windup compensation amount of the engine intake pressure in accordance with the degree to which the command value of the nozzle opening of the variable nozzle turbo acts on the intake pressure of the engine. And (F) calculating an anti-windup compensation amount for the fresh air amount of the engine according to the degree to which the command value of the valve opening degree of the exhaust circulator acts on the fresh air amount of the engine. At that time, the control amount calculation step further uses the anti-windup compensation amount of the engine intake pressure and the anti-windup compensation amount of the fresh air amount of the engine to further control the nozzle opening amount of the variable nozzle turbo and the exhaust circulator. The control amount of the valve opening may be calculated. In this way, the windup phenomenon can be reduced. Note that the control amount calculation step may include the process of the decoupling filter described in the embodiment.

  Further, the engine control method described above includes (G) the first interference component relating to the degree to which the command value of the nozzle opening of the variable nozzle turbo acts on the fresh air amount of the engine and the command of the nozzle opening of the variable nozzle turbo. A step of calculating the first saturation compensation amount including a first direct achievement relating to the degree of the value acting on the intake pressure of the engine; and (H) a command value of the valve opening of the exhaust circulator is determined by the intake pressure of the engine Calculating a second saturation compensation amount including a second interference component relating to the degree of effect on the engine and a second direct achievement relating to the degree to which the command value of the valve opening of the exhaust circulator acts on the fresh air amount of the engine May be further included.

  For example, as in the first or fourth embodiment, it is effective when the non-saturation side is prioritized to follow the target value.

  Further, the engine control method described above includes (I) the second interference component relating to the degree to which the command value of the exhaust circulator valve opening acts on the intake air pressure of the engine and the command value of the valve circulator opening of the exhaust circulator. Calculating a first saturation compensation amount including a second direct achievement relating to the degree to which the engine acts on the fresh air amount of the engine, and (J) a second including a second interference component and a second direct achievement And a step of calculating a saturation compensation amount.

  For example, as in the second or fifth embodiment, it is effective when the new air amount is prioritized to follow the target value.

  Further, the engine control method described above includes (K) the first interference component relating to the degree to which the command value of the nozzle opening of the variable nozzle turbo acts on the fresh air amount of the engine and the command of the valve opening of the exhaust circulator. Calculating a first saturation compensation amount including a second direct achievement relating to the degree of the value acting on the fresh air amount of the engine; and (L) a first including a first interference component and a second direct achievement. And a step of calculating a saturation compensation amount of 2.

  For example, as in the third or sixth embodiment, it is effective when the intake pressure is prioritized to follow the target value.

  Further, the engine control device (FIG. 32) (A) sets the fuel injection amount for the engine having the exhaust circulator and the variable nozzle turbo, the set value of the engine speed, the measured value of the engine intake pressure, and the fresh air amount. A sensor value acquisition unit for acquiring a measured value of (B), (B) a target value of intake pressure and a target value of fresh air amount corresponding to a set value of fuel injection amount and a set value of engine speed, and setting of fuel injection amount A target value acquisition unit for acquiring the target value of the nozzle opening of the variable nozzle turbo and the target value of the valve opening of the exhaust circulator corresponding to the value and the set value of the engine speed, and (C) the target value of the intake pressure Control amount calculation for calculating the control amount of the nozzle opening of the variable nozzle turbo and the control amount of the valve opening of the exhaust circulator from the target value of the new air amount, the measured value of the intake air pressure, and the measured value of the new air amount And (D) variable nozzle turbo nozzle opening Control amount and exhaust valve circulator valve opening control amount, variable nozzle turbo nozzle opening target value, exhaust circulator valve opening target value, and exhaust circulator valve opening target saturation The first saturation compensation amount for compensating the nozzle opening of the variable nozzle turbo and the second saturation compensation amount for compensating the valve opening of the exhaust circulator against the saturation of the nozzle opening of the variable nozzle turbo And a command value generation unit for calculating a command value of the nozzle opening of the variable nozzle turbo and a command value of the valve opening of the exhaust circulator.

  A program for causing the processor to perform the processing according to the above method can be created, and the program can be a computer-readable storage medium such as a flexible disk, a CD-ROM, a magneto-optical disk, a semiconductor memory, a hard disk, or the like. It is stored in a storage device. The intermediate processing result is temporarily stored in a storage device such as a main memory.

  The following supplementary notes are further disclosed with respect to the embodiments including the above examples.

(Appendix 1)
Obtaining a set value of fuel injection amount for an engine having an exhaust circulator and a variable nozzle turbo, a set value of engine speed, a measured value of intake pressure of the engine and a measured value of fresh air;
The target value of the intake pressure and the target value of the fresh air amount corresponding to the set value of the fuel injection amount and the set value of the engine speed, the set value of the fuel injection amount, and the set value of the engine speed Obtaining a corresponding target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator;
From the target value of the intake pressure and the target value of the fresh air amount, the measured value of the intake pressure and the measured value of the fresh air amount, the control amount of the nozzle opening of the variable nozzle turbo and the valve of the exhaust circulator A control amount calculating step for calculating a control amount of the opening;
A control amount of the nozzle opening of the variable nozzle turbo and a control amount of the valve opening of the exhaust circulator, a target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator, A first saturation compensation amount for compensating the nozzle opening of the variable nozzle turbo with respect to saturation of the valve opening of the exhaust circulator, and the exhaust circulation with respect to saturation of the nozzle opening of the variable nozzle turbo. A command value calculating step of calculating a command value of the nozzle opening of the variable nozzle turbo and a command value of the valve opening of the exhaust circulator from a second saturation compensation amount for compensating the valve opening of the exhaust device; ,
Engine control program for causing a processor to execute

(Appendix 2)
Calculating an anti-windup compensation amount of the engine intake pressure according to the degree to which the command value of the nozzle opening of the variable nozzle turbo acts on the intake pressure of the engine;
Calculating an anti-windup compensation amount of the new air amount of the engine according to a degree to which a command value of the valve opening degree of the exhaust circulator acts on the fresh air amount of the engine;
Is further executed by the processor,
In the control amount calculation step,
Further using the anti-windup compensation amount of the engine intake pressure and the anti-windup compensation amount of the new air amount of the engine, the control amount of the nozzle opening of the variable nozzle turbo and the valve opening of the exhaust circulator The engine control program according to appendix 1, which calculates a control amount.

(Appendix 3)
The first interference component related to the degree to which the command value of the nozzle opening of the variable nozzle turbo acts on the fresh air amount of the engine and the degree of the command value of the nozzle opening of the variable nozzle turbo acting on the intake pressure of the engine Calculating the first saturation compensation amount including a first direct achievement for
The second interference component related to the degree to which the command value of the valve opening of the exhaust circulator acts on the intake air pressure of the engine and the degree of the command value of the valve opening of the exhaust circulator acting on the fresh air amount of the engine Calculating the second saturation compensation amount including a second direct achievement for
3. The engine control program according to appendix 1 or 2 for causing the processor to execute.

(Appendix 4)
The second interference component related to the degree to which the command value of the valve opening of the exhaust circulator acts on the intake air pressure of the engine and the degree of the command value of the valve opening of the exhaust circulator acting on the fresh air amount of the engine Calculating the first saturation compensation amount including a second direct achievement for
Calculating the second saturation compensation amount including the second interference component and the second direct achievement;
3. The engine control program according to appendix 1 or 2 for causing the processor to execute.

(Appendix 5)
The first interference component relating to the degree to which the command value of the nozzle opening of the variable nozzle turbo acts on the fresh air amount of the engine and the command value of the valve opening of the exhaust circulator acts on the fresh air amount of the engine. Calculating the first saturation compensation amount including a second direct achievement relating to the degree;
Calculating the second saturation compensation amount including the first interference component and the second direct achievement;
3. The engine control program according to appendix 1 or 2 for causing the processor to execute.

(Appendix 6)
Obtaining a set value of fuel injection amount for an engine having an exhaust circulator and a variable nozzle turbo, a set value of engine speed, a measured value of intake pressure of the engine and a measured value of fresh air;
The target value of the intake pressure and the target value of the fresh air amount corresponding to the set value of the fuel injection amount and the set value of the engine speed, the set value of the fuel injection amount, and the set value of the engine speed Obtaining a corresponding target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator;
From the target value of the intake pressure and the target value of the fresh air amount, the measured value of the intake pressure and the measured value of the fresh air amount, the control amount of the nozzle opening of the variable nozzle turbo and the valve of the exhaust circulator A control amount calculating step for calculating a control amount of the opening;
A control amount of the nozzle opening of the variable nozzle turbo and a control amount of the valve opening of the exhaust circulator, a target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator, A first saturation compensation amount for compensating the nozzle opening of the variable nozzle turbo with respect to saturation of the valve opening of the exhaust circulator, and the exhaust circulation with respect to saturation of the nozzle opening of the variable nozzle turbo. A command value calculating step of calculating a command value of the nozzle opening of the variable nozzle turbo and a command value of the valve opening of the exhaust circulator from a second saturation compensation amount for compensating the valve opening of the exhaust device; ,
Including an engine control method.

(Appendix 7)
A sensor value acquisition unit for acquiring a set value of fuel injection amount for an engine having an exhaust circulator and a variable nozzle turbo, a set value of engine speed, a measured value of intake pressure of the engine, and a measured value of fresh air amount When,
The target value of the intake pressure and the target value of the fresh air amount corresponding to the set value of the fuel injection amount and the set value of the engine speed, the set value of the fuel injection amount, and the set value of the engine speed A target value acquisition unit for acquiring the target value of the corresponding nozzle opening of the variable nozzle turbo and the target value of the valve opening of the exhaust circulator;
From the target value of the intake pressure and the target value of the fresh air amount, the measured value of the intake pressure and the measured value of the fresh air amount, the control amount of the nozzle opening of the variable nozzle turbo and the valve of the exhaust circulator A control amount calculation unit for calculating a control amount of the opening;
A control amount of the nozzle opening of the variable nozzle turbo and a control amount of the valve opening of the exhaust circulator, a target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator, A first saturation compensation amount for compensating the nozzle opening of the variable nozzle turbo with respect to saturation of the valve opening of the exhaust circulator, and the exhaust circulation with respect to saturation of the nozzle opening of the variable nozzle turbo. A command value generator for calculating a command value of the nozzle opening of the variable nozzle turbo and a command value of the valve opening of the exhaust circulator from a second saturation compensation amount for compensating the valve opening of the exhaust device; ,
An engine control device.

DESCRIPTION OF SYMBOLS 101 Fuel injection amount detection part 102 Engine speed detection part 103 Sensor value acquisition part 104 Target value table 105 Target value generation part 107 Feedback control amount generation part 108 Command value generation part 109 Saturation processing part 110 Saturation compensation amount calculation part 111 Addition part 112 Anti-windup calculation unit 1 Engine 2 Intake pressure sensor 3 New air volume sensor

Claims (7)

Obtaining a set value of fuel injection amount for an engine having an exhaust circulator and a variable nozzle turbo, a set value of engine speed, a measured value of intake pressure of the engine and a measured value of fresh air;
The target value of the intake pressure and the target value of the fresh air amount corresponding to the set value of the fuel injection amount and the set value of the engine speed, the set value of the fuel injection amount, and the set value of the engine speed Obtaining a corresponding target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator;
From the target value of the intake pressure and the target value of the fresh air amount, the measured value of the intake pressure and the measured value of the fresh air amount, the control amount of the nozzle opening of the variable nozzle turbo and the valve of the exhaust circulator A control amount calculating step for calculating a control amount of the opening;
A control amount of the nozzle opening of the variable nozzle turbo and a control amount of the valve opening of the exhaust circulator, a target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator, A first saturation compensation amount for compensating the nozzle opening of the variable nozzle turbo with respect to saturation of the valve opening of the exhaust circulator, and the exhaust circulation with respect to saturation of the nozzle opening of the variable nozzle turbo. A command value calculating step of calculating a command value of the nozzle opening of the variable nozzle turbo and a command value of the valve opening of the exhaust circulator from a second saturation compensation amount for compensating the valve opening of the exhaust device; ,
Engine control program for causing a processor to execute Calculating an anti-windup compensation amount of the engine intake pressure according to the degree to which the command value of the nozzle opening of the variable nozzle turbo acts on the intake pressure of the engine;
Calculating an anti-windup compensation amount of the new air amount of the engine according to a degree to which a command value of the valve opening degree of the exhaust circulator acts on the fresh air amount of the engine;
Is further executed by the processor,
In the control amount calculation step,
Further using the anti-windup compensation amount of the engine intake pressure and the anti-windup compensation amount of the new air amount of the engine, the control amount of the nozzle opening of the variable nozzle turbo and the valve opening of the exhaust circulator The engine control program according to claim 1, wherein the control amount is calculated. The first interference component related to the degree to which the command value of the nozzle opening of the variable nozzle turbo acts on the fresh air amount of the engine and the degree of the command value of the nozzle opening of the variable nozzle turbo acting on the intake pressure of the engine Calculating the first saturation compensation amount including a first direct achievement for
The second interference component related to the degree to which the command value of the valve opening of the exhaust circulator acts on the intake air pressure of the engine and the degree of the command value of the valve opening of the exhaust circulator acting on the fresh air amount of the engine Calculating the second saturation compensation amount including a second direct achievement for
The engine control program according to claim 1, further causing the processor to execute. The second interference component related to the degree to which the command value of the valve opening of the exhaust circulator acts on the intake air pressure of the engine and the degree of the command value of the valve opening of the exhaust circulator acting on the fresh air amount of the engine Calculating the first saturation compensation amount including a second direct achievement for
Calculating the second saturation compensation amount including the second interference component and the second direct achievement;
The engine control program according to claim 1, further causing the processor to execute. The first interference component relating to the degree to which the command value of the nozzle opening of the variable nozzle turbo acts on the fresh air amount of the engine and the command value of the valve opening of the exhaust circulator acts on the fresh air amount of the engine. Calculating the first saturation compensation amount including a second direct achievement relating to the degree;
Calculating the second saturation compensation amount including the first interference component and the second direct achievement;
The engine control program according to claim 1, further causing the processor to execute. Obtaining a set value of fuel injection amount for an engine having an exhaust circulator and a variable nozzle turbo, a set value of engine speed, a measured value of intake pressure of the engine and a measured value of fresh air;
The target value of the intake pressure and the target value of the fresh air amount corresponding to the set value of the fuel injection amount and the set value of the engine speed, the set value of the fuel injection amount, and the set value of the engine speed Obtaining a corresponding target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator;
From the target value of the intake pressure and the target value of the fresh air amount, the measured value of the intake pressure and the measured value of the fresh air amount, the control amount of the nozzle opening of the variable nozzle turbo and the valve of the exhaust circulator A control amount calculating step for calculating a control amount of the opening;
A control amount of the nozzle opening of the variable nozzle turbo and a control amount of the valve opening of the exhaust circulator, a target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator, A first saturation compensation amount for compensating the nozzle opening of the variable nozzle turbo with respect to saturation of the valve opening of the exhaust circulator, and the exhaust circulation with respect to saturation of the nozzle opening of the variable nozzle turbo. A command value calculating step of calculating a command value of the nozzle opening of the variable nozzle turbo and a command value of the valve opening of the exhaust circulator from a second saturation compensation amount for compensating the valve opening of the exhaust device; ,
Including an engine control method. A sensor value acquisition unit for acquiring a set value of fuel injection amount for an engine having an exhaust circulator and a variable nozzle turbo, a set value of engine speed, a measured value of intake pressure of the engine, and a measured value of fresh air amount When,
The target value of the intake pressure and the target value of the fresh air amount corresponding to the set value of the fuel injection amount and the set value of the engine speed, the set value of the fuel injection amount, and the set value of the engine speed A target value acquisition unit for acquiring the target value of the corresponding nozzle opening of the variable nozzle turbo and the target value of the valve opening of the exhaust circulator;
From the target value of the intake pressure and the target value of the fresh air amount, the measured value of the intake pressure and the measured value of the fresh air amount, the control amount of the nozzle opening of the variable nozzle turbo and the valve of the exhaust circulator A control amount calculation unit for calculating a control amount of the opening;
A control amount of the nozzle opening of the variable nozzle turbo and a control amount of the valve opening of the exhaust circulator, a target value of the nozzle opening of the variable nozzle turbo and a target value of the valve opening of the exhaust circulator, A first saturation compensation amount for compensating the nozzle opening of the variable nozzle turbo with respect to saturation of the valve opening of the exhaust circulator, and the exhaust circulation with respect to saturation of the nozzle opening of the variable nozzle turbo. A command value generator for calculating a command value of the nozzle opening of the variable nozzle turbo and a command value of the valve opening of the exhaust circulator from a second saturation compensation amount for compensating the valve opening of the exhaust device; ,
An engine control device.

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