JP2010121491A - Control device for drive source - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve stability of control of an engine by calculating a target value of output torque based on difference of target rotation speed and output rotation speed. <P>SOLUTION: ECU mounts: a power train manager 9100 converting target drive force of a vehicle to first target engine torque, calculating second target engine torque based on the target engine rotation speed and the output rotation speed calculated by an actual machine model G(s), and setting either of the first target engine torque or the second target engine torque as the final target engine torque; and an engine control part 9000 controlling the engine 1000 based on the set target engine torque. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a drive source control device, and more particularly to a technique for improving the stability of drive source control using a target output value converted from a target rotational speed.

  2. Description of the Related Art Conventionally, an engine in which an output torque value or the like is determined by a throttle valve opening (hereinafter also referred to as a throttle opening) is known. Generally, the throttle opening operates so as to uniquely correspond to the position of an accelerator pedal (hereinafter also referred to as an accelerator opening). However, if the throttle opening and the accelerator opening always correspond uniquely, it is difficult to control the driving force of the vehicle regardless of the driver's intention, for example, when the behavior of the vehicle is disturbed. It is. Therefore, there is a vehicle in which an engine is provided with an electronic throttle valve that is operated by an actuator so that output torque and the like can be controlled without depending on the accelerator opening. In a vehicle equipped with an electronic throttle valve, the target engine torque is set based on the behavior of the vehicle in addition to the accelerator opening, and the engine is controlled so that the actual engine torque becomes the set target engine torque. It is possible. Such control realizes, for example, constant speed travel of the vehicle.

  As a technique for causing a vehicle to travel at a constant speed, for example, Japanese Patent Application Laid-Open No. 2002-331852 (Patent Document 1) discloses a constant speed traveling device that stabilizes the vehicle speed at a constant vehicle speed at a target vehicle speed. This constant speed traveling device is a constant speed traveling device for an automobile that travels by shifting power from an internal combustion engine with a continuously variable transmission, and detects vehicle speed and vehicle speed detection means for detecting the vehicle speed and the rotational speed of the internal combustion engine. An automobile based on the rotation speed detection means, the target vehicle speed setting means for setting the target vehicle speed, the set target vehicle speed, the vehicle speed detected by the vehicle speed detection means, and the rotation speed of the internal combustion engine detected by the rotation speed detection means Is provided with constant speed control means for controlling the operation of the internal combustion engine and the continuously variable transmission so that the vehicle travels at the target vehicle speed.

According to this constant speed traveling device, the internal combustion engine and the continuously variable transmission are controlled for driving so that the vehicle travels at the target vehicle speed based on the set target vehicle speed, the detected vehicle speed, and the detected rotational speed of the internal combustion engine. By doing so, the automobile can be stably driven at the target vehicle speed.
JP 2002-331852 A

  By the way, when setting the target engine torque based on the engine speed, the target engine torque may be set in consideration of the differential term of the engine speed.

  However, if the engine speed is controlled using the target engine torque set in this manner, the control amount of the engine may greatly change with respect to a minute change in the engine speed. Therefore, the engine torque control may not be sufficiently stable.

  In the constant speed traveling device disclosed in the above-mentioned publication, in order to obtain the required cruise opening, the differential term of the engine speed is taken into account. However, this problem is not disclosed and is solved. I can't.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a drive source control device that improves control stability.

  A drive source control device according to a first aspect of the present invention is a drive source control device coupled to a transmission. The control apparatus includes means for setting a target rotational speed of the output shaft of the drive source, first calculating means for calculating the output rotational speed of the output shaft, and the target rotational speed and the first calculating means. A second calculating means for calculating a target value of the output torque of the driving source based on the difference from the calculated output rotational speed; and a control means for controlling the driving source based on a calculation result by the second calculating means. Control means.

  According to the first aspect, the target rotational speed of the output shaft of the drive source is set, and the target value of the output torque of the drive source is calculated based on the difference between the target rotational speed and the output rotational speed. The drive source is controlled based on the calculated target value. As a result, the drive source can be controlled so as to satisfy the demand for the output shaft speed. In particular, by calculating the target value of the output torque based on the difference between the target rotational speed and the output rotational speed, it is not necessary to consider the differential term of the rotational speed, and control stability can be improved. Therefore, it is possible to provide a drive source control device that improves control stability.

  In addition to the configuration of the first invention, the drive source control device according to the second invention includes means for setting a final target value used for control of the drive source based on the calculation result by the second calculation means. In addition. The first calculation means calculates the output rotation speed using the final target value as an input value.

  According to the second invention, by calculating the output rotation speed using the final target value as an input value, a value including various corrections and the like can be set as the input value, so that the output rotation speed can be calculated with high accuracy. . Thereby, the control accuracy can be improved.

  The drive source control device according to the third aspect of the invention further includes torque detection means for detecting the output torque of the drive source in addition to the configuration of the first aspect of the invention. The first calculation means calculates the output rotation speed using the detected output torque as an input value.

  According to the third invention, the output rotation speed can be calculated with high accuracy by calculating the output rotation speed using the detected output torque as an input value.

  In the drive source control apparatus according to the fourth aspect of the invention, in addition to the configuration of the second or third aspect of the invention, the first calculation means calculates the input value and the torque required to maintain the rotational speed of the output shaft. The output rotation speed is calculated based on the difference.

  According to the fourth aspect of the invention, the torque required for changing the rotation can be calculated by subtracting the torque required to maintain the rotation speed from the input value, so that the output rotation speed can be calculated with high accuracy.

  In the drive source control device according to the fifth aspect of the invention, in addition to the configuration of the fourth aspect of the invention, the first calculation means calculates the difference between the input value and the torque required to maintain the rotational speed of the output shaft. Dividing by inertia from the drive source to the input shaft of the transmission to calculate a rotation change amount of the output rotation speed, and means for calculating the output rotation speed by integrating the rotation change amount .

  According to the fifth invention, by calculating the output rotational speed according to the difference between the torque required to maintain the input value and the rotational speed of the output shaft, and the inertia from the drive source to the input shaft of the transmission, The output rotation speed can be calculated with high accuracy. In particular, since it is not necessary to consider the differential term of the rotational speed, the stability of the control can be improved.

  The drive source control device according to a sixth aspect of the present invention further includes a rotation speed detection means for detecting the rotation speed of the output shaft, in addition to the configuration of any one of the first to fifth aspects of the invention. The first calculating means calculates the output rotational speed using the detected rotational speed as an initial value.

  According to the sixth invention, the output rotation speed can be calculated with high accuracy by calculating the output rotation speed with the detected output rotation speed as an initial value.

  In the drive source control apparatus according to the seventh invention, in addition to the configuration of any one of the first to sixth inventions, the drive source is an engine. The rotation speed of the output shaft is the engine rotation speed.

  According to the seventh invention, the stability of the control can be improved by applying the present invention to the engine control based on the engine speed.

  In the drive source control apparatus according to the eighth invention, in addition to the configuration of any one of the first to sixth inventions, the drive source includes an engine and a torque converter connected to the output shaft of the engine. The rotation speed of the output shaft is the turbine rotation speed of the torque converter.

  According to the eighth aspect of the present invention, the stability of control can be improved by applying the present invention to engine control based on the turbine speed.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the same parts are denoted by the same reference numerals. Their names and functions are also the same. Therefore, detailed description thereof will not be repeated.

<Vehicle hardware configuration>
A vehicle equipped with a control device according to an embodiment of the present invention will be described with reference to FIG. This vehicle is an FR (Front engine Rear drive) vehicle. A vehicle other than FR may be used.

  The vehicle includes an engine 1000, an automatic transmission 2000, a torque converter 2100, a planetary gear unit 3000 that forms part of the automatic transmission 2000, a hydraulic circuit 4000 that forms part of the automatic transmission 2000, a propeller shaft 5000, A differential gear 6000, a rear wheel 7000, and an ECU (Electronic Control Unit) 8000 are included.

  Engine 1000 is an internal combustion engine that burns a mixture of fuel and air injected from an injector (not shown) in a combustion chamber of a cylinder. The piston in the cylinder is pushed down by the combustion, and the crankshaft is rotated. Engine 1000 drives auxiliary equipment 1004 such as an alternator and an air conditioner. The output torque (engine torque TE) of engine 1000 changes according to the operation amount of electronic throttle valve 8016, that is, the throttle opening degree. A motor may be used as a power source instead of or in addition to engine 1000. A diesel engine may be used. In the diesel engine, the output torque changes according to the valve opening time (operation amount) of the injector, that is, the fuel injection amount.

  Automatic transmission 2000 is connected to engine 1000 via torque converter 2100. Automatic transmission 2000 changes the rotational speed of the crankshaft to a desired rotational speed by forming a desired gear stage. Instead of the automatic transmission that forms the gear stage, CVT (Continuously Variable Transmission) that changes the gear ratio steplessly may be mounted. Furthermore, you may make it mount the automatic transmission which consists of a constant-meshing-type gearwheel speed-changed by a hydraulic actuator or an electric motor.

  Torque output from automatic transmission 2000 is transmitted to left and right rear wheels 7000 via propeller shaft 5000 and differential gear 6000.

  The ECU 8000 includes a position switch 8006 of a shift lever 8004, an accelerator opening sensor 8010 of an accelerator pedal 8008, an air flow meter 8012, a throttle opening sensor 8018 of an electronic throttle valve 8016, an engine speed sensor 8020, and an input shaft. A rotational speed sensor 8022, an output shaft rotational speed sensor 8024, an oil temperature sensor 8026, and a water temperature sensor 8028 are connected via a harness or the like.

  The position (shift position) of shift lever 8004 is detected by position switch 8006, and a signal representing the detection result is transmitted to ECU 8000. Corresponding to the position of the shift lever 8004, the gear stage of the automatic transmission 2000 is automatically formed. Further, a manual shift mode in which the driver can select an arbitrary gear stage may be selected according to the driver's operation.

  Accelerator opening sensor 8010 detects the opening of accelerator pedal 8008 and transmits a signal representing the detection result to ECU 8000. Air flow meter 8012 detects the amount of air taken into engine 1000 and transmits a signal representing the detection result to ECU 8000.

  The throttle opening sensor 8018 detects the opening of the electronic throttle valve 8016 whose opening is adjusted by the actuator, and transmits a signal representing the detection result to the ECU 8000. Electronic throttle valve 8016 adjusts the amount of air taken into engine 1000.

  In place of or in addition to the electronic throttle valve 8016, the engine 1000 is inhaled by a variable valve lift system that changes the lift amount and opening / closing phase of an intake valve (not shown) and an exhaust valve (not shown). The amount of air may be adjusted.

  Engine speed sensor 8020 detects the speed of the output shaft (crankshaft) of engine 1000 (hereinafter also referred to as engine speed NE), and transmits a signal representing the detection result to ECU 8000. Input shaft rotational speed sensor 8022 detects input shaft rotational speed NI of automatic transmission 2000 (turbine rotational speed NT of torque converter 2100), and transmits a signal representing the detection result to ECU 8000. Output shaft rotational speed sensor 8024 detects output shaft rotational speed NO of automatic transmission 2000 and transmits a signal representing the detection result to ECU 8000.

  Oil temperature sensor 8026 detects the temperature (oil temperature) of oil (ATF: Automatic Transmission Fluid) used for the operation and lubrication of automatic transmission 2000, and transmits a signal indicating the detection result to ECU 8000.

  Water temperature sensor 8028 detects the temperature (water temperature) of cooling water for engine 1000 and transmits a signal representing the detection result to ECU 8000.

  ECU 8000 includes position switch 8006, accelerator opening sensor 8010, air flow meter 8012, throttle opening sensor 8018, engine speed sensor 8020, input shaft speed sensor 8022, output shaft speed sensor 8024, oil temperature sensor 8026, and water temperature sensor. Based on a signal sent from 8028 or the like, a map stored in a ROM (Read Only Memory) 8002 and a program, the devices are controlled so that the vehicle is in a desired running state. The program executed by ECU 8000 may be recorded on a recording medium such as a CD (Compact Disc) or a DVD (Digital Versatile Disc) and distributed to the market. Further, ECU 8000 may be divided into a plurality of ECUs.

  In the present embodiment, ECU 8000 has the forward 1st to 8th gears when the shift lever 8004 is in the D (drive) position and the D (drive) range is selected as the shift range of automatic transmission 2000. Automatic transmission 2000 is controlled so that one of these gears is formed. A gear stage is formed by engaging friction engagement elements (clutch and brake), which will be described later, in a predetermined combination so as to connect the input shaft and the output shaft of automatic transmission 2000. When any one of the first to eighth forward gears is formed, torque can be transmitted to the rear wheel 7000. In the D range, it may be possible to form a higher gear than the eighth gear. The gear stage to be formed is determined based on a shift diagram created in advance by experiments or the like using the vehicle speed and the accelerator opening as parameters.

  When the shift lever 8004 is in the N (neutral) position or the P (parking) position, the friction engagement element is released when the N (neutral) range or the P (parking) range is selected as the shift range of the automatic transmission 2000. Then, the automatic transmission 2000 enters a neutral state. In the neutral state, the input shaft and output shaft of automatic transmission 2000 are disconnected.

  The planetary gear unit 3000 will be described with reference to FIG. Planetary gear unit 3000 is connected to a torque converter 2100 having an input shaft 2102 coupled to the crankshaft.

  The planetary gear unit 3000 includes a front planetary 3100, a rear planetary 3200, a C1 clutch 3301, a C2 clutch 3302, a C3 clutch 3303, a C4 clutch 3304, a B1 brake 3311, a B2 brake 3312, and a one-way clutch (F). 3320.

  The front planetary 3100 is a double pinion type planetary gear mechanism. Front planetary 3100 includes a first sun gear (S1) 3102, a pair of first pinion gears (P1) 3104, a carrier (CA) 3106, and a ring gear (R) 3108.

  The first pinion gear (P1) 3104 meshes with the first sun gear (S1) 3102 and the first ring gear (R) 3108. The first carrier (CA) 3106 supports the first pinion gear (P1) 3104 so that it can revolve and rotate.

  First sun gear (S1) 3102 is fixed to gear case 3400 so as not to rotate. First carrier (CA) 3106 is coupled to input shaft 3002 of planetary gear unit 3000.

  The rear planetary 3200 is a Ravigneaux type planetary gear mechanism. The rear planetary 3200 includes a second sun gear (S2) 3202, a second pinion gear (P2) 3204, a rear carrier (RCA) 3206, a rear ring gear (RR) 3208, a third sun gear (S3) 3210, a third Pinion gear (P3) 3212.

  Second pinion gear (P2) 3204 meshes with second sun gear (S2) 3202, rear ring gear (RR) 3208, and third pinion gear (P3) 3212. Third pinion gear (P3) 3212 meshes with third sun gear (S3) 3210 in addition to second pinion gear (P2) 3204.

  The rear carrier (RCA) 3206 supports the second pinion gear (P2) 3204 and the third pinion gear (P3) 3212 so that they can revolve and rotate. Rear carrier (RCA) 3206 is coupled to one-way clutch (F) 3320. The rear carrier (RCA) 3206 becomes non-rotatable when driving the first gear (when traveling using the driving force output from the engine 1000). Rear ring gear (RR) 3208 is coupled to output shaft 3004 of planetary gear unit 3000.

  The one-way clutch (F) 3320 is provided in parallel with the B2 brake 3312. That is, the outer race of the one-way clutch (F) 3320 is fixed to the gear case 3400, and the inner race is connected to the rear carrier (RCA) 3206.

  FIG. 3 shows an operation table showing the relationship between each gear position and the operation state of each clutch and each brake. By operating the brakes and the clutches in the combinations shown in the operation table, a forward 1st to 8th gear and a reverse 1st and 2nd gear are formed.

  The main part of the hydraulic circuit 4000 will be described with reference to FIG. The hydraulic circuit 4000 is not limited to the one described below.

  The hydraulic circuit 4000 includes an oil pump 4004, a primary regulator valve 4006, a manual valve 4100, a solenoid modulator valve 4200, an SL1 linear solenoid (hereinafter referred to as SL (1)) 4210, and an SL2 linear solenoid (hereinafter referred to as “the solenoid valve”). SL2 (described as SL (4)) 4220, SL3 linear solenoid (hereinafter referred to as SL (3)) 4230, SL4 linear solenoid (hereinafter referred to as SL (4)) 4240, and SL5 linear solenoid (hereinafter referred to as SL (3)). , SL (5)) 4250, SLT linear solenoid (hereinafter referred to as SLT) 4300, and B2 control valve 4500.

  Oil pump 4004 is connected to the crankshaft of engine 1000. As the crankshaft rotates, the oil pump 4004 is driven to generate hydraulic pressure. The hydraulic pressure generated by the oil pump 4004 is regulated by the primary regulator valve 4006 to generate a line pressure.

  Primary regulator valve 4006 operates using the throttle pressure regulated by SLT 4300 as a pilot pressure. The line pressure is supplied to the manual valve 4100 via the line pressure oil passage 4010.

  Manual valve 4100 includes a drain port 4105. From the drain port 4105, the oil pressure in the D range pressure oil passage 4102 and the R range pressure oil passage 4104 is discharged. When the spool of the manual valve 4100 is in the D position, the line pressure oil passage 4010 and the D range pressure oil passage 4102 are communicated, and hydraulic pressure is supplied to the D range pressure oil passage 4102. At this time, the R range pressure oil passage 4104 and the drain port 4105 are communicated, and the R range pressure of the R range pressure oil passage 4104 is discharged from the drain port 4105.

  When the spool of the manual valve 4100 is in the R position, the line pressure oil passage 4010 and the R range pressure oil passage 4104 are communicated, and the oil pressure is supplied to the R range pressure oil passage 4104. At this time, the D range pressure oil passage 4102 and the drain port 4105 are communicated, and the D range pressure in the D range pressure oil passage 4102 is discharged from the drain port 4105.

  When the spool of the manual valve 4100 is in the N position or the P position, both the D range pressure oil passage 4102 and the R range pressure oil passage 4104 are connected to the drain port 4105, and the D range pressure oil passage 4102 is in the D range. The pressure and the R range pressure of the R range pressure oil passage 4104 are discharged from the drain port 4105.

  The hydraulic pressure supplied to the D range pressure oil path 4102 is finally supplied to the C1 clutch 3301, the C2 clutch 3302, and the C3 clutch 3303. The hydraulic pressure supplied to the R range pressure oil passage 4104 is finally supplied to the B2 brake 3312.

  The solenoid modulator valve 4200 adjusts the hydraulic pressure (solenoid modulator pressure) supplied to the SLT 4300 to a constant pressure using the line pressure as the original pressure.

  SL (1) 4210 regulates the hydraulic pressure supplied to the C1 clutch 3301. SL (2) 4220 regulates the hydraulic pressure supplied to C2 clutch 3302. SL (3) 4230 regulates the hydraulic pressure supplied to the C3 clutch 3303. SL (4) 4240 regulates the hydraulic pressure supplied to C4 clutch 3304. SL (5) 4250 regulates the hydraulic pressure supplied to the B1 brake 3311.

  The SLT 4300 adjusts the solenoid modulator pressure in accordance with a control signal from the ECU 8000 based on the accelerator opening detected by the accelerator opening sensor 8010, and generates a throttle pressure. The throttle pressure is supplied to the primary regulator valve 4006 via the SLT oil passage 4302. The throttle pressure is used as a pilot pressure for the primary regulator valve 4006.

  SL (1) 4210, SL (2) 4220, SL (3) 4230, SL (4) 4240, SL (5) 4250, and SLT 4300 are controlled by a control signal transmitted from ECU 8000.

  The B2 control valve 4500 selectively supplies hydraulic pressure from one of the D range pressure oil passage 4102 and the R range pressure oil passage 4104 to the B2 brake 3312. A D range pressure oil passage 4102 and an R range pressure oil passage 4104 are connected to the B2 control valve 4500. The B2 control valve 4500 is controlled by the hydraulic pressure supplied from the SLU solenoid valve (not shown) and the biasing force of the spring.

  When the SLU solenoid valve is on, the B2 control valve 4500 is in the state on the left side in FIG. In this case, the B2 brake 3312 is supplied with the hydraulic pressure adjusted from the D range pressure using the hydraulic pressure supplied from the SLU solenoid valve as a pilot pressure.

  When the SLU solenoid valve is off, the B2 control valve 4500 is in the state on the right side in FIG. In this case, the R range pressure is supplied to the B2 brake 3312.

<About functions realized by ECU>
Referring to FIG. 5, ECU 8000 that is the control device according to the present embodiment will be further described. In FIG. 5, “F” indicates the driving force, “TE” indicates the engine torque, and “N” indicates the rotational speed. It should be noted that each function of ECU 8000 described below may be realized by hardware or may be realized by software.

  As shown in FIG. 5, the ECU 8000 includes an engine control unit 9000, a power train manager (PTM) 9100, an ECT (Electronic Controlled Transmission) unit 9200, a power train driver model (PDRM: Power train Driver). Model) 9300 is implemented.

  The engine control unit 9000 outputs an output torque (engine torque) of the engine 1000 such as an electronic throttle valve 8016, an ignition timing, an EGR (Exhaust Gas Recirculation) valve so as to realize the target engine torque input from the power train manager 9100. In order to control, the apparatus provided in the engine 1000 is controlled.

  The power train manager 9100 sets a target engine torque of the engine 1000 based on a driver's operation, vehicle behavior, a request from the ECT unit 9200, and the like. More specifically, among the first target engine torque set in consideration of the target driving force of the vehicle and the second target engine torque set in consideration of the target engine speed NET in the setting unit 9102 Is set as the final target engine torque to be output to the engine control unit 9000. The larger target engine torque may be set as the final target engine torque.

  The power train manager 9100 sets the first target engine torque in consideration of the target driving force of the vehicle, the target driving force set by the power train driver model 9300, VDIM (Vehicle Dynamics Integrated Management), and vibration suppression control. Then, the driving force arbitration unit 9110 mediates the target driving force set by the maximum vehicle speed limit control or the like. For example, the driving force arbitration unit 9110 selects the smallest target driving force or the largest target driving force.

  VDIM is a system that integrates VSC (Vehicle Stability Control), TRC (TRaction Control), ABS (Antilock Brake System), EPS (Electric Power Steering), etc. The difference between the running image and the vehicle behavior based on various sensor information is calculated, and the driving force of the vehicle, the brake hydraulic pressure, etc. are controlled so as to reduce the difference.

  VSC is a control that ensures the stability of the vehicle by automatically setting the brake hydraulic pressure of each wheel, the target driving force of the vehicle, and the like when the sensor detects a state where the front and rear wheels are likely to skid.

  The TRC automatically sets the brake hydraulic pressure of each wheel, the target driving force of the vehicle, etc., when the sensor detects idling of the driving wheel when starting and accelerating on a slippery road surface to ensure the optimum driving force. Control.

  ABS is a control system that automatically sets an optimum value of brake hydraulic pressure and prevents wheel lock. EPS is a control system that assists steering of a steering wheel by the force of an electric motor.

  The vibration damping control is a control for setting a target driving force for suppressing the pitching and bouncing of the vehicle calculated using the vehicle model from the actual driving force of the vehicle. As for the method for setting the driving force for suppressing the pitching and bouncing of the vehicle, the conventional technique may be used, and therefore the detailed description thereof will not be repeated here.

  The maximum vehicle speed restriction control is a control for setting a target driving force for limiting the vehicle speed to a predetermined maximum vehicle speed or less according to, for example, the current acceleration and the vehicle speed.

  The target driving force adjusted by the driving force adjusting unit 9110 is converted into the target engine torque by the torque converting unit 9112. For example, the driving force is converted into torque using the radius of rear wheel 7000, the gear ratio of differential gear 6000, the current gear ratio of automatic transmission 2000, the torque ratio of torque converter 2100, and the like. Note that a known general technique may be used as a method for converting the driving force into torque, and therefore detailed description thereof will not be given here.

  One of the target engine torque converted from the target driving force and the target engine torque set by the ECT unit 9200 is set in the torque arbitration unit 9114 as the first target engine torque. Which engine torque is set as the first target engine torque is determined according to the driving state of the vehicle, the shift state of the automatic transmission 2000, and the like.

  In order to set the second target engine torque in consideration of the target engine speed NET, the power train manager 9100 uses the target engine speed NET set by the power train driver model 9300 and the ECT section 9200 in the speed adjuster 9120. The target engine speed NET set by is adjusted. Which target engine torque is selected is determined in accordance with the driving state of the vehicle. The target engine speed NET adjusted by the rotation speed adjusting unit 9120 is input to the controller 9130.

  The controller 9130 calculates the second target engine torque based on the target engine speed NET. Controller 9130 includes a feedforward control unit 9132 and a feedback control unit 9134.

  In the present embodiment, the feedforward control unit 9132 calculates the difference between the target engine speed NET and the engine speed (hereinafter referred to as output speed) calculated based on the actual machine model G (s). Accordingly, the second target engine torque is calculated. In the present embodiment, feedforward control unit 9132 calculates the output rotational speed of engine 1000 using final target engine torque previously set in setting unit 9102 as an input value of actual machine model G (s).

  The feedback control unit 9134 performs feedback control using the target engine speed NET and the actual engine speed NE, and calculates a provisional second target engine torque correction amount calculated by the feedforward control unit 9132. To do. Note that the calculated correction amount is limited (guarded) so as to be equal to or greater than a predetermined lower limit value and equal to or less than a predetermined upper limit value.

  The controller 9130 adds the correction amount calculated by the feedback control unit 9134 to the provisional second target engine torque calculated by the feedforward control unit 9132 to calculate the final second target engine torque.

  In the present embodiment, controller 9130 calculates a second target engine torque that is suitable when the input shaft and output shaft of automatic transmission 2000 are disconnected, that is, in a neutral state. This is because the function of the controller 9130 is to control the engine 1000 based on the target engine speed NET, particularly in the neutral state of the automatic transmission 2000. Therefore, the second target engine torque calculated by the controller 9130 is suitable when the automatic transmission 2000 is in the neutral state, when shifting, or when neutral control is being executed.

  On the other hand, the second target engine torque calculated by the controller 9130 is, for example, when the input shaft and output shaft of the automatic transmission 2000 are connected via a clutch or brake and the torque can be transmitted to the rear wheel 7000. Is inappropriate.

  However, if the first target engine torque set in consideration of the target driving force of the vehicle is smaller than the second target engine torque calculated by the controller 9130, the first target engine torque is set as the final target engine torque. Therefore, the control of engine 1000 is not disturbed.

  Even if the second target engine torque is set as the final target engine torque, a smaller target engine torque is set, so that the actual engine torque does not become excessive.

  Even when the shift range is actually the drive range, the engine torque (driving force) does not become excessive even when it is erroneously recognized as the neutral range.

  The ECT unit 9200 performs shift control of the automatic transmission 2000 and sets a target engine torque and a target engine speed NET of the engine 1000 that are required to control the state of the automatic transmission 2000.

  The target engine torque set by ECT unit 9200 is set so that, for example, torque down or torque up for reducing shift shock can be realized. The ECT unit 9200 sets the target engine speed NET depending on whether the input shaft and the output shaft of the automatic transmission 2000 are disconnected or connected.

  The ECT unit 9200 determines the state of the input shaft and the output shaft of the automatic transmission 2000 by distinguishing between the control state and the actual state as shown in the tables of FIGS. As shown in FIGS. 6 and 7, ECT unit 9200 is configured to cut off the input shaft and output shaft of automatic transmission 2000 based on input shaft rotational speed NI, output shaft rotational speed NO, and shift range of automatic transmission 2000. It is determined whether it is a connected state or a connected state.

  The ECT unit 9200 sets the target engine speed NET according to the control state and actual state of the input shaft and output shaft of the automatic transmission 2000, as shown in the table of FIG.

  In FIG. 8, the invalid value means a value determined such that one of the first target engine torque and the second target engine torque is always greater than the other. Therefore, when the invalid value is set as the target driving force, the first target engine torque is larger than the second target engine torque. Similarly, when the invalid value is set as the target engine speed NET, the second target engine torque is larger than the first target engine torque.

  As shown in FIG. 8, the automatic transmission 2000 is controlled so that the input shaft and the output shaft are connected (controlled so that one of the gears is formed), and is actually connected. In this case, an invalid value is set as the target engine speed NET.

  When the input shaft and output shaft of automatic transmission 2000 are controlled so as to be connected and are actually cut off, it is preferable when the input shaft and output shaft of automatic transmission 2000 are actually connected. A value determined in this way is set as the target engine speed. Since the target engine speed NET at this time is based on the premise that the input shaft and the output shaft of automatic transmission 2000 are connected, the actual engine speed NE is a value that does not become excessive.

  Thus, if the input shaft and the output shaft are actually coupled, the first target engine torque is set as the final target engine torque, which is preferable in a state where the input shaft and the output shaft are actually connected. Control is possible. In contrast to the control, when the input shaft and the output shaft are actually cut off, the second target engine torque is set as the final target engine torque so that the actual engine speed NE does not become excessive. The engine 1000 can be controlled.

  In addition, as shown in FIG. 8, when the input shaft and the output shaft of the automatic transmission 2000 are controlled to be cut off, the input shaft and the output shaft of the automatic transmission 2000 are actually cut off. A value determined to be suitable is set as the target engine speed.

  Note that when the input shaft and output shaft of automatic transmission 2000 are actually connected, an unsuitable value can be set as the target engine speed, but correction of target engine torque in feedback control unit 9134 of controller 9130 is possible. Since the amount is limited (guarded), control does not fail.

  In addition, the ECT unit 9200 sets the invalid value as the target engine torque or the target engine speed when the target engine torque or the target engine speed is not set to be set. Therefore, the ECT unit 9200 always sets and outputs the target engine torque or the target engine speed.

  Returning to FIG. 5, the power train driver model 9300 is a model (function) used to set the target driving force and the target engine speed NET of the vehicle based on the operation of the driver.

  In the present embodiment, as shown in FIG. 9, the target driving force is set from the accelerator opening according to a map determined in advance based on the results of experiments and simulations. Further, the target engine speed NET is set from the accelerator opening.

  As shown in FIG. 10, the target engine speed NET is set in accordance with the accelerator opening, so that the engine speed NEL to be finally reached is set. Is obtained by processing in consideration of the delay due to inertia. A model expressed by a second-order lag function may be used.

In the model G ′ (s), an operation using the following Equation 1 is executed.
Current NET = Previous NET + (Current NET−Previous NET) / Coefficient (1)
The actual engine speed NE at the start of control is used as the initial value of the target engine speed NET.

  Thus, the target engine speed NET that gradually changes according to the accelerator opening is obtained from the engine speed NE at the start of control.

  In order to prevent interference with ISC (Idle Speed Control) control, when the engine 1000 is idle, an invalid value is set as the target engine speed NET. Except when idling, the target engine speed NET is set so as not to be lower than the target idling speed when the ISC control is executed.

  Further, in a state where the input shaft and the output shaft of automatic transmission 2000 are connected, more specifically, in a state where the driver recognizes that they are connected, the target driving force is set according to the accelerator opening. In addition, an invalid value is set as the target engine speed NET. Therefore, during neutral control, shifting, and when the turbine speed NT is excessive, the input shaft and output shaft are not actually connected, but the target driving force is set according to the accelerator opening. The invalid value is set as the target engine speed NET.

  In a state where the input shaft and the output shaft of automatic transmission 2000 are disconnected, more specifically, in a state where the driver recognizes that it is disconnected, an invalid value is set as the target driving force, and the accelerator The target engine speed NET is set according to the opening.

  For example, when the neutral range or the parking range is not selected as the shift range (when a travel range such as a drive range is selected), the input shaft and output shaft of the automatic transmission 2000 are connected (connected). It is determined that the driver recognizes that

  When the neutral range or the parking range is selected as the shift range, it is determined that the input shaft and the output shaft of automatic transmission 2000 are disconnected (the driver recognizes that they are disconnected). The

  Based on the input shaft rotational speed NI and the output shaft rotational speed NO of automatic transmission 2000, it is determined whether the input shaft and the output shaft of automatic transmission 2000 are disconnected or connected. You may do it.

  In addition, the power train driver model 9300 sets an invalid value as the target driving force or the target engine speed when the target driving force or the target engine speed is not in an operating state. Therefore, the power train driver model 9300 always sets and outputs the target driving force or the target engine speed.

<Regarding Characteristic Parts of ECU Function in the Present Embodiment>
In the power train having such a configuration, in the present embodiment, as shown in FIG. 11, the output calculated by the feedforward control unit 9132 of the controller 9130 in the target engine speed NET and the actual machine model G (s). It is characterized in that it is calculated as a provisional second target engine torque according to the difference from the rotational speed.

  In the present embodiment, the feedforward control unit 9132 provisional second target engine torque is obtained by multiplying the difference between the target engine speed NET and the output speed calculated in the actual machine model G (s) by the gain. Calculate as

  The controller 9130 adds the correction amount calculated by the feedback control unit 9134 to the provisional second target engine torque calculated by the feedforward control unit 9132 to calculate the final second target engine torque.

  In the present embodiment, feedforward control unit 9132 calculates provisional second target engine torque using final target engine torque previously determined by setting unit 9102 as an input value of actual machine model G (s). .

  As shown in FIG. 12, in the actual machine model G (s), the engine torque required to maintain the engine speed NE is subtracted from the input value to the actual machine model G (s). The engine torque required to maintain the engine speed NE includes the engine torque lost due to the frictional resistance of the engine 1000 itself and the load of the oil pump 4004, and the engine torque required to maintain the speed of the input shaft of the torque converter 2100. It is calculated by the sum of. The engine torque required to maintain the engine speed is not limited to being calculated by such a method.

  The engine torque lost due to the frictional resistance of engine 1000 itself and the load of oil pump 4004 is calculated, for example, according to a map created in advance by experiments or the like, having engine speed NE as a parameter.

The engine torque required to maintain the rotational speed of the input shaft of torque converter 2100 is, for example, torque capacity τ (input shaft rotational speed) determined by speed ratio e (turbine rotational speed NT / engine rotational speed NE) of torque converter 2100. The engine torque required for maintenance / the engine speed NE ² ) and the engine speed NE are calculated. By subtracting the engine torque required to maintain the engine speed NE from the input value, the portion of the engine torque required to change the engine speed NE is calculated.

  Further, in the actual machine model G (s), the value obtained by subtracting the engine torque required to maintain the engine speed NE from the input value is divided by the value I · K obtained by multiplying the inertia I by the coefficient K. The coefficient K is a predetermined unit conversion coefficient.

  As the inertia I, inertia from the engine 1000 to the input shaft of the automatic transmission 2000 is used. More specifically, in the engine 1000, the drive plate, the torque converter 2100, and the automatic transmission 2000, the inertia of a member located on the engine 1000 side of the forward clutch (particularly the C1 clutch 3301) on the torque transmission path. That is, inertia is used when automatic transmission 2000 is in a neutral state (a state where the input shaft and the output shaft are disconnected). The inertia is previously stored as data.

  Further, in the actual machine model G (s), the value divided by I · K is integrated to calculate the output rotation speed. The initial value of the output value (output rotation speed) of actual machine model G (s) is the engine rotation speed detected at the start of engine 1000 control.

  In the present embodiment, the input value of the actual machine model G (s) is not particularly limited to the final target engine torque previously determined by the setting unit 9102. For example, as the input value of the actual machine model G (s), as shown in FIG. 13, the provisional second target engine torque calculated by the feedforward control unit 9132 is used as the input value of the next actual machine model G (s). Or the last value of the final second target engine torque corrected by the feedback control unit 9134 may be used as the input value of the actual machine model G (s), or The torque estimated based on a load such as the intake air amount of the engine 1000 or the current actual torque detected using a torque detection sensor such as a strain gauge may be used as the input value of the actual machine model G (s). Good. By using a value close to the actual output torque as the input value, the calculation accuracy of the output rotation speed can be improved, and the control accuracy can be improved. The intake air amount is detected by an air flow meter 8012 or an intake pipe pressure sensor.

  Further, the feedback control unit 9134 performs PID (Proportion Integration Differential) control on the difference between the target engine speed NET and the actual engine speed NE, and the target engine speed NET and the actual engine speed NE. The amount of correction of the engine torque is calculated so that the difference between is reduced. The calculated correction amount is limited (guarded) so as to be not less than a predetermined lower limit value and not more than a predetermined upper limit value.

  The feedback control is executed only when the second target engine torque converted from the target engine speed NET is set (selected) as the final target engine torque. The initial value of the torque correction amount when the feedback control is started is, for example, zero.

  If the difference between the target engine speed NET and the actual engine speed NE is greater than or equal to the threshold value, the PID control integrator is not activated. That is, only proportional control and differential control are performed. If the difference between the target engine speed NET and the actual engine speed NE is greater than or equal to the threshold value, there is a high possibility that the automatic transmission 2000 is not in the neutral state, and the engine 1000 is based on the target engine speed NET. This is because it is not in a state to be controlled.

  As described above, according to the control device according to the present embodiment, one of the first target engine torque set from the target driving force of the vehicle and the second target engine torque converted from the target engine speed. One is set as the final target engine torque used to control the engine. Thus, when it is preferable to control the engine so as to satisfy the demand for the output torque of the engine, that is, the demand for the driving force of the vehicle, the engine is controlled based on the output torque so as to satisfy the demand for the engine speed. When it is preferable to control the engine, the engine can be controlled based on the engine speed. As a result, the control accuracy of the engine can be improved.

  In particular, as shown in FIG. 14, in the feedforward control unit 9132, the engine torque required for the engine speed NE to change to the target engine speed NET is expressed as the rate of change (angular acceleration) of the target engine speed NET, inertia, The provisional second target engine torque according to the present embodiment is calculated by adding the engine torque required for maintaining the rotation, as compared with the case of calculating the provisional second target engine torque. When doing so, it is not necessary to consider the differential term of the rotational speed. In the rotational speed control, if the differential term of the rotational speed is taken into account, the control amount of the engine greatly reacts to a minute change in the rotational speed, so that the control stability may not be sufficiently improved. Therefore, by applying the present invention and performing the rotational speed control without considering the differential term of the rotational speed, the stability of the control is sufficiently improved as compared with the case of considering the differential term of the rotational speed. Can be planned. Therefore, it is possible to provide a drive source control device that improves control stability.

  Note that the target turbine speed and the target turbine torque may be set instead of the target engine speed and the target engine torque. That is, it may be considered that the drive source is configured by the engine and the torque converter.

  In the present embodiment, the configuration in which one of the target engine torque based on the target engine speed and the target engine torque based on the target driving force is set as the final target value has been described as an example. The configuration is not limited. For example, the final target value may be set based on the target engine speed.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

It is a schematic block diagram which shows the power train of a vehicle. It is a skeleton figure which shows the planetary gear unit of an automatic transmission. It is a figure which shows the operation | movement table | surface of an automatic transmission. It is a figure which shows the hydraulic circuit of an automatic transmission. It is a functional block diagram of ECU. It is a figure which shows the state on the control of an automatic transmission. It is a figure which shows the actual state of an automatic transmission. It is a figure which shows the value set as target engine speed NET. It is a figure which shows a power train driver model. It is a figure which shows the map and model used in order to set the target engine speed NET. It is a figure which shows the controller which converts a target engine speed into the 2nd target engine torque. It is FIG. (1) which shows a structure of a feedforward control part. It is a figure (the 2) which shows the structure of a feedforward control part. It is a figure which shows the controller containing the feedforward control part which has a differential term.

Explanation of symbols

  1000 Engine, 1004 Auxiliary Machine, 2000 Automatic Transmission, 2100 Torque Converter, 4000 Hydraulic Circuit, 4004 Oil Pump, 5000 Propeller Shaft, 6000 Differential Gear, 7000 Rear Wheel, 8004 Shift Lever, 8006 Position Switch, 8008 Accelerator Pedal, 8010 Accelerator Open Degree sensor, 8012 air flow meter, 8016 electronic throttle valve, 8018 throttle opening sensor, 8020 engine speed sensor, 8022 input shaft speed sensor, 8024 output shaft speed sensor, 8026 oil temperature sensor, 8028 water temperature sensor, 9000 engine control Part, 9100 power train manager, 9102 setting part, 9110 driving force arbitration part, 9112 Torr Conversion unit, 9114 torque arbitration unit, 9120 rotation speed arbitration unit, 9130 controller, 9132 feedforward control unit, 9134 feedback control unit, 9200 ECT unit, 9300 power train driver model.

Claims (8)

A drive source control device coupled to the transmission,
Means for setting a target rotational speed of the output shaft of the drive source;
First calculating means for calculating the output rotational speed of the output shaft;
Second calculation means for calculating a target value of the output torque of the drive source based on a difference between the target rotation speed and the output rotation speed calculated by the first calculation means;
A drive source control device comprising: control means for controlling the drive source based on a calculation result by the second calculation means. The control device further includes means for setting a final target value used for controlling the drive source based on a calculation result by the second calculation means,
2. The drive source control device according to claim 1, wherein the first calculation unit calculates the output rotation speed using the final target value as an input value. 3. The control device further includes torque detection means for detecting output torque of the drive source,
2. The drive source control device according to claim 1, wherein the first calculation unit calculates the output rotation speed using the detected output torque as an input value. 3.   4. The drive source according to claim 2, wherein the first calculation unit calculates the output rotation speed based on a difference between the input value and a torque required to maintain the rotation speed of the output shaft. 5. Control device. The first calculation means includes
The difference between the input value and the torque required to maintain the rotation speed of the output shaft is divided by the inertia from the drive source to the input shaft of the transmission to calculate the rotation change amount of the output rotation speed. With means to
The drive source control device according to claim 4, further comprising means for calculating the output rotation speed by integrating the rotation change amount. The control device further includes a rotational speed detection means for detecting the rotational speed of the output shaft,
6. The drive source control device according to claim 1, wherein the first calculation unit calculates the output rotation speed using the detected rotation speed as an initial value. 7. The drive source is an engine,
The drive source control device according to claim 1, wherein the rotation speed of the output shaft is an engine rotation speed. The drive source includes an engine and a torque converter coupled to an output shaft of the engine,
The drive source control device according to claim 1, wherein the rotation speed of the output shaft is a turbine rotation speed of the torque converter.

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