JP4263134B2 - Control device for movable part drive mechanism - Google Patents

Description

  The present invention relates to a control device for a movable part drive mechanism in which at least one of an operation timing and an operation amount of a movable part of an internal combustion engine is changed, and a periodic disturbance whose amplitude periodically changes with the operation of the internal combustion engine is applied. About.

  2. Description of the Related Art Conventionally, a control device for a movable part drive mechanism that changes at least one of the operation timing and the operation amount of a movable part of an internal combustion engine is disclosed in Patent Document 1. This movable part drive mechanism changes the valve timing of the intake valve by freely changing the phase of the intake camshaft, that is, the intake cam crankshaft (hereinafter referred to as “cam phase”). It is composed of a variable cam phase mechanism and an electromagnetic control valve that supplies hydraulic pressure from an oil pump to the variable cam phase mechanism. In addition, the control device includes a crank angle sensor and a cam angle sensor that detect signals corresponding to the angular positions of the crankshaft and the intake cam, respectively, and a controller to which detection signals of these sensors are input.

  This controller calculates the actual cam phase based on the detection signals of the crank angle sensor and the cam angle sensor, calculates the target cam phase based on the operating state of the internal combustion engine, and, as described below, sliding mode control The variable cam phase mechanism is controlled by an algorithm so that the cam phase converges to the target cam phase. That is, a system in which a control signal to the electromagnetic control valve is a control input and a cam phase is output is regarded as a control target, and the control target is modeled as a continuous time system model. Specifically, the state equation to be controlled is set as a differential equation having first and second time differential values of the cam phase as state variables. Furthermore, the switching function in the sliding mode control algorithm is set as a linear function having the deviation between the target cam phase and the cam phase and the time differential value (that is, the changing speed) as a state variable. Then, by calculating the control input so that the deviation and the change speed thereof, which are the state variables of the switching function set as described above, are placed on the switching line, that is, the deviation and the changing speed slide on the switching line, By calculating the control input to converge to the value 0, the cam phase is controlled to converge to the target cam phase.

  Further, the present applicant has already proposed a control device using a sliding mode control algorithm described in Patent Document 2. This control device controls a throttle valve driving device of an internal combustion engine, and includes an adaptive sliding mode controller, an on-board identifier, a state predictor, and the like. The throttle valve drive device changes the opening degree by driving the throttle valve, and includes a motor and the like.

  In this control device, a control input for controlling the throttle valve driving device is calculated as follows. That is, the duty ratio of the control signal to the motor is set as the control input, and the system that outputs the opening degree deviation between the opening degree of the throttle valve and the target opening degree is regarded as the control target, and the control target is set as the duty ratio, It is modeled as a discrete-time system model that defines the relationship between the opening deviation and the compensation value. This compensation value is for compensating for the modeling error and disturbance of the controlled object model.

  Then, the model parameters and the compensation values of the controlled object model are identified and calculated by the on-board identifier, and the control input is calculated by the sliding mode control algorithm in the adaptive sliding mode controller using these identified values. In this control apparatus, since the control input is calculated as described above, the modeling error and disturbance of the controlled object model can be appropriately compensated, thereby ensuring high control accuracy.

Japanese Patent Laid-Open No. 2001-132482 JP 2003-5804 A

  In the control device of Patent Document 1 described above, (f1) the influence of the disturbance applied to the controlled object is not taken into consideration. Therefore, in the case of a controlled object such as a variable cam phase mechanism that is susceptible to a steady disturbance, the steady disturbance As a result, the stability and accuracy of control are reduced. (F2) Further, since the variable cam phase mechanism freely changes the cam phase of the intake cam with respect to the crankshaft, when the intake cam opens and closes the intake valve, the biasing force and reaction force of the valve spring of the intake valve are reduced. Due to the force, a periodic disturbance whose amplitude periodically changes is received (see FIG. 12 described later). When such a periodic disturbance is received, the opening time of the intake valve is shortened as a whole due to the influence thereof (see FIGS. 14 and 15 to be described later), and the intake air amount at the time of opening the valve is reduced. The engine torque is reduced and the combustion state becomes unstable.

  (F3) Since a continuous-time system model is used as the controlled object model, it is difficult to directly identify the model parameters of the controlled object model from the experimental data of the controlled object. Therefore, it is necessary to approximately convert a continuous-time system model to a discrete-time system model and identify model parameters based on the model, and the use of such approximate conversion reduces the accuracy of model parameter identification. Resulting in. Furthermore, since the discrete-time system model must be approximated again to the continuous-time system model, the modeling error of the control target model also increases by using such two approximate transformations. As a result, it is necessary to keep the controller gain low in order to ensure a stable control margin, and the controllability is further reduced. In other words, the control device of Patent Document 1 cannot secure the robustness and response designating characteristics peculiar to sliding mode control.

  In order to solve the problems of Patent Document 1 as described above, it is conceivable to apply the control method of Patent Document 2 to the control apparatus of Patent Document 1. In this case, although the problems (f1) and (f3) of Patent Document 1 described above can be solved, the compensation method is calculated by the on-board identifier in the control method of Patent Document 2, so that calculation is performed. Until the number of times reaches a predetermined value, the problem (f2) cannot be solved. That is, it takes some time to compensate for and suppress the influence of periodic disturbances, during which time control stability and control accuracy may be reduced.

  The present invention has been made to solve the above problems, and can more quickly compensate for and suppress the influence of periodic disturbances on the movable part drive mechanism, thereby improving the stability and accuracy of control. It is an object of the present invention to provide a control device for a movable part drive mechanism that can be improved.

In order to achieve the above object, the invention according to claim 1 is directed to the operation timing (cam phase Cain) and the operation amount (valve lift Liftin) of the movable portion (intake valve 4, intake camshaft 5, piston 3b) of the internal combustion engine 3. , with changes at least one of the stroke) of the piston 3b, the movable portion driving mechanism periodic disturbances whose amplitude varies periodic manner with the rotation of the crankshaft 3d of the engine 3 is added (variable valve lift mechanism 50, the control device 1, 1A, 1B of the variable cam phase mechanism 70 and the variable compression ratio mechanism 80) for predicting a change in amplitude of the periodic disturbance accompanying the rotation of the crankshaft 3d to compensate for the periodic disturbance. A plurality of disturbance compensation values set in advance according to the results (map value Rcyc_bs_cin of disturbance compensation values for cam phase control, valve lift Disturbance compensation value storage means (ECU2, ROM2c, compensation elements 102, 112, 122, 202, 212, 222, 222) for storing a map value Rcyc_bs_lin of a disturbance compensation value for control, and a map value Rcyc_bs_cr of a disturbance compensation value for compression ratio control 302, 312, 322) and every time the crankshaft 3d of the internal combustion engine 3 rotates by a predetermined angle, at a corresponding selection timing (generation timing of the CRK signal), a plurality of stored disturbance compensation values are selected. Disturbance compensation value selection means (ECU2, compensation elements 102, 112, 122, 202, 212, 222, 302, 312, 322, steps 6, 9, 12) for selecting a disturbance compensation value according to the selection timing, and a movable part Control input for controlling the drive mechanism (SLD control input Rsld for cam phase control, cam Reference input Rsld_f for phase control, SLD control input Rsld ′ for valve lift control, reference input Rsld_f ′ for valve lift control, SLD control input Rsld ″ for compression ratio control, reference input Rsld_f ′ for compression ratio control the '), the control input calculating means for de San according to the selected disturbance compensation value (ECU2,2 degree-of-freedom sliding mode controller 103,113,123,203,213,223,303,313,323, summing element 104 , 114, 124, steps 25-28).

According to the control device for the movable part drive mechanism, a plurality of disturbance compensation values for compensating for the periodic disturbance are set in advance according to the prediction result of the amplitude change of the periodic disturbance. Each time the crankshaft of the internal combustion engine rotates by a predetermined angle, a disturbance compensation value corresponding to the selection timing is selected from the plurality of disturbance compensation values. Therefore, by appropriately setting the predetermined angle, the disturbance compensation value can be selected as a value that can compensate for the periodic disturbance appropriately and quickly. Further, the need only to select the disturbance compensation value, according to the disturbance compensation value selected so, since the control input for controlling the movable section driving mechanism is issued calculated, so calculated control input By controlling the movable part drive mechanism using the above, the influence of the periodic disturbance on at least one of the operation timing and the operation amount of the movable part can be compensated and suppressed more quickly than in the past. As a result, the stability and control accuracy of the control of the movable part drive mechanism can be improved (Note that “disturbance compensation value storage” in this specification is not limited to storing the disturbance compensation value in a memory or the like. In addition, the disturbance compensation value is stored in the apparatus, and “calculation” such as “calculation of control input” and “calculation of disturbance estimated value” is not limited to calculation by a program, Generating an electrical signal representative of

  According to a second aspect of the present invention, in the control device 1, 1A, 1B for the movable part drive mechanism according to the first aspect, the movable part drive mechanism is at least one of the intake camshaft 5 and the exhaust camshaft 8 of the internal combustion engine 3. It includes a variable cam phase mechanism 70 that changes a cam phase Cain that is a phase with respect to the crankshaft 3d as an operation timing of the movable portion.

  According to the control device for the movable part drive mechanism, the movable part drive mechanism includes the variable cam phase mechanism that changes the cam phase as the operation timing of the movable part, so that the control input calculated according to the disturbance compensation value is used. By controlling the variable cam phase mechanism, the effect of periodic disturbance on the variable cam phase mechanism can be compensated and suppressed more quickly than before, and the stability and control accuracy in the control of the variable cam phase mechanism can be improved. Can be improved. Thereby, when the variable cam phase mechanism is applied to the one that changes the cam phase on the intake camshaft side, unlike the conventional case, it is possible to avoid that the opening time of the intake valve is shortened as a whole due to the influence of periodic disturbance, It is possible to avoid a reduction in the intake air amount when the valve is opened. As a result, the generated torque of the internal combustion engine can be appropriately secured and a stable combustion state can be secured. In addition, when the variable cam phase mechanism is applied to one that changes the cam phase on the exhaust camshaft side, the exhaust valve opening time is shortened as a whole due to the influence of periodic disturbance, and the internal EGR amount is prevented from decreasing. it can. As a result, a stable combustion state can be secured.

  According to a third aspect of the present invention, in the control device 1, 1A, 1B for the movable part drive mechanism according to the second aspect, the disturbance compensation value selection means further includes a cam phase parameter (target cam phase Cain_cmd) representing the cam phase. Accordingly, a disturbance compensation value (map value Rcyc_bs_cin of disturbance compensation value for cam phase control) is selected (step 6).

  In general, when the variable cam phase mechanism is provided in the internal combustion engine, when the cam phase is changed by the variable cam phase mechanism, the phase of the periodic disturbance applied to the variable cam phase mechanism changes accordingly. On the other hand, according to this control device, the disturbance compensation value is further selected in accordance with the cam phase parameter representing the cam phase, so that the disturbance compensation value is changed to the phase change of the periodic disturbance accompanying the change of the cam phase. Can be selected as a value that can be appropriately compensated. Thereby, the stability and control accuracy in the control of the variable cam phase mechanism can be further improved.

  According to a fourth aspect of the present invention, in the control device 1, 1A, 1B for the movable part drive mechanism according to the second or third aspect, the internal combustion engine 3 is at least one of the intake valve 4 and the exhaust valve 7 of the internal combustion engine 3. A variable valve lift mechanism 50 that changes a valve lift Liftin that is a lift is provided, and the plurality of disturbance compensation values are at least one of an amplitude change and a behavior change of a periodic disturbance accompanying a change of the valve lift Liftin by the variable valve lift mechanism 50. The disturbance compensation value selection means is further set according to the prediction result, and the disturbance compensation value selection means further determines a disturbance compensation value (map value Rcyc_bs_cin of disturbance compensation value for cam phase control) according to a valve lift parameter (valve lift Liftin) indicating valve lift. ) Is selected (step 6).

  In general, when a variable valve lift mechanism is provided in an internal combustion engine, when the valve lift is changed by the variable valve lift mechanism, at least one of the amplitude and behavior of a periodic disturbance applied to the variable cam phase mechanism is accordingly accompanied. Also changes. On the other hand, according to this control device, a plurality of disturbance compensation values are further set according to the prediction result of at least one of the amplitude change and behavior change of the periodic disturbance accompanying the change of the valve lift by the variable valve lift mechanism. Since the disturbance compensation value is further selected in accordance with the valve lift parameter representing the valve lift, the disturbance compensation value is determined based on at least one of the amplitude change and the behavior change of the periodic disturbance accompanying the change of the valve lift. It can be selected as a value that can be compensated appropriately. Thereby, stability and control accuracy in the control of the variable cam phase mechanism can be further improved.

  According to a fifth aspect of the present invention, in the control device 1, 1A, 1B for the movable part drive mechanism according to any of the second to fourth aspects, the control input calculating means includes a disturbance compensation value (disturbance compensation for cam phase control). The map value Rcyc_bs_cin) is corrected in accordance with the rotational speed NE of the internal combustion engine 3 (steps 7 and 8), and control input (in accordance with the corrected disturbance compensation value (disturbance compensation value Rcyc_cin for cam phase control)) ( The SLD control input Rsld for cam phase control and the reference input Rsld_f for cam phase control are calculated.

  Generally, when the rotational speed of the internal combustion engine changes, the frequency of the periodic disturbance applied to the variable cam phase mechanism also changes accordingly. On the other hand, according to this control device, the disturbance compensation value is corrected in accordance with the rotational speed of the internal combustion engine, so that the frequency change of the periodic disturbance accompanying the rotational speed change of the internal combustion engine is added to the corrected disturbance compensation value. Can be reflected. Further, since the control input is calculated according to the disturbance compensation value corrected as described above, the variable cam phase mechanism is controlled while appropriately compensating for the frequency change of the periodic disturbance accompanying the rotational speed change of the internal combustion engine. be able to.

  According to a sixth aspect of the present invention, in the control device 1, 1A, 1B for the movable part drive mechanism according to any of the second to fifth aspects, the control input calculating means is configured such that the rotational speed NE of the internal combustion engine 3 is a predetermined rotational speed. When it is greater than or equal to NEREF1, the control input is calculated regardless of the disturbance compensation value (Rcyc_cin = 0).

  In the control device according to the second aspect, the disturbance compensation value is selected at a selection timing corresponding to the rotation of the crankshaft of the internal combustion engine every predetermined angle. Therefore, when the rotational speed of the internal combustion engine becomes high, the disturbance compensation value is selected. Compensation value selection timing interval, that is, the selection cycle becomes extremely short, and when the control input is calculated using the disturbance compensation value selected in such a short selection cycle, the variable cam phase mechanism has low responsiveness. Thus, disturbance compensation cannot be performed properly, and controllability may be reduced. On the other hand, in the control device according to the sixth aspect, the control input is calculated regardless of the disturbance compensation value when the rotational speed of the internal combustion engine is equal to or higher than the predetermined rotational speed. By setting the value, the variable cam phase mechanism can be controlled while avoiding a decrease in controllability in the high rotation range.

The invention according to claim 7 is the target cam phase setting for setting the target cam phase Cain_cmd which is the target of the cam phase in the control device 1, 1A, 1B of the movable part drive mechanism according to any of claims 2 to 6. Means (ECU2, target cam phase calculation units 101, 201, 301), and the control input calculation means uses a predetermined response designation control algorithm so that the cam phase Cain converges to the target cam phase Cain_cmd. A control input is calculated .

According to this control device for the movable part drive mechanism , the control input is calculated using a predetermined response designating control algorithm so that the cam phase converges to the target cam phase. Even if a large deviation occurs during the period, the cam phase can be quickly and accurately converged to the target cam phase while avoiding the occurrence of overshoot due to such deviation. As a result, control stability and control accuracy can be significantly improved.

  According to an eighth aspect of the present invention, there is provided a disturbance estimation value (cam) for compensating for disturbances and modeling errors in the variable cam phase mechanism 70 in the control device 1A for the movable part drive mechanism according to any one of the second to sixth aspects. The estimated disturbance value c1) for phase control is estimated based on a model [formula (20)] that defines the relationship between the estimated disturbance value, the control input (SLD control input Rsld for cam phase control), and the cam phase Cain. Disturbance estimated value calculation means (ECU2, adaptive disturbance observer 206) calculated by an algorithm is further provided, and the control input calculation means calculates the control input further according to the calculated disturbance estimated value.

  According to the control device for the movable part drive mechanism, the disturbance estimated value for compensating for disturbance and modeling error in the variable cam phase mechanism is based on a model that defines the relationship between the disturbance estimated value, the control input, and the cam phase. Calculated by a predetermined estimation algorithm, and the control input is further calculated according to the calculated disturbance estimated value. Therefore, the steady disturbance acting on the variable cam phase mechanism and the modeling error in the cam phase control are also appropriately set. It is possible to compensate, and the cam phase can be controlled so that no steady deviation occurs. As a result, control stability and control accuracy can be significantly improved.

According to a ninth aspect of the present invention, in the control device 1B for the movable part driving mechanism according to any of the second to sixth aspects, the disturbance compensation value Rcyc_cin, the control input (SLD control input Rsld for cam phase control), and the cam phase. Model parameter identification means (ECU2, partial parameter identifier 307) for on-board identification of model parameters b1 and b2 of the model [Equation (40)] defining the relationship with Cain is further provided, and the control input calculation means The input is further calculated according to the identified model parameter.

According to the control device for the movable part drive mechanism, the model parameter of the model that defines the relationship between the disturbance compensation value, the control input, and the cam phase is identified on-board , and the control input is converted to the identified model parameter . Since the calculation is further performed, even when the dynamic characteristic of the variable cam phase mechanism changes, the variable cam phase mechanism can be controlled while quickly absorbing the influence of such change. As a result, control stability and control accuracy can be significantly improved.

  According to a tenth aspect of the present invention, in the control device 1, 1A, 1B for the movable part drive mechanism according to the first aspect, the movable part drive mechanism is a lift of at least one of the intake valve 4 and the exhaust valve 7 of the internal combustion engine 3. A variable valve lift mechanism 50 that changes the valve lift Liftin as the operation amount of the movable portion is included.

  According to the control device for the movable part drive mechanism, since the movable part drive mechanism includes the variable valve lift mechanism that changes the valve lift as the operation amount of the movable part, the control input calculated according to the disturbance compensation value is used. By controlling the variable valve lift mechanism, the effect of periodic disturbance on the variable valve lift mechanism can be compensated and suppressed more quickly than before, and the stability and control accuracy in the control of the variable valve lift mechanism can be reduced. Can be improved. Thereby, it is possible to avoid fluctuations in the lift of the intake valve and / or the exhaust valve due to the influence of the periodic disturbance, and it is possible to avoid fluctuations in the intake air amount and / or the internal EGR amount when the valve is opened. As a result, the generated torque of the internal combustion engine can be appropriately secured and a stable combustion state can be secured.

  According to an eleventh aspect of the present invention, in the control device 1, 1A, 1B of the movable part drive mechanism according to the tenth aspect, the disturbance compensation value selection means further includes a valve lift parameter (target valve lift Liftin_cmd) representing the valve lift. Accordingly, a disturbance compensation value (map value Rcyc_bs_lin of disturbance compensation value for valve lift control) is selected (step 9).

  In general, when the variable valve lift mechanism is provided in the internal combustion engine, when the valve lift is changed by the variable valve lift mechanism, the amplitude of the periodic disturbance applied to the variable valve lift mechanism also changes accordingly. On the other hand, according to this control device, the disturbance compensation value is further selected according to the valve lift parameter indicating the valve lift, and therefore the disturbance compensation value is used as the amplitude change of the periodic disturbance accompanying the change of the valve lift. Can be selected as a value that can be appropriately compensated. Thereby, the stability and control accuracy in the control of the variable valve lift mechanism can be further improved.

  According to a twelfth aspect of the present invention, in the control device 1, 1A, 1B for the movable part drive mechanism according to the tenth or eleventh aspect, the internal combustion engine 3 includes at least the intake camshaft 5 and the exhaust camshaft 8 of the internal combustion engine 3. A variable cam phase mechanism 70 that changes a cam phase Cain that is a phase with respect to one crankshaft 3d is provided, and the disturbance compensation value selection means further includes a disturbance compensation value (cam phase Cain) that represents a cam phase. A disturbance compensation value map value Rcyc_bs_lin) for valve lift control is selected (step 9).

  In general, when the variable cam phase mechanism is provided in the internal combustion engine, when the cam phase is changed by the variable cam phase mechanism, the phase of the periodic disturbance applied to the variable valve lift mechanism changes accordingly. On the other hand, according to this control device, the disturbance compensation value is further selected in accordance with the cam phase parameter representing the cam phase, so that the disturbance compensation value is changed to the phase change of the periodic disturbance accompanying the change of the cam phase. Can be selected as a value that can be appropriately compensated. Thereby, the stability and control accuracy in the control of the variable valve lift mechanism can be further improved.

  According to a thirteenth aspect of the present invention, in the control device 1, 1A, 1B for the movable part drive mechanism according to any one of the tenth to twelfth aspects, the control input calculating means includes a disturbance compensation value (disturbance compensation for valve lift control). Value map value Rcyc_bs_lin) is corrected in accordance with the rotational speed NE of the internal combustion engine 3 (steps 10 and 11), and control input (in accordance with the corrected disturbance compensation value (disturbance compensation value Rcyc_lin for valve lift control)) The valve lift control SLD input Rsld ′ and the valve lift control reference input Rsld_f ′) are calculated.

  Generally, when the rotational speed of the internal combustion engine changes, the frequency of the periodic disturbance applied to the variable valve lift mechanism also changes accordingly. On the other hand, according to this control device, the disturbance compensation value is corrected in accordance with the rotational speed of the internal combustion engine, so that the frequency change of the periodic disturbance accompanying the rotational speed change of the internal combustion engine is added to the corrected disturbance compensation value. Can be reflected. Further, since the control input is calculated according to the disturbance compensation value corrected as described above, the variable valve lift mechanism is controlled while appropriately compensating for the frequency change of the periodic disturbance accompanying the change in the rotational speed of the internal combustion engine. be able to.

  According to a fourteenth aspect of the present invention, in the control device 1, 1A, 1B for the movable part drive mechanism according to any one of the tenth to thirteenth aspects, the control input calculating means is configured such that the rotational speed NE of the internal combustion engine is a predetermined rotational speed NEREF2. In this case, the control input is calculated irrespective of the disturbance compensation value (Rcyc_lin = 0).

  In the control device according to claim 10, since the disturbance compensation value is selected at a selection timing corresponding to each rotation of the crankshaft of the internal combustion engine by a predetermined angle, when the rotation speed of the internal combustion engine becomes high, the disturbance compensation value is selected. Compensation value selection timing interval, that is, the selection cycle becomes extremely short, and when the control input is calculated using the disturbance compensation value selected in such a short selection cycle, the variable valve lift mechanism has low responsiveness. Thus, disturbance compensation cannot be performed properly, and controllability may be reduced. On the other hand, in the control device according to the fourteenth aspect, the control input is calculated regardless of the disturbance compensation value when the rotational speed of the internal combustion engine is equal to or higher than the predetermined rotational speed. By setting the value, it is possible to control the variable valve lift mechanism while avoiding a decrease in controllability in the high rotation range.

The invention according to claim 15 is the target valve lift setting for setting the target valve lift Liftin_cmd which is the target of the valve lift in the control device 1, 1A, 1B of the movable part drive mechanism according to any one of claims 10 to 14. Means (ECU2, target valve lift calculation units 111, 211, 311), and the control input calculation means uses a predetermined response designation control algorithm so that the valve lift Liftin converges to the target valve lift Liftin_cmd, A control input is calculated .

According to this control device for the movable part drive mechanism , the control input is calculated using a predetermined response designating control algorithm so that the valve lift converges to the target valve lift. Even when a large deviation occurs between the valve lifts, the valve lift can be quickly and accurately converged to the target valve lift while avoiding the occurrence of overshoot due to such deviations. As a result, control stability and control accuracy can be significantly improved.

  According to a sixteenth aspect of the present invention, there is provided a disturbance estimation value (valve for compensating for disturbance and modeling error in the variable valve lift mechanism 50 in the control device 1A for the movable part drive mechanism according to any one of the tenth to fourteenth aspects. The estimated disturbance c1 ′ for lift control is calculated by a predetermined estimation algorithm based on a model that defines the relationship between the estimated disturbance, the control input (SLD control input Rsld ′ for valve lift control), and the valve lift Liftin. A disturbance estimated value calculating means (ECU2, adaptive disturbance observer 216) is further provided, and the control input calculating means calculates the control input further according to the calculated disturbance estimated value.

  According to the control device for the movable part drive mechanism, the disturbance estimated value for compensating for disturbance and modeling error in the variable valve lift mechanism is based on a model that defines the relationship between the disturbance estimated value, the control input, and the valve lift. Calculated by a predetermined estimation algorithm, and the control input is further calculated according to the calculated disturbance estimated value. Therefore, the steady disturbance acting on the variable valve lift mechanism and the modeling error in the valve lift control are also appropriately It is possible to compensate, and it is possible to control the valve lift so that no steady deviation occurs. As a result, control stability and control accuracy can be significantly improved.

The invention according to claim 17 is the control device 1B for the movable part drive mechanism according to any one of claims 10 to 14, wherein the disturbance compensation value Rcyc_lin, the control input (SLD control input Rsld ′ for valve lift control) and the valve Model parameter identification means (ECU2, partial parameter identifier 317) for on-board identification of the model parameters b1 ′ and b2 ′ of the model defining the relationship with the lift Liftin is further provided, and the control input calculation means includes the control input, The calculation is further performed according to the identified model parameters b1 ′ and b2 ′.

According to the control device for the movable part drive mechanism, the model parameter of the model that defines the relationship between the disturbance compensation value, the control input, and the valve lift is identified on-board , and the control input is converted to the identified model parameter. Further, since the calculation is performed accordingly, even when the dynamic characteristic of the variable valve lift mechanism changes, the variable valve lift mechanism can be controlled while quickly absorbing the influence of such change. As a result, control stability and control accuracy can be significantly improved.

  According to an eighteenth aspect of the present invention, in the control device 1, 1A, 1B for the movable portion drive mechanism according to the first aspect, the movable portion drive mechanism uses the stroke of the piston 3b of the internal combustion engine 3 as an operation amount of the movable portion. It is characterized by including a variable compression ratio mechanism 80 that changes the compression ratio Cr of the internal combustion engine 3 by changing.

  In general, in the case of a variable compression ratio mechanism, if a periodic disturbance is applied, the compression ratio changes due to the influence of the change, and the compatibility between the compression ratio and the ignition timing is lowered, resulting in knocking. Or the combustion efficiency may be reduced. In contrast, according to this control apparatus, the influence of the periodic disturbance on the variable compression ratio mechanism is controlled by controlling the variable compression ratio mechanism with the control input calculated according to the disturbance compensation value. Since compensation and suppression can be performed quickly, changes in the compression ratio due to the influence of periodic disturbance can be avoided, and compatibility between the compression ratio and the ignition timing can be maintained in a good state. As a result, the occurrence of knocking and a decrease in combustion efficiency can be avoided, and a stable combustion state can be ensured.

  According to a nineteenth aspect of the present invention, in the control device 1, 1A, 1B of the movable part drive mechanism according to the eighteenth aspect, the disturbance compensation value selection means further includes a compression ratio parameter (target compression ratio Cr_cmd) representing a compression ratio. Accordingly, a disturbance compensation value (a map value Rcyc_bs_cr of a disturbance compensation value for compression ratio control) is selected (step 12).

  In general, when the variable compression ratio mechanism is provided in the internal combustion engine, when the compression ratio is changed by the variable compression ratio mechanism, the amplitude of the periodic disturbance applied to the variable compression ratio mechanism also changes accordingly. On the other hand, according to this control device, the disturbance compensation value is further selected in accordance with the compression ratio parameter representing the compression ratio. Therefore, the disturbance compensation value is changed as the amplitude change of the periodic disturbance accompanying the change of the compression ratio. Can be selected as a value that can be appropriately compensated. Thereby, the stability and control accuracy in the control of the variable compression ratio mechanism can be further improved.

  According to a twentieth aspect of the present invention, in the control device 1, 1A, 1B of the movable part drive mechanism according to the eighteenth or nineteenth aspect, the control input calculating means includes a disturbance compensation value (a map of a disturbance compensation value for compression ratio control). The value Rcyc_bs_cr) is corrected according to the rotational speed NE of the internal combustion engine 3 (steps 14 and 15), and the control input (compression ratio control) is performed according to the corrected disturbance compensation value (disturbance compensation value Rcyc_cr for compression ratio control). SLD control input Rsld ″ and reference input Rsld_f ″) for compression ratio control are calculated.

  Generally, when the rotational speed of the internal combustion engine changes, the frequency of the periodic disturbance applied to the variable compression ratio mechanism also changes accordingly. On the other hand, according to this control device, the disturbance compensation value is corrected in accordance with the rotational speed of the internal combustion engine, so that the frequency change of the periodic disturbance accompanying the rotational speed change of the internal combustion engine is added to the corrected disturbance compensation value. Can be reflected. Further, since the control input is calculated according to the disturbance compensation value corrected as described above, the variable compression ratio mechanism is controlled while appropriately compensating for the frequency change of the periodic disturbance accompanying the change in the rotational speed of the internal combustion engine. be able to.

  According to a twenty-first aspect of the present invention, in the control device 1, 1A, 1B of the movable part drive mechanism according to the eighteenth or nineteenth aspect, the control input calculating means sets the disturbance compensation value to a load parameter (the load parameter indicating the load of the internal combustion engine 3). The correction is performed according to the cam phase Cain and the valve lift Liftin (steps 13 and 15), and the control input is calculated according to the corrected disturbance compensation value (disturbance compensation value Rcyc_cr for compression ratio control). To do.

  Generally, when the load of the internal combustion engine changes, the amplitude of the periodic disturbance applied to the variable compression ratio mechanism also changes accordingly. On the other hand, according to this control device, the disturbance compensation value is corrected according to the load parameter representing the load of the internal combustion engine, so that the periodic disturbance accompanying the fluctuation of the load of the internal combustion engine is added to the corrected disturbance compensation value. It is possible to reflect the change in the amplitude of. Furthermore, since the control input is calculated according to the disturbance compensation value corrected in this way, the variable compression ratio mechanism is controlled while appropriately compensating for the change in the amplitude of the periodic disturbance accompanying the change in the load of the internal combustion engine. can do.

  According to a twenty-second aspect of the present invention, in the control device 1, 1A, 1B for the movable portion drive mechanism according to the twenty-first aspect, the internal combustion engine 3 is at least one of the intake camshaft 5 and the exhaust camshaft 8 of the internal combustion engine 3. The variable cam phase mechanism 70 which changes the cam phase Cain which is a phase with respect to the crankshaft 3d is provided, and a load parameter contains the cam phase parameter (cam phase Cain) showing a cam phase.

  In general, when the variable cam phase mechanism is provided in the internal combustion engine, when the cam phase is changed by the variable cam phase mechanism, the amplitude of the periodic disturbance applied to the variable compression ratio mechanism also changes accordingly. On the other hand, according to this control device, since the load parameter includes the cam phase parameter representing the cam phase, the disturbance compensation value is corrected according to the cam phase parameter. A change in the amplitude of the periodic disturbance accompanying a change in the cam phase of the engine can be reflected. As a result, the variable compression ratio mechanism can be controlled while appropriately compensating for the change in the amplitude of the periodic disturbance.

  According to a twenty-third aspect of the present invention, in the control device 1, 1A, 1B of the movable part drive mechanism according to the twenty-first or twenty-second aspect, the internal combustion engine 3 is at least one of the intake valve 4 and the exhaust valve 7 of the internal combustion engine 3. The variable valve lift mechanism 50 which changes the valve lift Liftin which is a lift is provided, and the load parameter includes a valve lift parameter (valve lift Liftin) representing the valve lift.

  In general, when a variable valve lift mechanism is provided in an internal combustion engine, when the valve lift is changed by the variable valve lift mechanism, the amplitude of a periodic disturbance applied to the variable compression ratio mechanism also changes accordingly. On the other hand, according to this control device, since the load parameter includes the valve lift parameter indicating the valve lift, the disturbance compensation value is corrected according to the valve lift parameter, so that the corrected disturbance compensation value is changed to the internal combustion compensation value. A change in the amplitude of the periodic disturbance accompanying the fluctuation of the valve lift of the engine can be reflected. As a result, the variable compression ratio mechanism can be controlled while appropriately compensating for the change in the amplitude of the periodic disturbance.

  According to a twenty-fourth aspect of the present invention, in the control device 1, 1A, 1B for the movable part drive mechanism according to any one of the twenty-second to twenty-third aspects, the control input calculating means is configured such that the rotational speed NE of the internal combustion engine is a predetermined rotational speed NEREF3. In the above case, the control input is calculated regardless of the disturbance compensation value (Rcyc_cr = 0).

  In the control device according to claim 18, since the disturbance compensation value is selected at a selection timing corresponding to each rotation of the crankshaft of the internal combustion engine by a predetermined angle, when the rotational speed of the internal combustion engine becomes high, the disturbance compensation value is selected. Compensation value selection timing interval, that is, the selection cycle becomes extremely short, and when the control input is calculated using the disturbance compensation value selected in such a short selection cycle, the variable compression ratio mechanism has low responsiveness. Thus, disturbance compensation cannot be performed properly, and controllability may be reduced. On the other hand, in the control device according to claim 24, when the rotational speed of the internal combustion engine is equal to or higher than the predetermined rotational speed, the control input is calculated regardless of the disturbance compensation value. By setting the value, the variable compression ratio mechanism can be controlled while avoiding a decrease in controllability in the high rotation range.

The invention according to claim 25 is the target compression ratio for setting the target compression ratio Cr_cmd which is the target of the compression ratio Cr in the control device 1, 1A, 1B of the movable part drive mechanism according to any of claims 18 to 24. Setting means (ECU2, target compression ratio calculation units 121, 221 and 321) are further provided, and the control input calculation means uses a predetermined response designation control algorithm so as to converge the compression ratio Cr to the target compression ratio Cr_cmd. The control input is calculated .

According to this control device for the movable part drive mechanism , the control input is calculated using a predetermined response designating control algorithm so that the compression ratio converges to the target compression ratio. Even if a large deviation occurs between the two, the compression ratio can be quickly and accurately converged to the target compression ratio while avoiding the occurrence of overshoot due to such deviation. As a result, control stability and control accuracy can be significantly improved.

  According to a twenty-sixth aspect of the present invention, in the control device 1A for the movable part driving mechanism according to any one of the eighteenth to twenty-fourth aspects, an estimated disturbance value (compression) for compensating for disturbances and modeling errors in the variable compression ratio mechanism 80. The disturbance estimation value c1 ″) for ratio control is obtained by a predetermined estimation algorithm based on a model that defines the relationship between the disturbance estimation value, the control input (SLD control input Rsld ″ for compression ratio control), and the compression ratio Cr. A disturbance estimated value calculating means (adaptive disturbance observer 226) for calculating is further provided, and the control input calculating means calculates the control input further according to the calculated disturbance estimated value.

  According to the control device for the movable part drive mechanism, the disturbance estimated value for compensating for disturbance and modeling error in the variable compression ratio mechanism is based on a model that defines the relationship between the disturbance estimated value, the control input, and the compression ratio. Calculated by a predetermined estimation algorithm, and the control input is further calculated according to the calculated disturbance estimated value, so that the steady disturbance acting on the variable compression ratio mechanism and the modeling error in the compression ratio control are also appropriately It is possible to compensate, and the compression ratio can be controlled so that no steady-state deviation occurs. As a result, control stability and control accuracy can be significantly improved.

According to a twenty-seventh aspect of the present invention, in the control device 1B for the movable part driving mechanism according to any of the eighteenth to twenty-fourth aspects, a disturbance compensation value Rcyc_cr and a control input (SLD control input Rsld ″ for compression ratio control) Model parameter identification means (partial parameter identifier 327) for on-board identification of the model parameters b1 ″ and b2 ″ of the model defining the relationship with the compression ratio Cr is further provided, and the control input calculation means receives the control input. Further, the calculation is further performed according to the identified model parameters b1 ″ and b2 ″.

According to the control device for this movable part drive mechanism, the model parameter of the model that defines the relationship between the disturbance compensation value, the control input, and the compression ratio is identified on-board , and the control input is converted to the identified model parameter. Further, since the calculation is performed accordingly, even when the dynamic characteristics of the variable compression ratio mechanism change, the variable compression ratio mechanism can be controlled while quickly absorbing the influence of such a change. As a result, control stability and control accuracy can be significantly improved.

It is a mimetic diagram showing a schematic structure of an internal-combustion engine to which a control device of a movable part drive mechanism concerning a 1st embodiment of the present invention is applied. It is a block diagram which shows schematic structure of the control apparatus of a movable part drive mechanism. It is sectional drawing which shows schematic structure of the variable type intake valve mechanism and exhaust valve mechanism of an internal combustion engine. It is sectional drawing which shows schematic structure of the variable valve lift mechanism of a variable intake valve mechanism. (A) It is a figure which shows the state which has the short arm of a lift actuator in the maximum lift position, and (b) the state in the minimum lift position. (A) It is a figure which shows the valve opening state of the intake valve when the lower link of the variable valve lift mechanism is at the maximum lift position, and (b) the valve opening state of the intake valve when it is at the minimum lift position. It is a figure which respectively shows the valve lift curve (solid line) of the intake valve when the lower link of the variable valve lift mechanism is at the maximum lift position, and the valve lift curve (two-dot chain line) when at the minimum lift position. It is a figure which shows typically schematic structure of a variable cam phase mechanism. By the variable cam phase mechanism, the valve lift curve (solid line) of the intake valve 4 when the cam phase is set to the most retarded value and the intake valve 4 when the cam phase is set to the most advanced value. It is a figure which shows a valve lift curve (two-dot chain line), respectively. (A) The figure which shows typically the whole structure of the variable compression ratio mechanism when the compression ratio is set to the low compression ratio, (b) The variable compression ratio when the compression ratio is set to the high compression ratio It is a figure which shows the structure of the control shaft and compression ratio actuator vicinity in a mechanism. It is a block diagram which shows schematic structure of a cam phase controller. It is operation | movement explanatory drawing when the (a) intake cam is driving the intake valve in the valve opening direction, and (b) the intake valve is driving in the valve closing direction for demonstrating a periodic disturbance. It is a timing chart which shows the influence of the periodic disturbance in cam phase control. It is a valve lift curve for comparing the presence or absence of a variable cam phase mechanism when the valve lift is a high lift. It is a valve lift curve for comparing the presence or absence of a variable cam phase mechanism when the valve lift is a low lift. It is a figure which shows an example of the map value when the valve lift is the maximum value in the disturbance compensation value map for cam phase control for one cylinder. It is a figure which shows an example of the map value when the valve lift is the minimum value in the disturbance compensation value map for cam phase control for one cylinder. It is a compensation element of 1st Embodiment, and is a figure which shows an example of the map value when the valve lift is the maximum value in the disturbance compensation value map for cam phase control. It is a compensation element of 1st Embodiment, and is a figure which shows an example of the map value in case the valve lift is the minimum value in the disturbance compensation value map for cam phase control. It is a figure which shows the control algorithm of a 2-degree-of-freedom sliding mode controller, and the model used for the derivation | leading-out. It is a figure which shows the arithmetic expression of an addition element, and the control algorithm of a DSM controller. It is a block diagram which shows schematic structure of a valve lift controller. It is a figure which shows an example of the map value when the target valve lift is the maximum value in the disturbance compensation value map for valve lift control. It is a figure which shows an example of the map value in case the target valve lift is the minimum value in the disturbance compensation value map for valve lift control. It is a block diagram which shows schematic structure of a compression ratio controller. It is a figure which shows an example of the disturbance compensation value map used for the search of the map value of the disturbance compensation value for compression ratio control. It is a flowchart which shows the calculation process of the disturbance compensation value for cam phase control, valve lift control, and compression ratio control. It is a figure which shows an example of the table used for calculation of the correction coefficient for cam phase control. It is a figure which shows an example of the table used for calculation of the correction coefficient for valve lift control. It is a figure which shows an example of the map used for calculation of the 1st correction coefficient for compression ratio control. It is a figure which shows an example of the table used for calculation of the 2nd correction coefficient for compression ratio control. It is a flowchart which shows the calculation process of a phase control input, a lift control input, and a compression ratio control input. It is a figure which shows an example of the map used for calculation of a target cam phase. It is a figure which shows an example of the map used for calculation of a target valve lift. It is a figure which shows an example of the map used for calculation of a target compression ratio. It is the figure which showed an example of the simulation result of the cam phase control by the control apparatus which concerns on 1st Embodiment about one cylinder. It is a figure which shows the modification of the disturbance compensation value map used for calculation of the map value of the disturbance compensation value for cam phase control. It is a block diagram which shows schematic structure of the cam phase controller of 2nd Embodiment. It is a block diagram which shows schematic structure of the valve lift controller of 2nd Embodiment. It is a block diagram which shows schematic structure of the compression ratio controller of 2nd Embodiment. It is a figure which shows the calculation algorithm of the disturbance estimated value in the adaptive disturbance observer of the cam phase controller of 2nd Embodiment, and the model used for the derivation | leading-out. It is a figure which shows the control algorithm of the 2 freedom degree sliding mode controller of the cam phase controller of 2nd Embodiment. It is a figure which shows the control algorithm of the DSM controller of the cam phase controller of 2nd Embodiment. It is a block diagram which shows schematic structure of the cam phase controller of 3rd Embodiment. It is a block diagram which shows schematic structure of the valve lift controller of 3rd Embodiment. It is a block diagram which shows schematic structure of the compression ratio controller of 3rd Embodiment. It is a figure which shows the model used for the identification algorithm of the partial parameter identifier of the cam phase controller of 3rd Embodiment, and its derivation | leading-out. It is a figure which shows the control algorithm of the 2-degree-of-freedom sliding mode controller of the cam phase controller of 3rd Embodiment. It is a figure which shows the control algorithm of the DSM controller of the cam phase controller of 3rd Embodiment.

  Hereinafter, a control device according to a first embodiment of the present invention will be described with reference to the drawings. As shown in FIG. 2, the control device 1 includes an ECU 2. As will be described later, the ECU 2 controls the valve lift control and cam according to the operating state of the internal combustion engine (hereinafter referred to as “engine”) 3. Control processing such as phase control and compression ratio control is executed.

  As shown in FIGS. 1 and 3, the engine 3 is an in-line four-cylinder gasoline engine having four sets of cylinders 3a and pistons 3b (only one set is shown), and is mounted on a vehicle (not shown). The engine 3 is provided for each cylinder 3a, and opens and closes an intake valve 4 and an exhaust valve 7 for opening and closing an intake port and an exhaust port, an intake camshaft 5 and an intake cam 6 for driving the intake valve 4, and an intake valve 4, respectively. A variable intake valve mechanism 40 for driving, an exhaust camshaft 8 and an exhaust cam 9 for driving the exhaust valve 7, an exhaust valve mechanism 30 for opening and closing the exhaust valve 7, a variable compression ratio mechanism 80, and the like are provided. Yes.

  The intake valve 4 has a stem 4a slidably fitted to a guide 4b, and the guide 4b is fixed to the cylinder head 3c. Further, as shown in FIG. 4, the intake valve 4 is provided with upper and lower spring seats 4c, 4d and a valve spring 4e provided therebetween, and is attached in the valve closing direction by the valve spring 4e. It is energized.

  Further, each of the intake camshaft 5 and the exhaust camshaft 8 is rotatably attached to the cylinder head 3c via a holder (not shown). An intake sprocket (not shown) is coaxially disposed on one end of the intake camshaft 5 and is rotatably provided. The intake sprocket is connected to the crankshaft 3d via a timing belt (not shown), and is connected to the intake camshaft 5 via a variable cam phase mechanism 70 described later. With the above configuration, the intake camshaft 5 rotates once every time the crankshaft 3d rotates twice. In addition, the intake cam 6 is provided for each cylinder 3a on the intake camshaft 5 so as to rotate integrally therewith.

  Further, the variable intake valve mechanism 40 is configured to open and close the intake valve 4 of each cylinder 3a as the intake camshaft 5 rotates, and to change the lift and valve timing of the intake valve 4 steplessly. Details thereof will be described later. In the present embodiment, “the lift of the intake valve 4 (hereinafter referred to as“ valve lift ”)” represents the maximum lift of the intake valve 4.

  On the other hand, the exhaust valve 7 has a stem 7a slidably fitted to a guide 7b, and the guide 7b is fixed to the cylinder head 3c. Further, the exhaust valve 7 includes upper and lower spring seats 7c and 7d and a valve spring 7e provided therebetween, and is urged in the valve closing direction by the valve spring 7e.

  The exhaust camshaft 8 includes an exhaust sprocket (not shown) integrated with the exhaust camshaft 8 and is connected to the crankshaft 3d via the exhaust sprocket and a timing belt (not shown). One rotation for every rotation. Further, the exhaust cam 9 is provided for each cylinder 3a on the exhaust camshaft 8 so as to rotate integrally therewith.

  Further, the exhaust valve mechanism 30 includes a rocker arm 31. The rocker arm 31 rotates with the rotation of the exhaust cam 9, thereby opening and closing the exhaust valve 7 against the urging force of the valve spring 7e. To drive.

  On the other hand, the engine 3 is provided with a crank angle sensor 20. The crank angle sensor 20 includes a magnet rotor and an MRE pickup, and outputs a CRK signal and a TDC signal, which are pulse signals, to the ECU 2 as the crankshaft 3d rotates. One pulse of this CRK signal is output every 10 ° of crank angle, and the ECU 2 calculates the engine speed (hereinafter referred to as “engine speed”) NE of the engine 3 based on this CRK signal. The TDC signal is a signal indicating that the piston 3b of each cylinder 3a is at a predetermined crank angle position slightly before the TDC position of the intake stroke, and one pulse is output for each predetermined crank angle.

  The intake pipe 10 of the engine 3 is provided with an airflow sensor 21, a throttle valve 11, an intake pipe absolute pressure sensor 22, a fuel injection valve 12, and the like in order from the upstream side.

  The air flow sensor 21 is constituted by a hot-wire air flow meter, and outputs a detection signal representing an intake air amount (hereinafter referred to as “TH passage intake air amount”) GTH passing through the throttle valve 11 to the ECU 2. The throttle valve 11 is rotatably provided in the middle of the intake pipe 10 and changes the TH passing intake air amount GTH by changing the opening degree associated with the rotation. Further, the throttle valve 11 is held in a fully opened state by the ECU 2 via an actuator (not shown) during normal operation, and the throttle valve 11 is negatively applied to the master back (not shown) when the variable intake valve mechanism 40 fails. When the pressure is supplied, the opening degree is controlled.

  A portion of the intake pipe 10 downstream of the throttle valve 11 is a surge tank 10a, and an intake pipe absolute pressure sensor 22 is provided in the surge tank 10a. The intake pipe absolute pressure sensor 22 is composed of, for example, a semiconductor pressure sensor, and outputs a detection signal representing the absolute pressure (hereinafter referred to as “intake pipe absolute pressure”) PBA in the intake pipe 10 to the ECU 2.

Further, the fuel injection valve 12 is driven by a drive signal from the ECU 2 to inject fuel into the intake pipe 10. A spark plug 13 (see FIG. 2) is attached to the cylinder head 3c of the engine 3. The spark plug 13 discharges by a drive signal corresponding to the ignition timing is applied from the ECU 2, to burn the mixture in the combustion chamber.

  Next, the variable intake valve mechanism 40 described above will be described. As shown in FIG. 4, the variable intake valve mechanism 40 includes an intake camshaft 5, an intake cam 6, a variable valve lift mechanism 50, a variable cam phase mechanism 70, and the like.

  The variable valve lift mechanism 50 (movable part drive mechanism) drives the intake valve 4 (movable part) to open and close as the intake camshaft 5 rotates, and sets the valve lift Liftin to a predetermined maximum value Liftinmax and minimum value Liftinmin. The four-link type rocker arm mechanism 51 provided for each cylinder 3a, and a lift actuator 60 (see FIG. 5) for simultaneously driving these rocker arm mechanisms 51 are provided. Yes.

  Each rocker arm mechanism 51 includes a rocker arm 52 and upper and lower links 53 and 54. One end portion of the upper link 53 is rotatably attached to the upper end portion of the rocker arm 52 via the upper pin 55, and the other end portion is rotatably attached to the rocker arm shaft 56. The rocker arm shaft 56 is attached to the cylinder head 3c via a holder (not shown).

  A roller 57 is rotatably provided on the upper pin 55 of the rocker arm 52. The roller 57 is in contact with the cam surface of the intake cam 6 and rolls on the intake cam 6 while being guided by the cam surface when the intake cam 6 rotates. As a result, the rocker arm 52 is driven in the vertical direction, and the upper link 53 rotates about the rocker arm shaft 56.

  Further, an adjustment bolt 52a is attached to the end of the rocker arm 52 on the intake valve 4 side. When the rocker arm 52 moves up and down with the rotation of the intake cam 6, the adjust bolt 52a drives the stem 4a up and down to open and close the intake valve 4 against the urging force of the valve spring 4e.

  One end of the lower link 54 is pivotally attached to the lower end of the rocker arm 52 via a lower pin 58, and a connecting pin 59 is pivotally attached to the other end of the lower link 54. It is attached. The lower link 54 is connected to a short arm 65 (to be described later) of the lift actuator 60 via the connecting pin 59.

  On the other hand, the lift actuator 60 includes a motor 61, a nut 62, a link 63, a long arm 64, a short arm 65, and the like, as shown in FIG. The motor 61 is connected to the ECU 2 and is disposed outside the head cover 3 g of the engine 3. The rotation shaft of the motor 61 is a screw shaft 61a on which a male screw is formed, and a nut 62 is screwed onto the screw shaft 61a. The nut 62 is connected to the long arm 64 via the link 63. One end of the link 63 is rotatably attached to the nut 62 via a pin 63a, and the other end is rotatably attached to one end of the long arm 64 via a pin 63b. .

  The other end of the long arm 64 is attached to one end of the short arm 65 via a rotation shaft 66. The rotation shaft 66 is formed in a circular cross section, penetrates the head cover 3g of the engine 3, and is rotatably supported by the rotation shaft 66. As the rotation shaft 66 rotates, the long arm 64 and the short arm 65 rotate integrally therewith.

  Further, the above-described connecting pin 59 is rotatably attached to the other end of the short arm 65, whereby the short arm 65 is connected to the lower link 54 via the connecting pin 59. .

  Next, the operation of the variable valve lift mechanism 50 configured as described above will be described. In this variable valve lift mechanism 50, when a later-described lift control input Uliftin from the ECU 2 is input to the lift actuator 60, the screw shaft 61a rotates and the long arm 64 and the short arm 65 are moved by the movement of the nut 62 associated therewith. While rotating about the rotation shaft 66, the lower link 54 of the rocker arm mechanism 51 rotates about the lower pin 58 as the short arm 65 rotates. That is, the lower link 54 is driven by the lift actuator 60.

  At that time, under the control of the ECU 2, the rotation range of the short arm 65 is regulated between the maximum lift position shown in FIG. 5A and the minimum lift position shown in FIG. The rotation range 54 is also regulated between the maximum lift position indicated by a solid line in FIG. 4 and the minimum lift position indicated by a two-dot chain line in FIG.

When the lower link 54 is in the maximum lift position, in the four-bar link constituted by the rocker arm shaft 56, the upper and lower pins 55, 58 and the connecting pin 59, the distance between the centers of the upper pin 55 and the lower pin 58 is the rocker arm shaft. 56 and the connecting pin 59 is configured to be longer than the distance between the centers of, thereby, as shown in FIG. 6 (a), when the intake cam 6 rotates, the contact point between this and the roller 57 The moving amount of the adjusting bolt 52a is larger than the moving amount.

On the other hand, when the lower link 54 is at the minimum lift position, the distance between the centers of the upper pin 55 and the lower pin 58 is shorter than the distance between the centers of the rocker arm shaft 56 and the connecting pin 59 in the four-bar link. Accordingly, as shown in FIG. 6B, when the intake cam 6 rotates, the moving amount of the adjusting bolt 52a is smaller than the moving amount of the contact point between the intake cam 6 and the roller 57. Become.

  For the above reasons, the intake valve 4 opens with a larger valve lift Liftin when the lower link 54 is at the maximum lift position than when it is at the minimum lift position. Specifically, during the rotation of the intake cam 6, when the lower link 54 is at the maximum lift position, the intake valve 4 is opened according to the valve lift curve shown by the solid line in FIG. 7, and the valve lift Liftin has its maximum value. Liftinmax is shown. On the other hand, when the lower link 54 is at the minimum lift position, the valve is opened according to the valve lift curve shown by the two-dot chain line in FIG. 7, and the valve lift Liftin indicates the minimum value Liftinmin.

  Accordingly, in the variable valve lift mechanism 50, the valve lift Liftin is set to the maximum value Liftinmax and the minimum value Liftinmin by rotating the lower link 54 between the maximum lift position and the minimum lift position via the actuator 60. Can be changed steplessly between.

  The engine 3 is provided with a rotation angle sensor 23 (see FIG. 2). The rotation angle sensor 23 detects the rotation angle of the rotation shaft 66, that is, the short arm 65, and detects the rotation angle. A signal is output to the ECU 2. The ECU 2 calculates the valve lift Liftin based on the detection signal of the rotation angle sensor 23.

  Next, the aforementioned variable cam phase mechanism 70 (movable part drive mechanism) will be described. This variable cam phase mechanism 70 changes the relative phase (hereinafter referred to as “cam phase”) Cain of the intake camshaft 5 as a movable portion with respect to the crankshaft 3d to the advance side or the retard side steplessly. Yes, provided at the end of the intake camshaft 5 on the intake sprocket side. As shown in FIG. 8, the variable cam phase mechanism 70 includes a housing 71, a three-blade vane 72, a hydraulic pump 73, an electromagnetic valve mechanism 74, and the like.

  The housing 71 is formed integrally with an intake sprocket on the intake camshaft 5 and includes three partition walls 71a formed at equal intervals. The vane 72 is coaxially attached to the end of the intake camshaft 5 on the intake sprocket side, extends radially outward from the intake camshaft 5, and is rotatably accommodated in the housing 71. In the housing 71, three advance chambers 75 and three retard chambers 76 are formed between the partition wall 71 a and the vane 72.

  The hydraulic pump 73 is a mechanical type connected to the crankshaft 3d. When the crankshaft 3d rotates, along with this, the lubricating oil stored in the oil pan 3e of the engine 3 passes through the oil passage 77c. And is supplied to the electromagnetic valve mechanism 74 via the oil passage 77c in a state where the pressure is increased.

  The electromagnetic valve mechanism 74 is a combination of a spool valve mechanism 74a and a solenoid 74b, and is connected to the advance chamber 75 and the retard chamber 76 via an advance oil passage 77a and a retard oil passage 77b, respectively. At the same time, the hydraulic pressure supplied from the hydraulic pump 73 is output to the advance chamber 75 and the retard chamber 76 as the advance hydraulic pressure Pad and the retard hydraulic pressure Prt, respectively. The solenoid 74b of the electromagnetic valve mechanism 74 is electrically connected to the ECU 2. When a phase control input Ucain (described later) is input from the ECU 2, the spool valve body of the spool valve mechanism 74a is made to respond to the phase control input Ucain. Thus, both the advance hydraulic pressure Pad and the retard hydraulic pressure Prt are changed by moving within a predetermined movement range.

  In the variable cam phase mechanism 70 described above, during the operation of the hydraulic pump 73, the electromagnetic valve mechanism 74 operates in accordance with a phase control input Ucain described later, whereby the advance hydraulic pressure Pad is transferred to the advance chamber 75 and the retard hydraulic pressure Prt. Are respectively supplied to the retard chamber 76, whereby the relative phase between the vane 72 and the housing 71 is changed to the advance side or the retard side. As a result, the aforementioned cam phase Cain is continuously between the most retarded angle value Cainrt (for example, a value corresponding to a cam angle of 0 °) and the most advanced angle value Cainad (for example, a value corresponding to a cam angle of 55 °). Thus, the valve timing of the intake valve 4 is changed steplessly between the most retarded timing shown by the solid line in FIG. 9 and the most advanced timing shown by the two-dot chain line in FIG.

  The variable cam phase mechanism 70 is provided with a lock mechanism (not shown), and when the hydraulic pressure supplied from the hydraulic pump 73 is low, the operation of the variable cam phase mechanism 70 is locked. That is, change of the cam phase Cain by the variable cam phase mechanism 70 is prohibited, and the cam phase Cain is locked to a value suitable for idle operation and engine start.

  As described above, in the variable intake valve mechanism 40 of the present embodiment, the variable valve lift mechanism 50 changes the valve lift Liftin continuously, and the variable cam phase mechanism 70 causes the cam phase Cain, that is, the intake valve. The valve timing 4 is changed steplessly between the most retarded timing and the most advanced timing described above. Further, as will be described later, the ECU 2 controls the valve lift Liftin and the cam phase Cain via the variable valve lift mechanism 50 and the variable cam phase mechanism 70, respectively.

  On the other hand, a cam angle sensor 24 (see FIG. 2) is provided at the end of the intake camshaft 5 opposite to the variable cam phase mechanism 70. The cam angle sensor 24 is composed of, for example, a magnet rotor and an MRE pickup, and outputs a CAM signal, which is a pulse signal, to the ECU 2 every predetermined cam angle (for example, 1 °) as the intake camshaft 5 rotates. . The ECU 2 calculates the cam phase Cain based on this CAM signal and the above-described CRK signal.

  Next, the aforementioned variable compression ratio mechanism 80 (movable part drive mechanism) will be described with reference to FIG. The variable compression ratio mechanism 80 changes the compression ratio Cr steplessly between a predetermined maximum value Crmax and a minimum value Crmin by changing the top dead center position of the piston 3b as a movable part, that is, the stroke of the piston 3b. A composite link mechanism 81 connected between the piston 3b and the crankshaft 3d, a control shaft 85 for controlling the movement of the composite link mechanism 81, and a compression ratio for driving the control shaft 85. It comprises an actuator 87 and the like.

  The composite link mechanism 81 includes an upper link 82, a lower link 83, a control link 84, and the like. The upper link 82 corresponds to a so-called connecting rod, and its upper end is rotatably connected to the piston 3b via the piston pin 3f, and its lower end is connected to one end of the lower link 83 via the pin 83a. It is pivotally connected.

  The lower link 83 has a triangular shape, and two ends other than the end connected to the upper link 82 are connected to the crankshaft 3d via the crankpin 83b and the control link 84 via the control pin 83c. One end is pivotally connected. With the above configuration, the reciprocating motion of the piston 3b is transmitted to the crankshaft 3d via the composite link mechanism 81 and converted into the rotational motion of the crankshaft 3d.

  Similarly to the crankshaft 3d, the control shaft 85 extends in the depth direction in the figure, and a rotation shaft portion 85a that is rotatably supported by the cylinder block, an eccentric shaft portion 85b integrated therewith, and An arm 86 is provided. A lower end portion of the control link 84 is rotatably connected to the eccentric shaft portion 85b. The distal end portion of the arm 86 is a fork portion 86a, and the distal end portion of the drive shaft 87b of the compression ratio actuator 87 is rotatably connected to the fork portion 86a.

  The compression ratio actuator 87 is a combination of a motor and a speed reduction mechanism (both not shown), and includes a casing 87a incorporating these, a drive shaft 87b that can move in the direction of protruding from the casing 87a, and the like. Yes. In the compression ratio actuator 87, when the motor is driven in the forward / reverse rotation direction by a compression ratio control input Ucr (described later) from the ECU 2, the drive shaft 87b is positioned at the low compression ratio position that protrudes most from the casing 87a (FIG. ) And the high compression ratio position (the position shown in FIG. 10B) that is most retracted to the casing 87a side.

  With the above-described configuration, in the variable compression ratio mechanism 80, when the drive shaft 87b of the actuator 87 moves from the low compression ratio position to the high compression ratio position, the control shaft 85 is moved via the arm 86 to the rotation shaft portion 85a. Is driven to rotate counterclockwise in the figure, and accordingly, the eccentric shaft portion 85b moves downward. Accordingly, as the entire control link 84 is pushed down, the lower link 83 rotates about the crank pin 83b in the clockwise direction in the drawing, and the upper link 82 rotates counterclockwise in the drawing about the piston pin 3f. Rotate around. As a result, the piston pin 3f, the upper pin 83a, and the crank pin 83b come closer to a straight line than at the low compression ratio position, so that the piston pin 3f and the crank pin 83b when the piston 3b reaches the top dead center The compression distance Cr increases as the connecting linear distance increases (that is, the stroke of the piston 3b increases) and the volume of the combustion chamber decreases.

  On the other hand, contrary to the above, when the drive shaft 87b of the actuator 87 moves from the high compression ratio position to the low compression ratio position, the rotation shaft portion 85a rotates in the clockwise direction in the drawing, and accordingly, eccentricity occurs. As the shaft portion 85b moves upward, the entire control link 84 is pushed up. As a result, the lower link 83 rotates counterclockwise and the upper link 82 rotates clockwise by an operation opposite to the above. As a result, the linear distance connecting the piston pin 3f and the crank pin 83b when the piston 3b reaches top dead center is shortened (that is, the stroke of the piston 3b is shortened), and the volume of the combustion chamber is increased. The ratio Cr is lowered. As described above, in the variable compression ratio mechanism 80, the compression ratio Cr is changed steplessly between the predetermined maximum value Crmax and the minimum value Crmin described above by changing the rotation angle of the control shaft 85. The

  Further, the engine 3 is provided with a control angle sensor 25 in the vicinity of the control shaft 85 (see FIG. 2), and this control angle sensor 25 sends a detection signal indicating the rotation angle of the control shaft 85 to the ECU 2. Output. The ECU 2 calculates the compression ratio Cr based on the detection signal of the control angle sensor 25.

  Further, as shown in FIG. 2, an accelerator opening sensor 26 and an ignition switch (hereinafter referred to as “IG · SW”) 27 are connected to the ECU 2. The accelerator opening sensor 26 outputs to the ECU 2 a detection signal indicating the depression amount (hereinafter referred to as “accelerator opening”) AP of an accelerator pedal (not shown) of the vehicle. The IG / SW 27 is turned ON / OFF by operating an ignition key (not shown), and outputs a signal representing the ON / OFF state to the ECU 2.

  The ECU 2 includes a microcomputer including a CPU 2a, a RAM 2b, a ROM 2c (disturbance compensation value storage means), an I / O interface (not shown), and the like. The operating state of the engine 3 is determined according to the ON / OFF signal of the SW 27, and various controls are executed. Specifically, as described later, the ECU 2 controls the cam phase Cain and the valve lift Liftin via the variable cam phase mechanism 70 and the variable valve lift mechanism 50, and also via the variable compression ratio mechanism 80. The compression ratio Cr is controlled. Further, the ignition timing of the spark plug 13 is controlled according to the operating state.

  In this embodiment, the ECU 2 constitutes a disturbance compensation value storage unit, a disturbance compensation value selection unit, a control input calculation unit, a target cam phase setting unit, a target valve lift setting unit, and a target compression ratio setting unit. In this embodiment, the cam phase Cain corresponds to the operation timing of the movable part, the cam phase parameter, and the load parameter, and the valve lift Liftin corresponds to the operation amount of the movable part, the valve lift parameter, and the load parameter.

  Next, the control apparatus 1 of this embodiment is demonstrated. The control device 1 includes a cam phase controller 100 (see FIG. 11), a valve lift controller 110 (see FIG. 22), and a compression ratio controller 120 (see FIG. 25). It is comprised by ECU2. First, the cam phase controller 100 will be described. As shown in FIG. 11, the cam phase controller 100 includes a target cam phase calculation unit 101, a compensation element 102, a two-degree-of-freedom sliding mode controller (hereinafter “two-degree-of-freedom SLD controller”). 103), an addition element 104, and a DSM controller 105.

  In the cam phase controller 100, as described below, the phase control input Ucain is calculated, and the phase control input Ucain is input to the variable cam phase mechanism 70, whereby the cam phase Cain becomes the target cam phase Cain_cmd. It is controlled to become.

  First, in the target cam phase calculation unit 101 (target cam phase setting means), a target cam phase Cain_cmd (cam phase parameter) is set on a map (see FIG. 33) described later according to the engine speed NE and the accelerator pedal opening AP. Calculated by searching.

  Further, in the compensation element 102 (disturbance compensation value storage means, disturbance compensation value selection means), as described later, cam phase control is performed in accordance with the target cam phase Cain_cmd calculated by the target cam phase calculation unit 101 and the like. A disturbance compensation value Rcyc_cin is calculated.

  Further, in the two-degree-of-freedom SLD controller 103 (control input calculation means), an SLD control input Rsld for cam phase control is calculated by a control algorithm described later according to the target cam phase Cain_cmd and the cam phase Cain.

  On the other hand, in the addition element 104 (control input calculation means), the disturbance compensation value Rcyc_cin for cam phase control calculated by the compensation element 102 and the SLD control input Rsld for cam phase control calculated by the two-degree-of-freedom SLD controller 103. Is calculated as a reference input Rsld_f (control input) for cam phase control. Further, the DSM controller 105 calculates a phase control input Ucain by a control algorithm described later in accordance with the cam phase control reference input Rsld_f.

  Next, the compensation element 102 described above will be described. In this compensation element 102, as described below, a disturbance compensation value Rcyc_cin for cam phase control is calculated according to the target cam phase Cain_cmd, the count value C_crk of the crank angle counter, the valve lift Liftin, and the engine speed NE. The The crank angle counter is an up counter for counting the crank angle, and the count value C_crk is incremented by 10 in synchronization with the generation of the CRK signal and reaches the value 720, as will be described later. Is reset to 0.

  This disturbance compensation value Rcyc_cin for controlling the cam phase is used to compensate for periodic disturbances that are expected to occur periodically with the rotation of the intake camshaft 5, that is, the rotation of the intake cam 6 during operation of the engine 3. Is. Hereinafter, a periodic disturbance and a method of calculating the disturbance compensation value Rcyc_cin for compensating for the periodic disturbance will be described. First, in order to facilitate understanding, the case of one cylinder 3a (in other words, the case of a single cylinder engine) will be described as an example with reference to FIGS. As shown in FIG. 12A, when the intake cam 6 rotates in the direction of the arrow Y1 in the drawing and drives the intake valve 4 in the valve opening direction, the intake cam 6 is the valve of the intake valve 4. Due to the reaction force of the spring 4e, a disturbance acting as a rotational moment in the direction of the arrow Y2 in the figure is received.

  On the other hand, as shown in FIG. 12B, when the intake cam 6 drives the intake valve 4 in the valve closing direction, the intake cam 6 is caused by the urging force of the valve spring 4e of the intake valve 4. , A disturbance acting as a rotational moment in the direction of arrow Y3 in the figure is received. The disturbance as described above is periodically generated as the intake camshaft 5 rotates, and the amplitude thereof is also periodically changed.

  Here, when feedback control is executed so that the cam phase Cain converges to the target cam phase Cain_cmd, when the periodic disturbance as described above is received, the target cam phase Cain_cmd is constant as shown in FIG. The cam phase Cain is shifted to the retard side while the intake valve 4 is driven to the valve opening side by the intake cam 6 and is advanced while the cam phase Cain is driven to the valve closing side. Shifts to the corner

  When such a cam phase Cain shift occurs, the valve timing of the intake valve 4 changes compared to the case where the variable cam phase mechanism 70 is not provided. Specifically, as shown in FIGS. 14 and 15, the valve lift curve of the intake valve 4 is obtained when the engine 3 includes a variable cam phase mechanism 70 (in the case of a curve indicated by a solid line in the figure). Is not provided (curve indicated by a broken line in the figure), the opening time of the intake valve 4 is shortened. As a result, the amount of intake air changes, and the generated torque of the engine 3 fluctuates. In addition, the combustion state may become unstable.

  In order to avoid this, for example, it is conceivable to change the cam profile of the intake cam 6 in advance. However, as apparent from comparison between the valve lift curves shown in FIGS. 14 and 15, when the engine 3 includes the variable valve lift mechanism 50, the valve lift Liftin is controlled to a predetermined high lift side value. When the valve lift Liftin is controlled to a predetermined low lift side value (when the valve lift curve shown in FIG. 15). The degree of timing change will be different from each other. For this reason, when the engine 3 includes both the variable cam phase mechanism 70 and the variable valve lift mechanism 50 as in this embodiment, the influence of the periodic disturbance can be reduced by changing the cam profile of the intake cam 6. It is difficult to avoid.

  In this embodiment, in order to avoid the influence when the periodic disturbance as described above is applied to the variable cam phase mechanism 70, the value of the periodic disturbance applied to the variable cam phase mechanism 70 is predicted, A value corresponding to a value obtained by inverting the sign of the predicted value is calculated as a disturbance compensation value Rcyc_cin for cam phase control. Specifically, the disturbance compensation value Rcyc_cin for cam phase control calculates a map value Rcyc_bs_cin by searching a disturbance compensation value map according to the valve lift Liftin, the count value C_crk of the crank angle counter, and the target cam phase Cain_cmd. The map value Rcyc_bs_cin is calculated by correcting it according to the engine speed NE.

  As the disturbance compensation value map, a map value Rcyc_bs_cin for Cain_cmd = Cainrt & Liftin = Liftinmax shown by a solid line in FIG. 16, a map value Rcyc_bs_cin for Cain_cmd = Cainrt & Liftin = Liftinmin shown by a solid line in FIG. A plurality of map values Rcyc_bs_cin (not shown) set in correspondence with a plurality of stages of Liftin values for interpolation calculation when the valve lift Liftin is between the maximum value Liftinmax and the minimum value Liftinmin. Use what you have.

  When searching for the above disturbance compensation value map, if the target cam Cain_cmd is a value on the advance side of the most retarded angle value Cainrt, the periodic disturbance occurrence period is shifted to the advance side (left side in the figure). The disturbance compensation value also needs to be corrected accordingly, for example, as indicated by a two-dot chain line in FIGS. Therefore, in the search for the disturbance compensation value map of the present embodiment, the count value C_crk of the crank angle counter is corrected in consideration of the advance angle degree of the target cam Cain_cmd with respect to the most retarded angle value Cainrt. Then, two map values Rcyc_bs_cin that are close to the valve lift Liftin at that time out of the map values Rcyc_bs_cin are selected according to the count value C_crk and the valve lift Liftin corrected as described above, and the two selection values are selected. The map value Rcyc_bs_cin of the disturbance compensation value for cam phase control is calculated by the interpolation calculation. Further, as described later, the map value Rcyc_bs_cin calculated as described above is corrected according to the engine speed NE to calculate a disturbance compensation value Rcyc_cin for cam phase control.

  It can be considered that the disturbance compensation value Rcyc_cin for cam phase control for compensating for the periodic disturbance generated in one cylinder 3a is calculated as described above. On the other hand, since the engine 3 of the present embodiment is of a four-cylinder type, periodic disturbances are generated four times for each cylinder 3a in one control cycle, and are caused by the phase difference between them. Occur in a state where they overlap each other. Therefore, in the present embodiment, in order to compensate for such periodic disturbance, instead of the above-described disturbance compensation value map, the map value Rcyc_bs_cin for Cain_cmd = Cainrt & Liftin = Liftinmax shown in FIG. As shown in FIG. 4, the map value Rcyc_bs_cin for Cain_cmd = Cainrt & Liftin = Liftminmin, and Cain_cmd = Cainrt, and the value of multiple stages of Liftin for interpolation when the valve lift Liftin is between the maximum value Liftinmax and the minimum value Liftinmin. A plurality of map values Rcyc_bs_cin (not shown) set in correspondence with each other is used.

  As is apparent from FIGS. 18 and 19, in this disturbance compensation value map, the map value Rcyc_bs_cin of the disturbance compensation value for cam phase control is set to the count value C_crk of the crank angle counter according to the prediction result of the periodic disturbance. It is set as the corresponding value. That is, the map value Rcyc_bs_cin is set in time series according to the prediction result of the periodic disturbance. Further, the cycle of the map value Rcyc_bs_cin is set to a crank angle of 180 °. This is because the period of the periodic disturbance applied to the variable cam phase mechanism 70 is equal to the crank angle of 180 ° for the reason described above. This disturbance compensation value map is stored in advance in the ROM 2c.

  Further, the search for the disturbance compensation value map is executed in the same manner as described above. That is, the count value C_crk of the crank angle counter is corrected in consideration of the advance angle of the target cam Cain_cmd with respect to the most retarded angle value Cainrt, and the map value Rcyc_bs_cin is determined according to the corrected count value C_crk and the valve lift Liftin. The map value Rcyc_bs_cin (disturbance compensation value) of the disturbance compensation value for cam phase control is calculated by selecting two map values Rcyc_bs_cin that are close to the valve lift Liftin at that time and interpolating the two selected values. To do. Further, as described later, the map value Rcyc_bs_cin calculated as described above is corrected according to the engine speed NE to calculate a disturbance compensation value Rcyc_cin for cam phase control. As described above, the disturbance compensation value Rcyc_cin for cam phase control is calculated as corresponding to a value obtained by inverting the sign of the predicted value of the periodic disturbance. As will be described later, the calculation of the disturbance compensation value Rcyc_cin for cam phase control is executed at a timing synchronized with the generation of the CRK signal.

  Next, the two-degree-of-freedom SLD controller 103 described above will be described. In the two-degree-of-freedom SLD controller 103, the cam phase is determined by a target value filter type two-degree-of-freedom sliding mode control algorithm [equations (1) to (8) shown in FIG. 20] according to the target cam phase Cain_cmd and the cam phase Cain. An SLD control input Rsld for control is calculated.

  In these formulas (1) to (8), each discrete data with the symbol (k) is data sampled (or calculated) in synchronization with a predetermined control period ΔT (5 msec in this embodiment). The symbol k represents the order of the sampling cycle of each discrete data. For example, the symbol k indicates a value sampled at the current control timing, and the symbol k-1 indicates a value sampled at the previous control timing. This also applies to the following discrete data. In the following description, the symbol (k) in each discrete data is omitted as appropriate.

  In this control algorithm, first, the filter value Cain_cmd_f of the target cam phase is calculated by the first-order lag filter algorithm shown in Expression (1). In the equation (1), POLE_f is a target value filter setting parameter, and is set to a value that satisfies the relationship of −1 <POLE_f <0.

  Next, the SLD control input Rsld for cam phase control is calculated by the sliding mode control algorithm expressed by the equations (2) to (8). That is, as shown in Expression (2), the SLD control input Rsld for cam phase control is calculated as the sum of the equivalent control input Req, the reaching law input Rrch, the adaptive law input Radp, and the nonlinear input Rnl. This equivalent control input Req is calculated by the equation (3). In the equation (3), a1, a2, b1, and b2 indicate model parameters of a model to be described later, and these are set to predetermined values. Further, in Expression (3), POLE is a switching function setting parameter, and is set to a value that satisfies the relationship of −1 <POLE_f <POLE <0.

  The reaching law input Rrch is calculated by the equation (4). In this equation (4), Krch represents a predetermined reaching law gain, and σs is a switching function defined as in equation (7).

  Furthermore, the adaptive law input Radp is calculated by the equation (5). In this equation (5), Kadp represents a predetermined adaptive law gain. On the other hand, the nonlinear input Rnl is calculated by the equation (6). In this equation (6), Knl represents a predetermined nonlinear gain, sgn (σs) represents a sign function, and its value is sgn (σs) = 1 when σs ≧ 0, When σs <0, sgn (σs) = − 1 (when σs = 0, sgn (σs) = 0 may be set).

  The above formulas (1) to (8) are derived as follows. That is, when the control target is defined as a system in which the SLD control input Rsld for cam phase control is an input and the cam phase Cain is an output, and is modeled as a discrete time system model, the equation (9) shown in FIG. can get. When the target value filter type two-degree-of-freedom sliding mode control theory is applied so that the cam phase Cain converges to the target cam phase Cain_cmd based on the model of the formula (9), the above-described formulas (1) to (8) are obtained. Derived.

  On the other hand, in the addition element 104 described above, as shown in the equation (10) in FIG. 21, the sum of the cam phase control disturbance compensation value Rcyc_cin calculated as described above and the cam phase control SLD control input Rsld is obtained. A reference input Rsld_f for cam phase control is calculated.

  Next, the aforementioned DSM controller 105 will be described. In the DSM controller 105, the phase control input Ucain is calculated by a control algorithm based on the ΔΣ modulation algorithm expressed by the equations (11) to (16) in FIG. In addition, the control algorithm of these Formulas (11)-(16) applies the control algorithm which the present applicant proposed in Japanese Patent Application No. 2003-293209.

  In Expression (11) of FIG. 21, Lim (Rsld_f) represents a limit value obtained by limiting the reference input Rsld_f for cam phase control. Specifically, the reference input Rsld_f for cam phase control is set to a predetermined value. Is calculated as a value limited within a range defined by a lower limit value Rmin and a predetermined upper limit value Rmax. That is, Lim (Rsld_f) = Rmin when Rsld_f <Rmin, Lim (Rsld_f) = Rsld_f when Rmin ≦ Rsld_f ≦ Rmax, and Lim (Rsld_f) = Rmax when Rsld_f> Rmax. The upper limit value Rmax and the lower limit value Rmin are set to positive and negative predetermined values whose absolute values are equal to each other.

  In Expression (12), r2 represents a limit value deviation, and udsm_of represents a predetermined offset value. Further, in equation (13), δ represents a deviation signal value, and is calculated as a deviation between the limit value deviation r2 and the previous value of the modulation output u as shown in equation (13).

  On the other hand, in equation (14), σ represents a deviation integral value that is an integral value of the deviation signal value δ, and is calculated as the sum of the previous value and the deviation signal value δ, as shown in the equation. . In Equation (15), fnl (σ) is a non-linear function, and its value is fnl (σ) = R when σ ≧ 0, and fnl (σ) = − R when σ <0. (When σ = 0, fnl (σ) = 0 may be set). The value R is set to a value that always satisfies the relationship R> | r2 |.

  In the DSM controller 105 of the present embodiment, the phase control input Ucain is calculated as a value that frequently repeats inversion between a predetermined upper limit value and a lower limit value by the above control algorithm, thereby controlling the cam phase control. Accuracy can be improved.

  Next, the valve lift controller 110 described above will be described. As shown in FIG. 22, the valve lift controller 110 includes a target valve lift calculation unit 111, a compensation element 112, a two-degree-of-freedom SLD controller 113, an addition element 114, and a DSM controller 115.

  In the valve lift controller 110, as described below, the lift control input Uliftin is calculated, and the lift control input Uliftin is input to the variable valve lift mechanism 50, whereby the valve lift Liftin is set to the target valve lift Liftin_cmd. It is controlled to become.

  First, in the target valve lift calculation unit 111 (target valve lift setting means), the target valve lift Liftin_cmd (valve lift parameter) is displayed on a map (see FIG. 34) described later according to the engine speed NE and the accelerator pedal opening AP. Calculated by searching.

  In addition, the compensation element 112 (disturbance compensation value storage means, disturbance compensation value selection means) calculates a disturbance compensation value Rcyc_lin for valve lift control as described below. The disturbance compensation value Rcyc_lin for the valve lift control compensates for the influence of the periodic disturbance generated by the rotation of the intake cam 6 during the operation of the engine 3 in the same manner as the disturbance compensation value Rcyc_cin for the cam phase control described above. Is to do. That is, when such a periodic disturbance is applied to the variable valve lift mechanism 50, the intake air amount changes due to the fluctuation of the valve lift Liftin, so that such a change in the intake air amount is avoided. Therefore, the value of the periodic disturbance applied to the variable valve lift mechanism 50 is predicted, and a value corresponding to a value obtained by inverting the sign of the predicted value is calculated as a disturbance compensation value Rcyc_lin for valve lift control. .

  Specifically, the disturbance compensation value Rcyc_lin for valve lift control is calculated by a method similar to that of the compensation element 102 described above. That is, first, a map value Rcyc_bs_lin (disturbance compensation value) is calculated by searching a disturbance compensation value map according to the cam phase Cain, the count value C_crk, and the target valve lift Liftin_cmd.

  In this compensation element 112, map values Rcyc_bs_lin for Liftin_cmd = Liftinmax & Cain = Cainrt shown in FIG. 23, Mapin values Rcyc_bs_lin and Cainrt for Liftin_cmd = Liftinmin & Cain = Cainrt shown in FIG. A plurality of map values Rcyc_bs_lin (not shown) respectively set corresponding to the values of a plurality of stages of Liftin_cmd for interpolation calculation when the target valve lift Liftin_cmd is between the maximum value Liftinmax and the minimum value Liftinmin. Use what you have. This disturbance compensation value map is stored in advance in the ROM 2c.

  In the search for the disturbance compensation value map described above, the count value C_crk of the crank angle counter is corrected in accordance with the advance angle of the cam phase Cain with respect to the most retarded angle value Cainrt, and the corrected count value C_crk and target valve lift are corrected accordingly. According to Liftin_cmd, two map values close to the target valve lift Liftin_cmd at that time are selected from the map values Rcyc_bs_lin, and the disturbance compensation value for valve lift control is calculated by interpolation between the two selected values. The map value Rcyc_bs_lin is calculated.

  Next, as described later, the map value Rcyc_bs_lin calculated as described above is corrected according to the engine speed NE to calculate a disturbance compensation value Rcyc_lin (corrected disturbance compensation value) for valve lift control. . As will be described later, the calculation of the disturbance compensation value Rcyc_lin for valve lift control is performed at a timing synchronized with the generation of the CRK signal.

  On the other hand, in the two-degree-of-freedom SLD controller 113 (control input calculating means), according to the target valve lift Liftin_cmd and the valve lift Liftin, the control algorithm [Expressions (1) to (8)] of the two-degree-of-freedom SLD controller 103 described above is used. The SLD control input Rsld ′ for valve lift control is calculated by a similar target value filter type two-degree-of-freedom sliding mode control algorithm.

  That is, in the two-degree-of-freedom SLD controller 113, the cam phase Cain, the target cam phase Cain_cmd, and the SLD control input Rsld for cam phase control in the equations (1) to (8) of FIG. , The target valve lift Liftin_cmd and the valve lift control SLD control input Rsld ′ and various variables, parameters, and predetermined set values are replaced with valve lift control values, respectively. An SLD control input Rsld ′ is calculated.

  In addition, in the addition element 114 (control input calculation means) described above, the disturbance compensation value Rcyc_lin for valve lift control calculated by the compensation element 112 and the SLD control for valve lift control calculated by the two-degree-of-freedom SLD controller 113. A reference input Rsld_f ′ (control input) for valve lift control is calculated as the sum of the inputs Rsld ′.

  Further, the DSM controller 115 described above uses a control algorithm similar to the control algorithm [Equations (11) to (16)] of the DSM controller 105 described above in accordance with the reference input Rsld_f ′ for valve lift control. Uliftin is calculated. That is, in the DSM controller 115, the reference input Rsld_f and the phase control input Ucain for the cam phase control are set to the reference input Rsld_f ′ for the valve lift control and the lift in the equations (11) to (16) of FIG. The lift control input Uliftin is calculated by an algorithm that replaces the control input Uliftin and replaces various functions and predetermined set values with values for valve lift control.

  Next, the compression ratio controller 120 described above will be described. As shown in FIG. 25, the compression ratio controller 120 includes a target compression ratio calculation unit 121, a compensation element 122, a two-degree-of-freedom SLD controller 123, an addition element 124, and a DSM controller 125.

  In the compression ratio controller 120, as described below, the compression ratio control input Ucr is calculated, and the compression ratio control input Ucr is input to the variable compression ratio mechanism 80, so that the compression ratio Cr becomes the target compression ratio. It is controlled to be Cr_cmd.

  First, in the target compression ratio calculation unit 121 (target compression ratio setting means), the target compression ratio Cr_cmd (compression ratio parameter) is a map (see FIG. 35) described later according to the engine speed NE and the accelerator pedal opening AP. Calculated by searching.

  The compensation element 122 (disturbance compensation value storage means, disturbance compensation value selection means) calculates a disturbance compensation value Rcyc_cr for compression ratio control as described below. This disturbance compensation value Rcyc_cr for controlling the compression ratio is for compensating for the influence of periodic disturbance caused by the combustion pressure during operation of the engine 3. That is, when such a periodic disturbance is applied to the variable compression ratio mechanism 80, the compression ratio Cr fluctuates, and accordingly, the compatibility with the ignition timing set in the ignition timing control is lowered. As a result, knocking may occur or combustion efficiency may be reduced. Therefore, in order to avoid such a change in the compression ratio, the compensation element 122 predicts the value of the periodic disturbance applied to the variable compression ratio mechanism 80 and sets a value obtained by inverting the sign of the predicted value. The disturbance compensation value Rcyc_cr for compression ratio control is calculated.

  Specifically, the disturbance compensation value Rcyc_cr for compression ratio control is calculated as follows. First, a map value Rcyc_bs_cr (disturbance compensation value) is calculated by searching a disturbance compensation value map in accordance with the compression ratio Cr and the count value C_crk of the crank angle counter.

  In this compensation element 122, as a disturbance compensation value map, the map value Rcyc_bs_cr for Cr_cmd = Crmax shown by a solid line in FIG. 26, the map value Rcyc_bs_cr for Cr_cmd = Crmin shown by a broken line in FIG. 26, and the target compression ratio Cr_cmd are maximum. For the interpolation calculation when the value is between the value Crmax and the minimum value Crmin, one having a plurality of map values Rcyc_bs_cr (not shown) set in correspondence with the values of Cr_cmd in a plurality of stages is used. This disturbance compensation value map is stored in advance in the ROM 2c. In this embodiment, the disturbance compensation value map described above is used due to the geometry of the variable compression ratio mechanism 80, but depending on the geometry of the variable compression ratio mechanism, the Crmax value and Crmin in the disturbance compensation value map are used. In some cases, the relationship with the value is reversed.

  As the map value Rcyc_bs_cr of the disturbance compensation value for compression ratio control, two map values close to the target compression ratio Cr_cmd at that time are selected from the above map values, and interpolation calculation of the two selected values is performed. Calculated.

  Next, the map value Rcyc_bs_cr calculated as described above is corrected according to the cam phase Cain, the valve lift Liftin, and the engine speed NE, as will be described later, thereby calculating a disturbance compensation value Rcyc_cr for compression ratio control. The As will be described later, the calculation of the disturbance compensation value Rcyc_cr for compression ratio control is executed at a timing synchronized with the generation of the CRK signal.

  On the other hand, in the two-degree-of-freedom SLD controller 123 (control input calculation means), according to the target compression ratio Cr_cmd and the compression ratio Cr, the control algorithm [Equations (1) to (8)] of the two-degree-of-freedom SLD controller 103 described above and The SLD control input Rsld ″ for compression ratio control is calculated by the same target value filter type two-degree-of-freedom sliding mode control algorithm.

  That is, in the two-degree-of-freedom SLD controller 123, the cam phase Cain, the target cam phase Cain_cmd, and the SLD control input Rsld for cam phase control in the equations (1) to (8) of FIG. For the compression ratio control by an algorithm in which the target compression ratio Cr_cmd and the SLD control input Rsld '' for controlling the compression ratio are replaced with various variables, parameters, and predetermined set values, respectively. SLD control input Rsld ″ is calculated.

  Further, in the addition element 124 (control input calculation means) described above, the disturbance compensation value Rcyc_cr for compression ratio control calculated by the compensation element 122 and the SLD control for compression ratio control calculated by the two-degree-of-freedom SLD controller 123. As a sum of the inputs Rsld ″, a reference input Rsld_f ″ (control input) for compression ratio control is calculated.

  Further, the DSM controller 125 described above uses a control algorithm similar to the control algorithm [Expressions (11) to (16)] of the DSM controller 105 described above in accordance with the reference input Rsld_f ″ for controlling the compression ratio. A control input Ucr is calculated. That is, in the DSM controller 125, in the above-described equations (11) to (16) of FIG. 21, the reference input Rsld_f for cam phase control and the phase control input Ucain are respectively set to the reference input Rsld_f ″ for compression ratio control and The compression ratio control input Ucr is calculated by an algorithm that replaces the compression ratio control input Ucr and replaces various functions and predetermined set values with values for compression ratio control.

  Next, various control processes executed by the ECU 2 will be described. First, a process for calculating three disturbance compensation values Rcyc_cin, Rcyc_lin, and Rcyc_cr will be described with reference to FIGS. This processing corresponds to the compensation elements 102, 112, and 122 described above, and after the IG · SW 27 is switched ON, the crankshaft 3d is in a predetermined crank angle position (for example, the predetermined cylinder 3a is in the TDC position). Is executed at a timing synchronized with the generation of the CRK signal. That is, the execution period of this process corresponds to the generation period of the CRK signal, and as described above, the generation period of the periodic disturbance is equivalent to the crank angle of 180 °, and therefore corresponds to a value of 1 / 18th thereof. To do.

  As shown in FIG. 27, in this process, first, in step 1 (abbreviated as “S1” in the figure, the same applies hereinafter), it is determined whether or not the calculation flag F_CAL is “1”. The calculation flag F_CAL is set to “0” when the IG • SW 27 is turned on. Therefore, when the current loop is the first time, the determination result of step 1 is NO. In this case, the process proceeds to step 2, and the calculation flag F_CAL is set to “1”. Thereby, the determination result of step 1 becomes YES in the loop after the next time.

  Next, in step 3, the count value C_crk of the crank angle counter is set to 0, and then the process proceeds to step 6 described later.

  On the other hand, if the determination result of step 1 is YES, the process proceeds to step 4 and the count value C_crk of the crank angle counter is incremented by 10 minutes. Next, at step 5, it is determined whether or not the count value C_crk of the crank angle counter is a value 720. When the determination result is NO, the process proceeds to Step 6 described later. On the other hand, when the determination result is YES, the process proceeds to step 3 described above, the count value C_crk of the crank angle counter is set to 0, and then the process proceeds to step 6.

  In step 6 following step 3 or step 5, a map value Rcyc_bs_cin of the disturbance compensation value for cam phase control is calculated. Specifically, the disturbance compensation value map value Rcyc_bs_cin for cam phase control is used for the cam phase control described above according to the target cam phase Cain_cmd, the count value C_crk of the crank angle counter and the valve lift Liftin, as described above. Is calculated by searching the disturbance compensation value map (FIGS. 18 and 19).

  Next, the routine proceeds to step 7, where the cam phase control correction coefficient Krcyc_cin is calculated by searching the table shown in FIG. 28 according to the engine speed NE. As shown in the figure, in this table, the correction coefficient Krcyc_cin is set to a larger value as the engine speed NE is lower. This is because the periodic disturbance frequency of the intake cam 6 is increased because the frequency of the periodic disturbance is low and the response gain of the cam phase control system to the external force is high in the low rotational speed range. This is to compensate.

  In this table, the correction coefficient Krcyc_cin is set to a value of 0 in a range equal to or higher than a predetermined rotation speed NEREF1 (for example, 4000 rpm). This is because, in the high rotation range, the response of the electromagnetic valve mechanism 74 as an actuator is not sufficient, so that it is difficult to accurately compensate for the periodic disturbance, and the periodic disturbance has a high frequency. On the other hand, the variable cam phase mechanism 70 is not affected by high-frequency periodic disturbance due to its response characteristic (low-pass characteristic).

  In Step 8 following Step 7, the disturbance compensation value Rcyc_cin for cam phase control is set to the product of the map value Rcyc_bs_cin calculated in Steps 6 and 7 and the correction coefficient Krcyc_cin, and stored in the RAM 2b.

  Next, in step 9, a map value Rcyc_bs_lin of a disturbance compensation value for valve lift control is calculated. Specifically, the disturbance compensation value map value Rcyc_bs_lin for the valve lift control, as described above, depends on the target valve lift Liftin_cmd, the cam phase Cain, and the count value C_crk of the crank angle counter as described above. This is calculated by searching the disturbance compensation value map (FIGS. 23 and 24).

  Next, the routine proceeds to step 10, where the correction coefficient Krcyc_lin for valve lift control is calculated by searching the table shown in FIG. 29 according to the engine speed NE. As shown in the figure, in this table, the correction coefficient Krcyc_lin is set to a larger value as the engine speed NE is lower. This is because, as described above, the frequency of the periodic disturbance is low and the response gain of the valve lift control system to the external force is high in the low rotation speed range, so that the periodic displacement of the valve lift Liftin is reduced. This is to compensate for it.

  Further, in this table, the correction coefficient Krcyc_lin is set to a value of 0 in a range equal to or higher than a predetermined rotation speed NEREF2 (for example, 5000 rpm). This is because the response of the lift actuator 60 is not sufficient in the high rotation range, so that it is difficult to accurately compensate for the periodic disturbance, and the periodic disturbance becomes a high frequency. This is because the variable valve lift mechanism 50 is not affected by periodic disturbances at high frequencies due to its response characteristics (low-pass characteristics).

  In Step 11 following Step 10, the disturbance compensation value Rcyc_lin for valve lift control is set to the product of the map value Rcyc_bs_lin calculated in Steps 9 and 10 and the correction coefficient Krcyc_lin.

  Next, the process proceeds to step 12, and a map value Rcyc_bs_cr of a disturbance compensation value for compression ratio control is calculated. Specifically, as described above, this map value Rcyc_bs_cr searches the above-described disturbance compensation value map for compression ratio control (FIG. 26) according to the count value C_crk of the crank angle counter and the target compression ratio Cr_cmd. Is calculated.

  Next, in step 13, the first correction coefficient Krcyc_cr1 for compression ratio control is calculated by searching the map shown in FIG. 30 according to the cam phase Cain and the valve lift Liftin. In addition, the predetermined values Liftin1 to 3 of the valve lift shown in the drawing are set so that the relationship of Liftin1> Liftin2> Liftin3 is established.

  As shown in the figure, in this map, the first correction coefficient Krcyc_cr1 is set to a smaller value as the cam phase Cain is an advanced value or as the valve lift Liftin is smaller. This is because the larger the cam phase Cain is, the lower the combustion temperature of the air-fuel mixture due to the increase in the amount of internal EGR, and the lower the combustion pressure, resulting in a smaller periodic disturbance amplitude. is there. The first correction coefficient Krcyc_cr1 is set to a smaller value as the valve lift Liftin is smaller. This is because the smaller the value of the valve lift Liftin, the smaller the intake air amount and the lower the combustion pressure, thereby reducing the amplitude of the periodic disturbance.

  Next, in step 14, the second correction coefficient Krcyc_cr2 for controlling the compression ratio is calculated by searching the table shown in FIG. 31 according to the engine speed NE. As shown in the figure, in this table, the second correction coefficient Krcyc_cr2 shows a maximum value when NE = NEREF4 (<NEREF3) in a region where the engine speed NE is lower than a predetermined engine speed NEREF3 (for example, 3000 rpm). Is set to This is because the maximum value is shown when the amplitude of the periodic disturbance is NE = NEREF4 due to the influence of the inertial mass in the low rotation speed range, and this is to be compensated.

  In this table, the second correction coefficient Krcyc_cr2 is set to a value of 0 in the region where NE ≧ NEREF3. This is because, in the high rotation range, the response of the compression ratio actuator 87 is not sufficient, so that it is difficult to accurately compensate for the periodic disturbance, and the periodic disturbance due to the combustion pressure is high frequency. On the other hand, the variable compression ratio mechanism 80 is not affected by high-frequency periodic disturbance due to its response characteristic (low-pass characteristic).

  In step 15 following step 14, the disturbance compensation value Rcyc_cr for controlling the compression ratio is set to the product of the map value Rcyc_bs_lin calculated in steps 12 to 14 and the first and second correction coefficients Krcyc_cr1, Krcyc_cr2. This process is terminated.

  Next, a process for calculating the three control inputs Ucain, Uliftin, and Ucr described above will be described with reference to FIG. This process is executed at a predetermined control period ΔT (5 msec in this embodiment) by setting the program timer.

  As shown in FIG. 32, in this process, first, in step 20, it is determined whether or not the variable mechanism normal flag F_VDOK is “1”. The variable mechanism normal flag F_VDOK is set to “1” when the variable cam phase mechanism 70, the variable valve lift mechanism 50, and the variable compression ratio mechanism 80 are all normal, and is set to “0” otherwise. .

  If the decision result in the step 20 is NO and at least one of the three variable mechanisms 50, 70, 80 has failed, the process proceeds to a step 32, and any of the phase control input Ucain, the lift control input Uliftin, and the compression ratio control input Ucr is selected. Is set to 0, the process is terminated. When all three control inputs are set to the value 0 in this way, the cam phase Cain is held at the most retarded angle value Cainrt by the variable cam phase mechanism 70, and the valve lift Liftin is set by the variable valve lift mechanism 50. Is held at a value suitable for idle operation and engine start, and the compression ratio Cr is held at the minimum value Crmin by the variable compression ratio mechanism 80.

  On the other hand, if the determination result of step 20 is YES and all the three variable mechanisms 50, 70, 80 are normal, the process proceeds to step 21, and it is determined whether or not the engine start flag F_ENGST is “1”. The engine start flag F_ENGST is set to “1” while the engine 3 is starting, and is set to “0” when the engine 3 has been started. If the determination result is YES and the engine is being started, the routine proceeds to step 22 where the target cam phase Cain_cmd is set to a predetermined starting value Cain_cmd_st.

  Next, in steps 23 and 24, the target valve lift Liftin_cmd and the target compression ratio Cr_cmd are set to predetermined starting values Liftin_cmd_st and Cr_cmd_st, respectively.

  Next, the process proceeds to step 25, and the three disturbance compensation values Rcyc_cin, Rcyc_lin, Rcyc_cr currently stored in the RAM 2b are read. That is, these values are sampled.

  In step 26 following step 25, the phase control input Ucain is used for the calculated target cam phase Cain_cmd and the read cam phase control disturbance compensation value Rcyc_cin, and the above-described equations (1) to (8), ( It calculates with the control algorithm of 10)-(16).

  Next, in step 27, a lift control input Uliftin is calculated. As described above, the lift control input Uliftin is calculated by the same control algorithm as the phase control input Ucain. That is, using the calculated target valve lift Liftin_cmd and the read disturbance compensation value Rcyc_lin for valve lift control, the lift is determined by the control algorithm similar to the equations (1) to (8) and (10) to (16). A control input Uliftin is calculated.

  Next, at step 28, a compression ratio control input Ucr is calculated. This compression ratio control input Ucr is also calculated by the same control algorithm as the phase control input Ucain as described above. That is, compression is performed using the calculated target compression ratio Cr_cmd and the read disturbance compensation value Rcyc_cr for controlling the compression ratio by the control algorithm similar to the equations (1) to (8) and (10) to (16). A ratio control input Ucr is calculated. Thereafter, this process is terminated.

  On the other hand, if the decision result in the step 21 is NO and the engine has been started, the process proceeds to a step 29, and the target cam phase Cain_cmd is searched for a map shown in FIG. 33 according to the engine speed NE and the accelerator pedal opening AP. To calculate. In the figure, the predetermined values AP1 to AP3 of the accelerator opening AP are set so that the relationship AP1> AP2> AP3 is established, and this relationship is the same in the following description.

  In this map, the target cam phase Cain_cmd is set to a more retarded value as the engine speed NE is higher when AP = AP1 and the load is high. When AP = AP2 and medium load, the target cam phase Cain_cmd is set to a more advanced value as the engine speed NE is higher from the low rotation range to the middle rotation range. From the rotational range to the high rotational range, the value is set to a more retarded value as the engine speed NE is higher. Further, even when AP = AP3 and the load is low, the target cam phase Cain_cmd is set to have the same tendency as that when the load is medium. The reason for this will be described later.

  In step 30 following step 29, the target valve lift Liftin_cmd is calculated by searching a map shown in FIG. 34 according to the engine speed NE and the accelerator pedal opening AP. In this map, the target valve lift Liftin_cmd is set to a larger value as the engine speed NE is higher when AP = AP1 and the load is high. Further, when AP = AP2 and medium load, the target cam phase Cain_cmd is set to a larger value as the engine speed NE is higher in the low engine speed range, and with respect to the engine speed NE in the medium engine speed range. In addition, the value is set to be almost the same, and in the high speed range, the value is set to a larger value as the engine speed NE is higher. Further, the target valve lift Liftin_cmd is set to have a tendency similar to that in the case of a low load even when the load is low, with AP = AP3.

  The reason why the target valve lift Liftin_cmd is set as described above and the target cam phase Cain_cmd is set as described above is as follows. That is, in the low load range / low rotation range, the valve lift Liftin is controlled to a low lift and the cam phase Cain is controlled to a value on the advance side so that the intake valve 4 closes earlier than the Otto cycle. Realize mirror cycle. This is to reduce the pumping loss and increase the in-cylinder flow by lowering the lift, thereby speeding up the combustion and improving the combustion efficiency.

  Further, in the middle load region / medium rotation region, the valve lift Liftin is controlled to a moderate lift and the cam phase Cain is controlled to a value on the advance side, thereby increasing the valve overlap and reducing the internal EGR amount. This is because the pumping loss is reduced and the fuel efficiency is improved by increasing the mirror cycle and increasing the speed of closing.

  Further, in the high load range / high rotation range, the valve lift Liftin is controlled to be a high lift and the cam phase Cain is controlled to a value on the retard side to increase the intake air amount and increase the engine torque. It is. In addition, during such control, since the intake behavior continues due to the inertial force of the intake at the beginning of the compression stroke and the reduction of the internal EGR amount, the cam phase is used to improve the charging efficiency. This is because Cain is controlled to a value on the retard side.

  In step 31 following step 30, the target compression ratio Cr_cmd is calculated by searching a map shown in FIG. 35 according to the engine speed NE and the accelerator pedal opening AP. In this map, the target compression ratio Cr_cmd is set to a smaller value as the AP is larger and the load is higher or the engine speed NE is higher. This is because the optimum value of the compression ratio Cr with respect to the ignition timing becomes smaller as the engine speed NE and the accelerator pedal opening AP are larger (that is, as the load is higher). That is, if the compression ratio Cr is set to a value on the high compression ratio side at high rotation / high load, the ignition timing must be controlled to the retard side in order to prevent knocking from occurring. This is to avoid the possibility of a decrease in efficiency.

  Next, as described above, steps 25 to 28 are executed to calculate three control inputs Ucain, Uliftin, Ucr, and then the present process is terminated.

  As described above, in the control device 1 of the present embodiment, the three disturbance compensation values Rcyc_cin, Rcyc_lin, and Rcyc_cr are values obtained by inverting the sign of the periodic disturbance to compensate for the expected periodic disturbance. It is calculated by map search, table search, etc. at the timing synchronized with the generation of the CRK signal. Further, according to the disturbance compensation values Rcyc_cin, Rcyc_lin, and Rcyc_cr calculated as described above, the three control inputs Ucain, Uliftin, and Ucr are respectively connected to the control algorithms [Equations (1) to (8), (10) to (16)] and a similar control algorithm.

  Therefore, by controlling the cam phase Cain, the valve lift Liftin, and the compression ratio Cr in a feed-forward manner using the control inputs Ucain, Uliftin, Ucr calculated as described above, the periodic disturbance is caused by the cam phase Cain, the valve lift Liftin. In addition, the influence on the compression ratio Cr can be compensated and suppressed more quickly than in the past. As a result, in the cam phase control and the valve lift control, it is possible to avoid changes in the intake air amount when the intake valve 4 is opened due to periodic disturbances, thereby avoiding fluctuations in the torque generated by the engine 3; A stable combustion state can be secured. In the compression ratio control, a change in the compression ratio Cr due to the influence of periodic disturbance can be avoided, and the compatibility between the compression ratio Cr and the ignition timing can be maintained in a good state. As a result, the occurrence of knocking and the decrease in combustion efficiency can be avoided.

  Further, in calculating the control inputs Ucain, Uliftin, Ucr, a target value filter type two-degree-of-freedom control algorithm is used. Therefore, the cam phase Cain is set to the target cam phase Cain_cmd, the valve lift Liftin is set to the target valve lift Liftin_cmd, and the compression ratio Cr is set. Can be converged to the target compression ratio Cr_cmd with quick and stable behavior. For example, even when a large deviation occurs between the cam phase Cain and the target cam phase Cain_cmd, the cam phase Cain is quickly and accurately set to the target cam phase Cain_cmd while avoiding the occurrence of overshoot due to such deviation. It can be well converged.

  Further, in the calculation of the disturbance compensation value Rcyc_cin for cam phase control, the map value Rcyc_bs_cin is calculated according to the valve lift Liftin and the target cam phase Cain_cmd, so that the disturbance compensation value Rcyc_cin is changed with the change of the valve lift Liftin. At least one of the amplitude change and behavior change of the periodic disturbance and the phase change of the periodic disturbance accompanying the change of the cam phase Cain can be calculated as values that can be appropriately compensated. Further, the correction coefficient Krcyc_cin is calculated according to the engine speed NE using the table of FIG. 28, and the disturbance compensation value Rcyc_cin is calculated by correcting the map value Rcyc_bs_cin with this correction coefficient Krcyc_cin. The frequency change of the periodic disturbance accompanying the change of the engine speed NE can be appropriately reflected.

  In addition, since the correction coefficient Krcyc_cin is set to a value of 0 in a range equal to or greater than the predetermined rotational speed NEREF1, the responsiveness of the variable cam phase mechanism 70 is not sufficient (that is, the responsiveness of the electromagnetic valve mechanism 74 as an actuator is not sufficient). Therefore, disturbance compensation by the disturbance compensation value Rcyc_cin is avoided in a high rotation speed range where it is difficult to accurately compensate for periodic disturbance, thereby preventing a decrease in controllability.

  Further, in the calculation of the disturbance compensation value Rcyc_lin for valve lift control, the map value Rcyc_bs_lin is calculated according to the target valve lift Liftin_cmd and the cam phase Cain. Therefore, the disturbance compensation value Rcyc_lin is changed with the change of the valve lift Liftin. At least one of the amplitude change and behavior change of the periodic disturbance and the phase change of the periodic disturbance accompanying the change of the cam phase Cain can be calculated as values that can be appropriately compensated. Further, the correction coefficient Krcyc_lin is calculated according to the engine speed NE using the table of FIG. 29, and the disturbance compensation value Rcyc_lin is calculated by correcting the map value Rcyc_bs_lin with this correction coefficient Krcyc_lin. It is possible to appropriately reflect the frequency change of the periodic disturbance accompanying the change of the engine speed NE.

  In addition to this, the correction coefficient Krcyc_lin is set to a value of 0 in a range equal to or higher than the predetermined rotational speed NEREF2, so that the responsiveness of the variable valve lift mechanism 50 is not sufficient (that is, the responsiveness of the lift actuator 60 is low). In a high rotational speed range where it is difficult to accurately compensate for periodic disturbances, disturbance compensation by the disturbance compensation value Rcyc_lin is avoided, so that deterioration in controllability can be avoided.

  In calculating the disturbance compensation value Rcyc_cr for compression ratio control, the map value Rcyc_bs_cr is calculated in accordance with the target compression ratio Cr_cmd. Therefore, the disturbance compensation value Rcyc_cr is changed to the amplitude of the periodic disturbance accompanying the change of the compression ratio Cr. It can be calculated as a value that can appropriately compensate for the change. Further, the first correction coefficient Krcyc_cr1 is calculated according to the cam phase Cain and the valve lift Liftin using the map of FIG. 30, and the disturbance compensation value Rcyc_cr is obtained by correcting the map value Rcyc_bs_cr with the first correction coefficient Krcyc_cr1. Since it is calculated, the disturbance compensation value Rcyc_cr can be calculated as a value that can appropriately compensate for the amplitude change of the periodic disturbance accompanying the change of the valve lift Liftin and the cam phase Cain.

  In addition, the second correction coefficient Krcyc_cr2 is calculated according to the engine speed NE using the table of FIG. 31, and the disturbance compensation value Rcyc_cr is obtained by correcting the map value Rcyc_bs_cr with the second correction coefficient Krcyc_cr2. Since it is calculated, the frequency change of the periodic disturbance accompanying the change of the engine speed NE can be appropriately reflected on this. Further, since the second correction coefficient Krcyc_cr2 is set to a value of 0 in a range equal to or higher than the predetermined rotational speed NEREF3, the responsiveness of the variable compression ratio mechanism 80 is not sufficient (that is, the responsiveness of the compression ratio actuator 87 is low). In a high rotation speed range where it is difficult to accurately compensate for periodic disturbances, disturbance compensation by the disturbance compensation value Rcyc_cr is avoided, thereby preventing a decrease in controllability.

  As described above, in any of the cam phase control, valve lift control, and compression ratio control, the control stability and control accuracy can be significantly improved.

  FIG. 36 shows a simulation result when the cam phase Cain is controlled while the target cam phase Cain_cmd is held at a constant value using the phase control input Ucain calculated by the control method as described above, and only one cylinder 3a is shown. This is shown by way of example. As is clear from comparison between FIG. 13 and FIG. 13 described above, according to the control device 1 of the present embodiment, the influence of periodic disturbance is obtained by using the disturbance compensation value Rcyc_cin for cam phase control as described above. It can be seen that it can be effectively suppressed.

  The first embodiment is an example in which the calculation timing (that is, the execution timing of the process of FIG. 27) as the selection timing of the three disturbance compensation values Rcyc_cin, Rcyc_lin, and Rcyc_cr is set to the generation timing of the CRK signal. The selection timing of the three disturbance compensation values is not limited to this, and may be set to a timing corresponding to each rotation of the crankshaft 3d by a predetermined angle. For example, the timing may be set to be synchronized with the generation of the CAM signal. In that case, in the compensation elements 102, 112, and 122, a map used for calculating the disturbance compensation values Rcyc_cin, Rcyc_lin, and Rcyc_cr is replaced with a predetermined value in synchronization with the generation of the CAM signal, instead of the count value C_crk of the crank angle counter. What is set according to the count value of the counter incremented by the cam angle may be used.

  Further, in the compensation element 102, the disturbance compensation value map value Rcyc_bs_cin corresponds to the target valve lift Liftin_cmd as the valve lift parameter and the cam phase Cain as the cam phase parameter, respectively, instead of the valve lift Liftin and the target cam phase Cain_cmd. May be calculated. Further, also in the compensation element 112, the map value Rcyc_bs_lin of the disturbance compensation value is changed to the valve lift Liftin as the valve lift parameter and the target cam phase Cain_cmd as the cam phase parameter, respectively, instead of the target valve lift Liftin_cmd and the cam phase Cain. It may be calculated accordingly.

  Similarly, in the compensation element 122, the map value Rcyc_bs_cr of the disturbance compensation value may be calculated according to the compression ratio Cr as the compression ratio parameter instead of the target compression ratio Cr_cmd. Instead of the valve lift Liftin and the cam phase Cain, Krcyc_cr1 may be calculated according to the target valve lift Liftin_cmd as the valve lift parameter and the target cam phase Cain_cmd as the cam phase parameter.

  In the first embodiment, in calculating the disturbance compensation value map value Rcyc_bs_cin for cam phase control, the count value C_crk of the crank angle counter is corrected in accordance with the target cam phase Cain_cmd, and in response to the valve lift Liftin. In this example, a technique for searching for one type of disturbance compensation value map (FIGS. 18 and 19) is used. According to a plurality of values of the target cam phase Cain_cmd, the disturbance compensation value map used for calculating the map value Rcyc_bs_cin is used. A plurality of types set respectively may be used. For example, preparing for Cain_cmd = Cainrt, for Cain_cmd = Cainad, and a plurality of target cam phase Cain_cmd values between them are prepared, and these disturbance compensation value maps Among them, two disturbance compensation value maps close to the target cam phase Cain_cmd at that time may be selected, and the map value Rcyc_bs_cin may be calculated by interpolation calculation of the map values in the two selection maps. Similarly, in the calculation of the map value Rcyc_bs_lin of the disturbance compensation value Rcyc_lin, a plurality of types set respectively according to a plurality of values of the target valve lift Liftin_cmd may be used as the disturbance compensation value map.

  Further, the first embodiment is an example using a target value filter type two-degree-of-freedom sliding mode control algorithm as a control algorithm for calculating a reference input Rsld for cam phase control. The control algorithm for calculating Rsld is not limited to this, and any control algorithm that can calculate the reference input Rsld for cam phase control as a value that causes the cam phase Cain to converge to the target cam phase Cain_cmd may be used. For example, a feedback control algorithm such as a PID control algorithm may be used, or a response designating control algorithm such as a backstepping control algorithm may be used. Similarly, as a control algorithm for calculating a reference input Rsld ′ for valve lift control or a reference input Rsld ″ for compression ratio control, a feedback control algorithm such as a PI control algorithm and a PID control algorithm, backstepping, etc. A response designating control algorithm such as a control algorithm may be used.

  The first embodiment is an example in which a target value filter type two-degree-of-freedom sliding mode control algorithm is used as a response designation type control algorithm. However, the response designation type control algorithm is not limited to this, and a backstepping control algorithm, etc. Any algorithm that can specify the convergence speed and convergence behavior of the output to be controlled with respect to the target value.

  The first embodiment is an example in which the DSM controller 105 is used in the calculation of the phase control input Ucain in the cam phase controller 100. However, this is omitted, and the reference input Rsld_f for cam phase control is directly used as the phase control input. You may comprise so that it may input into the variable cam phase mechanism 70 as Ucain. Further, in calculating the lift control input Uliftin in the valve lift controller 110, the DSM controller 115 is omitted, and the reference input Rsld_f ′ for valve lift control is directly input to the variable valve lift mechanism 50 as the lift control input Uliftin. It may be configured. Similarly, in calculating the compression ratio control input Ucr in the compression ratio controller 120, the DSM controller 125 is omitted, and the compression ratio control reference input Rsld_f ″ is used as it is as the compression ratio control input Ucr. You may comprise so that it may input into the mechanism 80. FIG.

  Furthermore, although 1st Embodiment is an example which used cam phase Cain and valve lift Liftin as a load parameter, a load parameter should just represent the load of the engine 3 not only in this. For example, the target cam phase Cain_cmd and the target valve lift Liftin_cmd may be used as load parameters, respectively, or the intake pipe absolute pressure PBA, the TH passage intake air amount GTH, and the accelerator opening AP may be used.

  Further, as the variable cam phase mechanism, instead of the hydraulic variable cam phase mechanism 70 of the first embodiment, the electromagnetic variable cam phase mechanism proposed by the present applicant in Japanese Patent Application No. 2003-293209 may be used. Good. In this case, in the electromagnetic variable cam phase mechanism, since the cam phase Cain is changed by the balance between the electromagnetic force of the solenoid and the biasing force of the spring, the periodic disturbance is only on the advance side or the retard side. Works. Therefore, when the disturbance compensation value Rcyc_cin for cam phase control is calculated in order to compensate for such periodic disturbance, the map value Rcyc_bs_cin is calculated using a map shown by a solid line or a broken line in FIG. That's fine.

  Next, a control device 1A according to a second embodiment of the present invention will be described. Since the control device 1A of the present embodiment is configured in the same manner except for a part as compared with the control device 1 of the first embodiment described above, the differences from the control device 1 of the first embodiment will be described below. It will be explained as the center. As shown in FIGS. 38 to 40, the control device 1A includes a cam phase controller 200, a valve lift controller 210, and a compression ratio controller 220, all of which are specifically ECU 2 (disturbance estimated value calculation). Means).

  First, the cam phase controller 200 will be described. As shown in FIG. 38, the cam phase controller 200 includes a target cam phase calculation unit 201 (target cam phase setting means), a compensation element 202 (disturbance compensation value storage means, disturbance compensation). Value selection means), a two-degree-of-freedom SLD controller 203 (control input calculation means), a DSM controller 205, and an adaptive disturbance observer 206 (disturbance estimated value calculation means). In the cam phase controller 200, the target cam phase calculation unit 201 and the compensation element 202 are configured in the same manner as that of the cam phase controller 100 described above, and thus description thereof is omitted here.

  The adaptive disturbance observer 206 calculates a disturbance estimated value c1 for cam phase control for compensating for modeling errors and disturbances. Specifically, in this adaptive disturbance observer 206, equations (17) to (19) in FIG. 41 are set according to the cam phase Cain, the disturbance compensation value Rcyc_cin for cam phase control, and the SLD control input Rsld for cam phase control. The disturbance estimated value c1 for cam phase control is calculated by an identification algorithm of the fixed gain method represented by Cain_hat in equation (17) represents the cam phase identification value, and e_id in equation (18) represents the identification error. Further, P ′ in Expression (19) represents an identification gain.

  The above formulas (17) to (19) are derived as follows. That is, when the estimated disturbance value c1 and disturbance compensation value Rcyc_cin for cam phase control are added to compensate for disturbance in the model of equation (9) in FIG. 20, the equation (20) shown in FIG. 41 is obtained. It is done. In this equation (20), the right side is replaced with the cam phase identification value Cain_hat, and statistical processing is performed so that the deviation between the cam phase identification value Cain_hat and the cam phase Cain is minimized based on the replaced model. When the identification algorithm of the fixed gain method based on the above is applied, the above-described equations (17) to (19) are derived.

  With the adaptive disturbance observer 206, the estimated disturbance c1 for cam phase control is calculated as a value that can appropriately compensate for modeling errors and disturbances by the algorithms of the above equations (17) to (19). .

  Further, the two-degree-of-freedom SLD controller 203 uses a target value filter type two-degree-of-freedom sliding mode control algorithm expressed by equations (21) to (27) in FIG. 42 to perform SLD control input Rsld (control input) for cam phase control. ) Is calculated. As is apparent from these equations (21) to (27), the control algorithm of the two-degree-of-freedom SLD controller 203 includes a cam phase control disturbance compensation value Rcyc_cin and a disturbance in the calculation formula of the equivalent control input Req. The point including the estimated value c1 and the point that the adaptive law input Radp is not used in the calculation of the SLD control input Rsld are different from those of the two-degree-of-freedom SLD controller 103 described above.

  Further, in the DSM controller 205, based on the SLD control input Rsld for cam phase control calculated as described above, a control algorithm similar to that of the DSM controller 105 described above [formulas (28) to (33) shown in FIG. ], The phase control input Ucain is calculated.

  The cam phase controller 200 is configured as described above, and similarly, the valve lift controller 210 is also configured. That is, as shown in FIG. 39, the valve lift controller 210 includes a target valve lift calculation unit 211 (target valve lift setting means), a compensation element 212 (disturbance compensation value storage means, disturbance compensation value selection means), and two degrees of freedom SLD. A controller 213 (control input calculating means), a DSM controller 215, and an adaptive disturbance observer 216 (disturbance estimated value calculating means) are provided. In the valve lift controller 210, the target valve lift calculation unit 211 and the compensation element 212 are configured in the same manner as that of the valve lift controller 110 described above, and thus description thereof is omitted here.

  The adaptive disturbance observer 216 calculates a disturbance estimated value c1 'for valve lift control by the same algorithm as the adaptive disturbance observer 206 of the cam phase controller 200. That is, in the equations (17) to (19) of FIG. 41 described above, Cain is replaced with Liftin, Cain_cmd is replaced with Liftin_cmd, Rcyc_cin is replaced with Rcyc_lin, c1 is replaced with c1 ′, Rsld is replaced with Rsld ′, each coefficient, etc. A disturbance estimated value c1 ′ for valve lift control is calculated by an algorithm in which is replaced with a value for valve lift control.

  Further, the two-degree-of-freedom SLD controller 213 calculates an SLD control input Rsld ′ for valve lift control by the same algorithm as the two-degree-of-freedom SLD controller 203 of the cam phase controller 200. That is, in the above-described equations (21) to (27) of FIG. 42, as described above, the SLD control input Rsld for valve lift control is performed by an algorithm in which each parameter, each coefficient, and the like are replaced with values for valve lift control. '(Control input) is calculated.

  Further, the DSM controller 215 calculates the lift control input Uliftin by the same control algorithm as the DSM controller 205 of the cam phase controller 200 based on the valve lift control SLD control input Rsld ′ calculated as described above. The That is, the lift control input Uliftin is calculated by an algorithm in which each parameter, each coefficient, and the like are replaced with values for valve lift control in the equations (28) to (33) in FIG.

  On the other hand, the compression ratio controller 220 is configured similarly to the cam phase controller 200. That is, as shown in FIG. 40, the compression ratio controller 220 includes a target compression ratio calculation unit 221 (target compression ratio setting means), a compensation element 222 (disturbance compensation value storage means, disturbance compensation value selection means), and two degrees of freedom SLD. A controller 223 (control input calculating means), a DSM controller 225, and an adaptive disturbance observer 226 (disturbance estimated value calculating means) are provided. In the compression ratio controller 220, the target compression ratio calculation unit 221 and the compensation element 222 are configured in the same manner as that of the compression ratio controller 120 described above, and a description thereof will be omitted here.

  The adaptive disturbance observer 226 calculates a disturbance estimated value c1 ″ for compression ratio control by the same algorithm as the adaptive disturbance observer 206 of the cam phase controller 200. That is, in the equations (17) to (19) of FIG. 41 described above, Cain is replaced with Cr, Cain_cmd is replaced with Cr_cmd, Rcyc_cin is replaced with Rcyc_cr, c1 is replaced with c1 ″, and Rsld is replaced with Rsld ″. A disturbance estimated value c1 ″ for compression ratio control is calculated by an algorithm in which a coefficient or the like is replaced with a value for compression ratio control.

  Further, the two-degree-of-freedom SLD controller 223 calculates an SLD control input Rsld ″ (control input) for compression ratio control by the same algorithm as the two-degree-of-freedom SLD controller 203 of the cam phase controller 200. That is, in the above-described equations (21) to (27) in FIG. 42, as described above, the SLD control input Rsld for compression ratio control is performed by the algorithm in which each parameter, each coefficient, and the like are replaced with values for compression ratio control. '' Is calculated.

  Further, in the DSM controller 225, the compression ratio control input Ucr is determined by the same control algorithm as the DSM controller 205 of the cam phase controller 200 based on the compression ratio control SLD control input Rsld ″ calculated as described above. Calculated. That is, the compression ratio control input Ucr is calculated by an algorithm in which the parameters, coefficients, and the like are replaced with values for compression ratio control in the equations (28) to (33) in FIG.

  In this control apparatus 1A, when the phase control inputs Ucain, Uliftin, Ucr are calculated by the ECU 2, the phase control input Ucain is calculated by the equations (21) to (33) in step 26 of FIG. Further, in step 27, the lift control input Uliftin is calculated by an algorithm in which the variables and the coefficients in equations (21) to (33) are replaced with values for valve lift control. In step 28, the same technique is used. Thus, the compression ratio control input Ucr is calculated.

  According to the control device 1A of the present embodiment configured as described above, similarly to the control device 1 of the first embodiment, the three control inputs Ucain, Rcyc_lin, Rcyc_cr correspond to the three disturbance compensation values Rcyc_cin, Rcyc_lin, Rcyc_cr. Since Uliftin and Ucr are respectively calculated, the control signal Ucain, Uliftin and Ucr calculated as described above are used to control the cam phase Cain, the valve lift Liftin and the compression ratio Cr in a feedforward manner, thereby causing periodic disturbance. Can be quickly compensated and suppressed for the effects on the cam phase Cain, valve lift Liftin and compression ratio Cr. As a result, in cam phase control, valve lift control, and compression ratio control, the same operational effects as those of the control device 1 described above can be obtained.

  In addition to this, the estimated disturbance values c1, c1 ′, c1 ″ are calculated by the adaptive disturbance observers 206, 216, 226 as values that compensate for modeling errors and disturbances, and such disturbance estimation is performed. Control inputs Ucain, Uliftin, Ucr are calculated according to the values c1, c1 ′, c1 ″. Therefore, the cam phase Cain, valve lift Liftin and compression ratio Cr can be controlled by these control inputs Ucain, Uliftin, Ucr so that no steady deviation occurs, and periodic disturbances are generated in the cam phase Cain, valve lift. The influence on Liftin and the compression ratio Cr can be compensated and suppressed more quickly than the control device 1 of the first embodiment. As described above, control stability and control accuracy can be further improved as compared with the control device 1.

  Next, a control device 1B according to a third embodiment of the present invention will be described. Since the control device 1B of the present embodiment is configured in the same manner except for a part as compared with the control device 1A of the second embodiment described above, the following points differ from the control device 1A of the second embodiment. It will be explained as the center. As shown in FIGS. 44 to 46, the control device 1B includes a cam phase controller 300, a valve lift controller 310, and a compression ratio controller 320, all of which are specifically ECU2 (model parameter identifying means). ).

  First, the cam phase controller 300 will be described. As shown in FIG. 44, the cam phase controller 300 includes a target cam phase calculation unit 301 (target cam phase setting means), a compensation element 302 (disturbance compensation value storage means, disturbance compensation). Value selection means), a two-degree-of-freedom SLD controller 303 (control input calculation means), a DSM controller 305, and a partial parameter identifier 307 (model parameter identification means). The cam phase controller 300 is provided with a partial parameter identifier 307 in place of the disturbance observer 206 described above, and the control of the two-degree-of-freedom SLD controller 303 accordingly. Part of the algorithm is different.

  The partial parameter identifier 307 is expressed by equations (34) to (39) in FIG. 47 according to the cam phase Cain, the disturbance compensation value Rcyc_cin for cam phase control, and the SLD control input Rsld for cam phase control. The parameter vector θ is identified by a sequential identification algorithm of the fixed gain method. This parameter vector θ is a vector whose transpose matrix is expressed as in equation (38), d1 in equation (38) is a disturbance compensation value gain, and the secular change and individuality of the variable cam phase mechanism 70 This is to compensate for the change in the amplitude of the periodic disturbance due to the variation between them. W in Expression (34) represents a virtual output, and W_hat in Expression (35) represents an identification value of the virtual output. Further, e_id ′ in the equation (37) is an identification error defined as in the equation (36), P ″ represents a predetermined identification gain, and ζ is a transposed matrix of the equation (39). It is a vector expressed as follows.

  The above equations (34) to (39) are derived as follows. That is, when the disturbance compensation value gain d1 is added to the above-described model of the equation (20) in FIG. 41, the equation (40) shown in FIG. 47 is obtained. In this equation (40), each variable is shifted by one discrete time, the parameters b1, b2, the disturbance compensation value gain d1 and the disturbance compensation value Rcyc_cin are discretized, and the Cain term is moved to the left side. Equation (41) is obtained. In the equation (41), if the left side is defined as W and the right side is defined as W_hat, the above equations (34) and (35) are obtained. Here, W can be considered as an output of a virtual control target, W_hat can be considered as an identification value of the output of such a control target, and Equation (35) Think of it as a model. Therefore, when the sequential identification algorithm of the fixed gain method is applied so as to identify the model parameter of the virtual control target so that the virtual output W approaches the identification value W_hat of the virtual output, the above (34) to (39) ) Is derived.

  The partial parameter identifier 307 sequentially identifies the model parameters b1 and b2, the estimated disturbance value c1, and the disturbance compensation value gain d1 by the identification algorithms of the above equations (34) to (39).

  Further, in the two-degree-of-freedom SLD controller 303, an SLD control input Rsld for cam phase control is calculated by a target value filter type two-degree-of-freedom sliding mode control algorithm expressed by equations (42) to (48) in FIG. The As is apparent from these equations (42) to (48), the control algorithm of the two-degree-of-freedom SLD controller 303 is equivalent to that of the two-degree-of-freedom SLD controller 203 described above to calculate the equivalent control input Req. The difference is that the disturbance compensation value Rcyc_cin for cam phase control is multiplied by the disturbance compensation value gain d1.

  Further, in the DSM controller 305, based on the SLD control input Rsld for cam phase control calculated as described above, the same control algorithm as the above-described DSM controller 205 [Equations (49) to (54) shown in FIG. 49]. Thus, the phase control input Ucain is calculated.

  Next, the valve lift controller 310 will be described. The valve lift controller 310 is also configured in the same manner as the cam phase controller 300. Specifically, as shown in FIG. 45, the valve lift controller 310 includes a target valve lift calculation unit 311 (target valve lift setting means), a compensation element 312 (disturbance compensation value storage means, disturbance compensation value selection means), 2 A degree-of-freedom SLD controller 313 (control input calculation means), a DSM controller 315, and a partial parameter identifier 317 (model parameter identification means) are provided. The valve lift controller 310 is provided with a partial parameter identifier 317 in place of the disturbance observer 216 described above, and the control of the two-degree-of-freedom SLD controller 303 accordingly. Part of the algorithm is different.

  In this partial parameter identifier 317, the model parameters b1 ′ and b2 ′, the estimated disturbance value c1 ′, and the disturbance compensation value gain d1 ′ for valve lift control are the same algorithm as the partial parameter identifier 307 of the cam phase controller 300. Are sequentially identified. That is, in the aforementioned equations (34) to (39) in FIG. 47, b1, b2, c1, d1 are b1 ′, b2 ′, c1 ′, d1 ′, Cain is Liftin, Rcyc_cin is Rcyc_lin, and Rsld is Rsld. The model parameters b1 ′ and b2 ′, the estimated disturbance value c1 ′, and the disturbance compensation value gain d1 ′ for valve lift control are obtained by an algorithm in which each coefficient is replaced with a value for valve lift control. Each is identified sequentially.

  Further, the two-degree-of-freedom SLD controller 313 calculates the SLD control input Rsld ′ for valve lift control by the same algorithm as the two-degree-of-freedom SLD controller 303 of the cam phase controller 300. That is, in the above-described equations (42) to (48) in FIG. 48, as described above, the SLD control input Rsld for valve lift control is performed by an algorithm in which each parameter and each coefficient are replaced with values for valve lift control. 'Is calculated.

  Further, the DSM controller 315 calculates the lift control input Uliftin by the same control algorithm as the DSM controller 305 of the cam phase controller 300 based on the valve lift control SLD control input Rsld ′ calculated as described above. The That is, in the equations (49) to (54) in FIG. 49, the lift control input Uliftin is calculated by an algorithm in which each parameter and each coefficient are replaced with values for valve lift control.

  On the other hand, the compression ratio controller 320 is configured similarly to the cam phase controller 300. That is, as shown in FIG. 46, the compression ratio controller 320 includes a target compression ratio calculation unit 321 (target compression ratio setting means), a compensation element 322 (disturbance compensation value storage means, disturbance compensation value selection means), and two degrees of freedom SLD. A controller 323 (control input calculation means), a DSM controller 325, and a partial parameter identifier 327 (model parameter identification means) are provided.

  In this partial parameter identifier 327, model parameters b 1 ″, b 2 ″, disturbance estimated value c 1 ″, and disturbance compensation value gain d 1 ″ for compression ratio control are converted into the partial parameter identifier 307 of the cam phase controller 300. Are sequentially identified by the same algorithm. That is, in the above-described equations (34) to (39) of FIG. 47, b1, b2, c1, d1 are b1 ″, b2 ″, c1 ″, d1 ″, Cain is Cr, and Rcyc_cin is Rcyc_cr. In addition, Rsld is replaced with Rsld ″, and model parameters b1 ″ and b2 ″ and disturbance estimated value c1 ″ for compression ratio control are obtained by an algorithm in which each coefficient is replaced with a value for compression ratio control. And disturbance compensation value gain d1 ″ are sequentially identified.

  Further, the two-degree-of-freedom SLD controller 313 calculates the SLD control input Rsld ″ for compression ratio control by the same algorithm as the two-degree-of-freedom SLD controller 303 of the cam phase controller 300. That is, in the above-described equations (42) to (48) in FIG. 48, as described above, the SLD control input Rsld for compression ratio control is obtained by an algorithm in which each parameter, each coefficient, and the like are replaced with values for compression ratio control. '' Is calculated.

  Further, in the DSM controller 325, the compression ratio control input Ucr is set by the same control algorithm as the DSM controller 305 of the cam phase controller 300 based on the compression ratio control SLD control input Rsld ″ calculated as described above. Calculated. That is, the compression ratio control input Ucr is calculated by an algorithm in which the parameters, coefficients, and the like are replaced with values for compression ratio control in the equations (49) to (54) in FIG.

  According to the control device 1B of the present embodiment configured as described above, in the same manner as the control devices 1 and 1A of the first and second embodiments, the three disturbance compensation values Rcyc_cin, Rcyc_lin, and Rcyc_cr correspond to three. Since two control inputs Ucain, Uliftin, and Ucr are calculated, the cam phase Cain, the valve lift Liftin, and the compression ratio Cr are respectively controlled in a feed-forward manner using the control inputs Ucain, Uliftin, and Ucr thus calculated. Thus, it is possible to quickly compensate and suppress the influence of the periodic disturbance on the cam phase Cain, the valve lift Liftin and the compression ratio Cr. As a result, in cam phase control, valve lift control, and compression ratio control, the same operational effects as those of the control device 1 described above can be obtained.

  In addition, in the cam phase controller 300 of the control device 1B, the model parameters b1 and b2, the disturbance estimated value c1, and the disturbance compensation value gain d1 are sequentially identified, and the two-degree-of-freedom SLD controller 303 does so. An SLD control input Rsld for cam phase control is calculated according to the identified values b1, b2, c1, d1 and the disturbance compensation value Rcyc_cin for cam phase control, and the phase control input Ucain is calculated based on this. . Therefore, even if the amplitude of the periodic disturbance changes due to the secular change of the variable cam phase mechanism 70 and the variation between individuals due to the phase control input Ucain, the cam phase Cain is appropriately compensated for it. Can be quickly and accurately converged to the target cam phase Cain_cmd. That is, the influence of periodic disturbance on the cam phase Cain can be compensated and suppressed more quickly than the cam phase controller 200 of the second embodiment. As described above, the stability and control accuracy of the cam phase control can be further improved as compared with the cam phase controller 200 of the second embodiment.

  In addition, the valve lift controller 310 and the compression ratio controller 320 can obtain the same effects as those of the cam phase controller 300, whereby the valve lift controller 210 and the compression ratio controller 220 of the second embodiment In comparison, the stability and control accuracy of valve lift control and compression ratio control can be further improved.

  The cam phase controller 300 of this embodiment is an example configured to identify a part of model parameters (b1, b2), the estimated disturbance value c1, and the disturbance compensation value gain d1 by the partial parameter identifier 307. Instead of the partial parameter identifier 307, a parameter identifier that identifies all model parameters a1, a2, b1, b2, disturbance estimated value c1, and disturbance compensation value gain d1 may be used. Instead, an identifier that identifies only the disturbance compensation value gain d1 may be used.

  Furthermore, in the partial parameter identifier 307, the fixed gain method is used as the identification algorithm, but other identification algorithms may be used instead. For example, a variable gain method, a δ correction method or σ correction method that is an improved algorithm of the fixed gain method, or an identification algorithm that combines a model parameter scheduler and a δ correction method may be used. In addition to this, it goes without saying that the partial parameter identifiers 317 and 327 in the controllers 310 and 320 may be configured as described above.

  Each of the above embodiments is an example in which the control device of the present invention is applied to the control of the variable cam phase mechanism 70, the variable valve lift mechanism 50, and the variable compression ratio mechanism 80 as a movable portion drive mechanism. Needless to say, the control device is not limited to this, and can be applied to control of the movable part drive mechanism of various industrial machines to which periodic disturbance is applied.

  Each embodiment is an example in which the variable cam phase mechanism 70 is configured to change the phase Cain of the intake camshaft 5 relative to the crankshaft 3d. However, the variable cam phase mechanism is not limited to this, and the exhaust camshaft is not limited thereto. 8 may be configured to change the phase of the crankshaft 3d with respect to the crankshaft 3d, and may further be configured to change the phases of the intake camshaft 5 and the exhaust camshaft 8 with respect to the crankshaft 3d. When the variable cam phase mechanism is configured in this way and controlled by the control algorithm described above, in addition to the above-described effects, the effects of periodic disturbances acting on the exhaust valve system are quickly compensated and suppressed. be able to. As a result, it is possible to avoid a decrease in the internal EGR amount due to the influence of periodic disturbance, and a stable combustion state can be ensured.

  Furthermore, although each embodiment is an example which comprised the variable valve lift mechanism 50 as what changes the lift Liftin of the intake valve 4, a variable valve lift mechanism is not restricted to this, The lift of the exhaust valve 7 is changed. You may comprise as a thing, Furthermore, you may comprise as what changes the lift of both the intake valve 4 and the exhaust valve 7. FIG. When the variable valve lift mechanism is configured in this way and controlled by the control algorithm described above, in addition to the above-described effects, the effects of periodic disturbances acting on the exhaust valve system are quickly compensated and suppressed. be able to. As a result, fluctuation of the internal EGR amount due to the influence of periodic disturbance can be avoided, and a stable combustion state can be ensured.

Explanation of symbols

1,1A, 1B controller
2 ECU (disturbance compensation value storage means, disturbance compensation value selection means, control input calculation means,
Target cam phase setting means, disturbance estimated value calculation means, model parameter identification means
, Target valve lift setting means, target compression ratio setting means)
2c ROM (Disturbance compensation value storage means)
3 Internal combustion engine
3b Piston (moving part)
3d crankshaft
4 Intake valve (moving part)
5 Intake camshaft (moving part)
7 Exhaust valve
8 Exhaust camshaft
50 Variable valve lift mechanism (moving part drive mechanism)
70 Variable cam phase mechanism (moving part drive mechanism)
80 Variable compression ratio mechanism (moving part drive mechanism)
101,201,301 Target cam phase calculation unit (target cam phase setting means)
111,211,311 Target valve lift calculation unit (Target valve lift setting means)
121,221,321 Target compression ratio calculation unit (Target compression ratio setting means)
102,112,122 Compensation element (disturbance compensation value storage means, disturbance compensation value selection means)
202,212,222 Compensation element (disturbance compensation value storage means, disturbance compensation value selection means)
302,312,322 Compensation element (disturbance compensation value storage means, disturbance compensation value selection means)
103,113,123 2-DOF sliding mode controller (control input calculation means)
203,213,223 2-DOF sliding mode controller (control input calculation means)
303,313,323 2-DOF sliding mode controller (control input calculation means)
104,114,124 Addition element
206,216,226 Adaptive disturbance observer (disturbance estimated value calculation means)
307,317,327 Partial parameter identifier (model parameter identification means)
NE speed of internal combustion engine
NEREF1 Predetermined speed
NEREF2 Predetermined speed
NEREF3 Predetermined speed
Cain cam phase (moving part operation timing, cam phase parameter, load parameter
T)
Cain_cmd Target cam phase (cam phase parameter)
Rcyc_cin Disturbance compensation value for cam phase control (corrected disturbance compensation value)
Rcyc_bs_cin Map value of disturbance compensation value for cam phase control (disturbance compensation value)
Rsld SLD control input (control input) for cam phase control
Rsld_f Reference input for cam phase control (control input)
c1 Disturbance estimate for cam phase control
b1, b2 model parameters
Liftin valve lift (moving part movement, valve lift parameters, load parameters
T)
Liftin_cmd Target valve lift (valve lift parameter)
Rcyc_lin Disturbance compensation value for valve lift control (corrected disturbance compensation value)
Rcyc_bs_lin Map value of disturbance compensation value for valve lift control (disturbance compensation value)
Rsld 'SLD control input (control input) for valve lift control
Rsld_f 'Reference input for valve lift control (control input)
c1 'Disturbance estimate for valve lift control
b1 ', b2' model parameters
Cr compression ratio
Cr_cmd Target compression ratio (compression ratio parameter)
Rcyc_cr Disturbance compensation value for compression ratio control (corrected disturbance compensation value)
Rcyc_bs_cr Map value of disturbance compensation value for compression ratio control (disturbance compensation value)
Rsld '' SLD control input (control input) for compression ratio control
Rsld_f '' Reference input for compression ratio control (control input)
c1 '' Disturbance estimate for compression ratio control
b1 '', b2 '' model parameters

Claims (27)

With changing at least one of operation timing and operation amount of the movable portion of the internal combustion engine, the periodic disturbance has an amplitude that varies periodic manner with rotation of the crankshaft of the internal combustion engine of the movable portion driving mechanism applied A control device,
Disturbance compensation value storage means for storing a plurality of disturbance compensation values set in advance according to a prediction result of the amplitude change of the periodic disturbance accompanying rotation of the crankshaft for compensating the periodic disturbance;
Each time the crankshaft of the internal combustion engine rotates by a predetermined angle, a disturbance compensation value for selecting a disturbance compensation value corresponding to the selected timing from the stored disturbance compensation values at a corresponding selection timing A selection means;
A control input for controlling the movable portion drive mechanism, and a control input-calculating means for de San according to the selected disturbance compensation value,
A control device for a movable part drive mechanism.   The movable part drive mechanism includes a variable cam phase mechanism that changes a cam phase that is a phase of at least one of an intake camshaft and an exhaust camshaft of the internal combustion engine with respect to the crankshaft as the operation timing of the movable part. The control device for a movable part drive mechanism according to claim 1.   3. The control device for a movable part driving mechanism according to claim 2, wherein the disturbance compensation value selection means selects the disturbance compensation value further according to a cam phase parameter representing the cam phase. The internal combustion engine includes a variable valve lift mechanism that changes a valve lift that is a lift of at least one of an intake valve and an exhaust valve of the internal combustion engine,
The plurality of disturbance compensation values are further set according to a prediction result of at least one of the amplitude change and behavior change of the periodic disturbance accompanying the change of the valve lift by the variable valve lift mechanism,
4. The control device for a movable part drive mechanism according to claim 2, wherein the disturbance compensation value selection unit selects the disturbance compensation value further according to a valve lift parameter representing the valve lift. 5.   The control input calculation means corrects the disturbance compensation value according to the rotational speed of the internal combustion engine, and calculates the control input according to the corrected disturbance compensation value. 4. The control device for a movable part drive mechanism according to any one of 4 above.   6. The control input calculation unit according to claim 2, wherein the control input calculation means calculates the control input regardless of the disturbance compensation value when the rotation speed of the internal combustion engine is equal to or higher than a predetermined rotation speed. The control apparatus of the movable part drive mechanism as described. Further comprising target cam phase setting means for setting a target cam phase as a target of the cam phase;
7. The control input calculating unit according to claim 2 , wherein the control input calculating unit calculates the control input using a predetermined response designating control algorithm so that the cam phase converges to the target cam phase. A control device for a movable part drive mechanism according to claim 1. Disturbance for calculating disturbance estimation value for compensating disturbance and modeling error in the variable cam phase mechanism by a predetermined estimation algorithm based on a model that defines the relationship between the disturbance estimation value, the control input, and the cam phase. Further comprising an estimated value calculation means,
The control device for a movable part drive mechanism according to any one of claims 2 to 6, wherein the control input calculation means calculates the control input further according to the calculated disturbance estimated value. A model parameter identifying means for on-board identification of a model parameter of a model defining a relationship between the disturbance compensation value, the control input, and the cam phase;
The control device for a movable part drive mechanism according to claim 2, wherein the control input calculation unit calculates the control input further according to the identified model parameter.   The movable portion drive mechanism includes a variable valve lift mechanism that changes a valve lift, which is a lift of at least one of an intake valve and an exhaust valve of the internal combustion engine, as the operation amount of the movable portion. 2. A control device for a movable part drive mechanism according to 1.   11. The control device for a movable part driving mechanism according to claim 10, wherein the disturbance compensation value selection means selects the disturbance compensation value further according to a valve lift parameter representing the valve lift. The internal combustion engine includes a variable cam phase mechanism that changes a cam phase that is a phase with respect to the crankshaft of at least one of an intake camshaft and an exhaust camshaft of the internal combustion engine,
The control device for a movable part drive mechanism according to claim 10 or 11, wherein the disturbance compensation value selection means selects the disturbance compensation value further according to a cam phase parameter representing the cam phase.   11. The control input calculation unit corrects the disturbance compensation value according to the rotational speed of the internal combustion engine, and calculates the control input according to the corrected disturbance compensation value. The control device for a movable part drive mechanism according to any one of 12.   14. The control input calculation means according to claim 10, wherein the control input is calculated irrespective of the disturbance compensation value when the rotational speed of the internal combustion engine is equal to or higher than a predetermined rotational speed. The control apparatus of the movable part drive mechanism as described. A target valve lift setting means for setting a target valve lift that is a target of the valve lift;
15. The control input calculating unit according to claim 10 , wherein the control input calculating means calculates the control input using a predetermined response designating control algorithm so that the valve lift converges to the target valve lift. A control device for a movable part drive mechanism according to claim 1. Disturbance in which a disturbance estimated value for compensating disturbance and modeling error in the variable valve lift mechanism is calculated by a predetermined estimation algorithm based on a model that defines the relationship between the estimated disturbance value, the control input, and the valve lift. Further comprising an estimated value calculation means,
15. The control device for a movable part drive mechanism according to claim 10, wherein the control input calculation unit calculates the control input further according to the calculated disturbance estimated value. A model parameter identifying means for on-board identification of a model parameter of a model defining a relationship between the disturbance compensation value, the control input, and the valve lift;
The control device for a movable part drive mechanism according to claim 10, wherein the control input calculation unit calculates the control input further according to the identified model parameter.   The movable portion drive mechanism includes a variable compression ratio mechanism that changes a compression ratio of the internal combustion engine by changing a stroke of a piston of the internal combustion engine as the operation amount of the movable portion. Item 4. The control device for the movable part drive mechanism according to Item 1.   19. The control device for a movable part drive mechanism according to claim 18, wherein the disturbance compensation value selection means selects the disturbance compensation value further according to a compression ratio parameter representing the compression ratio.   19. The control input calculating means corrects the disturbance compensation value according to the rotational speed of the internal combustion engine, and calculates the control input according to the corrected disturbance compensation value. 19. A control device for a movable part drive mechanism according to 19.   The control input calculating means corrects the disturbance compensation value according to a load parameter representing a load of the internal combustion engine, and calculates the control input according to the corrected disturbance compensation value. Item 20. The control device for a movable part drive mechanism according to Item 18 or 19. The internal combustion engine includes a variable cam phase mechanism that changes a cam phase that is a phase with respect to the crankshaft of at least one of an intake camshaft and an exhaust camshaft of the internal combustion engine,
The control device for a movable part driving mechanism according to claim 21, wherein the load parameter includes a cam phase parameter representing the cam phase. The internal combustion engine includes a variable valve lift mechanism that changes a valve lift that is a lift of at least one of an intake valve and an exhaust valve of the internal combustion engine,
The control device for a movable part drive mechanism according to claim 21 or 22, wherein the load parameter includes a valve lift parameter representing the valve lift.   The control input calculation means calculates the control input regardless of the disturbance compensation value when the rotation speed of the internal combustion engine is equal to or higher than a predetermined rotation speed. The control apparatus of the movable part drive mechanism as described. Further comprising target compression ratio setting means for setting a target compression ratio as a target of the compression ratio;
25. The control input calculating unit according to claim 18 , wherein the control input calculating unit calculates the control input using a predetermined response assignment control algorithm so that the compression ratio converges to the target compression ratio. A control device for a movable part drive mechanism according to claim 1. Disturbance in which a disturbance estimation value for compensating disturbance and modeling error in the variable compression ratio mechanism is calculated by a predetermined estimation algorithm based on a model that defines the relationship between the disturbance estimation value, the control input, and the compression ratio. Further comprising an estimated value calculation means,
The control device for a movable part drive mechanism according to any one of claims 18 to 24, wherein the control input calculation means further calculates the control input according to the calculated disturbance estimated value. A model parameter identifying means for on-board identification of a model parameter of a model defining a relationship between the disturbance compensation value, the control input, and the compression ratio;
25. The control device for a movable part drive mechanism according to claim 18, wherein the control input calculation unit calculates the control input further according to the identified model parameter.

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