WO2014002230A1 - 車両統合制御装置 - Google Patents
車両統合制御装置 Download PDFInfo
- Publication number
- WO2014002230A1 WO2014002230A1 PCT/JP2012/066573 JP2012066573W WO2014002230A1 WO 2014002230 A1 WO2014002230 A1 WO 2014002230A1 JP 2012066573 W JP2012066573 W JP 2012066573W WO 2014002230 A1 WO2014002230 A1 WO 2014002230A1
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- Prior art keywords
- torque
- actuator
- control device
- required torque
- integrated control
- Prior art date
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- 230000008859 change Effects 0.000 claims abstract description 18
- 238000004364 calculation method Methods 0.000 claims description 118
- 238000002485 combustion reaction Methods 0.000 claims description 56
- 230000005540 biological transmission Effects 0.000 claims description 54
- 238000011144 upstream manufacturing Methods 0.000 claims description 11
- 238000013016 damping Methods 0.000 claims description 7
- 230000006641 stabilisation Effects 0.000 claims description 4
- 238000011105 stabilization Methods 0.000 claims description 4
- 238000010586 diagram Methods 0.000 description 14
- 239000002699 waste material Substances 0.000 description 11
- 238000000034 method Methods 0.000 description 9
- 230000001133 acceleration Effects 0.000 description 6
- 230000004044 response Effects 0.000 description 5
- 238000012886 linear function Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/02—Control of vehicle driving stability
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D11/00—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
- F02D11/06—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance
- F02D11/10—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the electric type
- F02D11/105—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the electric type characterised by the function converting demand to actuation, e.g. a map indicating relations between an accelerator pedal position and throttle valve opening or target engine torque
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1497—With detection of the mechanical response of the engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/10—Parameters related to the engine output, e.g. engine torque or engine speed
- F02D2200/1002—Output torque
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/04—Introducing corrections for particular operating conditions
- F02D41/10—Introducing corrections for particular operating conditions for acceleration
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to a vehicle integrated control device including an internal combustion engine as a power source.
- the vehicle integrated control device includes a drive system manager that manages the operation of the entire drive system, an engine control unit that controls an internal combustion engine, a transmission control unit that controls an automatic transmission, a brake control unit that controls a brake device, and the like. ing.
- torque demand control is adopted as a control method of the internal combustion engine.
- a required torque is given to the engine control unit from the drive system manager.
- the requested torque includes a driver requested torque requested by the driver.
- the required torque includes a system required torque required by an in-vehicle system such as a sprung mass damping control system, a transmission control unit, and a vehicle attitude stabilization control system.
- the engine control unit determines an operation amount of an actuator of the internal combustion engine, for example, a throttle, based on a given required torque.
- the drive system manager determines the required torque to be given to the engine control unit by arbitrating the torque request from the driver and the torque request from the in-vehicle system. And an engine control unit operates actuators, such as a throttle, in order to realize the demand torque given from drive system manager.
- actuators such as a throttle
- the required torque cannot always be realized by the internal combustion engine. This is because there is an upper limit on the torque that can be realized by the internal combustion engine.
- the torque output from the internal combustion engine is maximized by fully opening the throttle. This maximum torque is not a constant value but a fluctuation value that varies depending on the engine speed.
- the maximum torque that can be output by the internal combustion engine varies depending on the supercharging state. That is, a difference occurs in the torque when the throttle is fully opened depending on the level of the supercharging pressure.
- the supercharging pressure can be actively controlled by an actuator, for example a wastegate valve. Therefore, in the case of an internal combustion engine with a supercharger equipped with a wastegate valve, the torque obtained when the throttle is fully opened and the wastegate valve is fully closed becomes the maximum torque of the internal combustion engine.
- the required torque given to the engine control unit includes a request regarding the magnitude of the torque and a request regarding the speed of change of the torque as information.
- the maximum torque of an internal combustion engine with a supercharger is the torque obtained when the throttle is fully open and the wastegate valve is fully closed, but the torque change speed that is always required over the entire torque range that does not exceed this maximum torque. Is not always possible. This is because the response speed of torque to the operation of the throttle is fast, but the response speed of torque to the operation of the wastegate valve is slow.
- the required torque When the required torque is in the torque range where the operation of the wastegate valve is required, and the required torque includes a torque component with a fast changing speed, the torque component of the changing speed must be realized. May not be possible.
- it In order to prevent control of the internal combustion engine based on a request torque that cannot be realized, it is required to provide the engine control unit with an appropriate request torque including not only the magnitude but also the speed of change.
- the above-mentioned subject is a subject applicable also to a certain kind of naturally aspirated internal combustion engine.
- an internal combustion engine in which the intake air amount is controlled by two types of actuators provided upstream and downstream of the intake passage such as an internal combustion engine having a throttle and an intake valve with a variable lift mechanism
- the torque control range by only the downstream actuator There is a difference in the torque control range by operating both actuators.
- the torque response speed for the operation of the downstream actuator and the torque response speed for the operation of the upstream actuator. Therefore, it is required to give an appropriate required torque including not only the size but also the change speed to the engine control unit that controls such an internal combustion engine.
- JP 2010-223122 A JP 2008-232069 JP 2009-293602 A JP 2010-255586 A JP 2010-066445 A JP 2010-132254 A JP 2007-189157 A
- the present invention has been made in view of the above-described problems, and an object of the present invention is to provide a vehicle integrated control device in which a required torque having an appropriate magnitude and change speed is given from a drive system manager to an engine control unit. To do.
- the vehicle integrated control device is a control device applied to a vehicle including an internal combustion engine as a power source.
- An internal combustion engine of a vehicle to which a vehicle integrated control device according to the present invention is applied includes a first actuator and a second actuator as actuators related to torque control.
- the first actuator is an actuator that is provided at the first position of the intake passage of the internal combustion engine and acts on the pressure downstream of the first position.
- a preferred first actuator is an actuator that acts to reduce the downstream pressure relative to the pressure upstream of the first position.
- the second actuator is an actuator that is provided at a second position upstream of the first position of the intake passage and acts on the pressure downstream of the second position.
- a preferred second actuator is an actuator that acts to increase the pressure downstream of the pressure upstream of the second position.
- the second actuator may be an actuator in which the rate of change in pressure downstream of the second position for the operation is slower than the rate of change of pressure downstream of the first position for the operation of the first actuator. .
- the example of the first actuator is a throttle
- the example of the second actuator is a supercharger with a control device for controlling the rotation speed of the compressor, for example, a supercharger with a wastegate valve. Machine.
- the vehicle integrated control apparatus includes at least a drive system manager that manages the operation of the entire drive system of the vehicle and an engine control unit that controls the internal combustion engine.
- a transmission control unit for controlling the automatic transmission and a brake control unit for controlling the brake device may be further included.
- Each control unit controls a mechanical device in charge based on a request or instruction from the drive system manager.
- the engine control unit includes at least an actuator operation unit, a first maximum torque calculation unit, and a second maximum torque calculation unit.
- the actuator operating unit is programmed to operate the first actuator and the second actuator based on the required torque provided from the drive system manager.
- the first maximum torque calculation unit is a maximum torque that can be realized when only the operation amount of the first actuator is actively changed without actively changing the operation amount of the second actuator (hereinafter referred to as the first maximum torque). ) Based on the engine speed and programmed to present the first maximum torque to the driveline manager.
- the second maximum torque calculation unit calculates the maximum torque (hereinafter referred to as the second maximum torque) that can be realized when both the operation amount of the first actuator and the operation amount of the second actuator are actively changed. And programmed to present the second maximum torque to the driveline manager.
- the drive system manager is programmed to determine the required torque to be applied to the engine control unit with reference to the first maximum torque and the second maximum torque presented from the engine control unit.
- the first maximum torque is an upper limit value of the torque range that can be realized by operating only the first actuator, whereas the second maximum torque is determined by operating both the first actuator and the second actuator. This is the upper limit value of the realizable torque range. Therefore, the torque range determined by the second maximum torque is wider than the torque range determined by the first maximum torque.
- a fast torque change can be realized by operating only the first actuator, whereas in the torque range from the first maximum torque to the second maximum torque, A fast torque change cannot be realized because of the need to operate the second actuator.
- the drive system manager can provide the engine control unit with an appropriate required torque including not only the magnitude but also the change speed.
- the drive system manager includes at least a first request torque calculation unit and a second request torque calculation unit.
- the first required torque calculation unit is programmed to calculate the first required torque which is a torque component having a slow change speed with reference to the second maximum torque presented from the engine control unit. Preferably, it is programmed to adjust the magnitude of the first required torque within a range not exceeding the second maximum torque.
- the first required torque may be a numerical value of a request regarding the torque from the driver transmitted through the accelerator pedal opening.
- the second required torque calculation unit is a torque component having a fast changing speed with reference to the first maximum torque presented from the engine control unit and the first required torque calculated by the first required torque calculation unit. 2 is programmed to calculate the required torque. Preferably, it is programmed to adjust the magnitude of the second required torque in a range not exceeding the margin of the first maximum torque with respect to the first required torque.
- the second required torque may be a numerical value of a request regarding torque from at least one of the sprung mass damping control system, the transmission control unit, and the vehicle attitude stabilization control system.
- the drive system manager gives the first required torque calculated by the first required torque calculation unit to the engine control unit, and also gives the second required torque calculated by the second required torque calculation unit to the engine control unit.
- the second required torque is superimposed on the first required torque to generate one signal, and the one signal is given to the engine control unit.
- a signal obtained by superimposing the second request torque on the first request torque and a signal representing the first request torque are generated, and these two signals are given to the engine control unit.
- a signal showing the 1st demand torque and a signal showing the 2nd demand torque are generated, respectively, and those two signals are given to an engine control unit.
- the transmission control unit may be programmed to control the automatic transmission according to the required speed ratio given from the drive system manager.
- the drive system manager is provided with a required speed ratio calculation unit for determining a required speed ratio to be given to the transmission control unit.
- the required speed ratio calculating unit is configured when a predetermined condition regarding a difference or ratio between the first maximum torque presented from the engine control unit and the first required torque calculated by the first required torque calculating unit is satisfied. , Programmed to change the required transmission ratio to a higher transmission ratio.
- Embodiment 1 FIG. Embodiment 1 of the present invention will be described below with reference to the drawings.
- FIG. 1 is a block diagram showing a configuration of a vehicle integrated control apparatus according to Embodiment 1 of the present invention.
- the vehicle integrated control apparatus 10 according to the present embodiment is composed of one or a plurality of in-vehicle computers, and is programmed as a control apparatus that integrally controls at least the internal combustion engine 20 and the automatic transmission 30.
- the internal combustion engine 20 to be controlled is a gasoline engine with a turbocharger.
- a throttle 22 is disposed in the intake passage of the internal combustion engine 20.
- a turbocharger with a wastegate valve 24 is attached upstream of the throttle 22 in the intake passage.
- the rotation speed of the compressor of the turbocharger can be controlled by operating the wastegate valve 24 to change the supercharging pressure that is the pressure upstream of the throttle 22.
- the intake pipe pressure that is the pressure downstream of the throttle 22 can be changed by operating the throttle 22, and the intake air amount that determines the output torque of the internal combustion engine 20 can be changed. That is, the throttle 22 corresponds to the first actuator in the present invention, and the entire turbocharger including the waste gate valve 24 corresponds to the second actuator in the present invention.
- the internal combustion engine 20 is further provided with a valve timing varying device 26 that changes the valve timing of the intake valve.
- the internal combustion engine 20 is equipped with various sensors including an engine speed sensor 28 that outputs a signal corresponding to the engine speed.
- the automatic transmission 30 is an electronically controlled automatic transmission that changes the gear ratio in accordance with a command signal.
- the automatic transmission 30 may be a stepped transmission that changes the gear ratio by a combination of a plurality of gears, or a continuously variable transmission that changes the gear ratio by changing the diameter of the pulley.
- the automatic transmission 30 may be a torque converter type transmission or a clutch type transmission.
- the vehicle integrated control device 10 includes a drive system manager 100, an engine control unit 200 that controls the internal combustion engine 20, and a transmission control unit 300 that controls the automatic transmission 30.
- the drive system manager 100 is positioned above the command transmission system, and the engine control unit 200 and the transmission control unit 300 are positioned below them.
- the vehicle integrated control device 10 includes a brake control unit for controlling the brake device, and the illustration and description thereof are omitted.
- the drive system manager 100 has a function of giving a required torque (TQrq) to the engine control unit 200 and a function of giving a required gear ratio (GRrq) to the transmission control unit 300.
- TQrq required torque
- GRrq required gear ratio
- the drive system manager 100 refers to the maximum torque of the internal combustion engine 20 presented from the engine control unit 200 in determining the required torque (TQrq) to be given to the engine control unit 200.
- TQrq required torque
- TQmax1 first maximum torque
- TQmax2 second maximum torque
- the engine control unit 200 continuously presents both types of maximum torque (TQmax1, TQmax2).
- the engine control unit 200 includes an actuator operation unit 210 that operates each actuator based on the required torque (TQrq) given from the drive system manager 100, and a first maximum torque calculation unit 220 that calculates a first maximum torque (TQmax1). And a second maximum torque calculation unit 230 for calculating the second maximum torque (TQmax2).
- the configuration of the actuator operation unit 210 is shown in the block diagram of FIG. 2, the configuration of the first maximum torque calculation unit 220 is shown in the block diagram of FIG. 3, and the configuration of the second maximum torque calculation unit 230 is the block diagram of FIG. Is shown in
- the actuator operation unit 210 includes five arithmetic elements 211, 212, 213, 214, and 215 as shown in FIG.
- the calculation element 211 calculates the intake air amount necessary for realizing the required torque (TQrq) using a map. In the map, torque and intake air amount are associated with various engine state quantities including engine speed, ignition timing, and air-fuel ratio as keys.
- the intake air amount calculated by the calculation element 211 is a required intake air amount (KLrq) for the internal combustion engine 20.
- the required intake air amount (KLrq) is input to the calculation element 212 and the calculation element 215.
- the calculation element 212 calculates an intake pipe pressure necessary for realizing the required intake air amount (KLrq) using a linear function equation.
- the relationship between the intake air amount and the intake pipe pressure is defined using a plurality of coefficients whose values are determined according to the engine speed, the waste gate valve duty, and the valve timing.
- the intake pipe pressure calculated by the calculation element 212 is the required intake pipe pressure (PMrq) for the internal combustion engine 20.
- the required intake pipe pressure (PMrq) is input to the calculation element 213 and the calculation element 214.
- the calculation element 213 calculates the throttle opening necessary for realizing the required intake pipe pressure (PMrq) using an inverse model of the air model.
- the air model is a physical model that models the dynamic characteristics of pressure and flow rate in the intake passage with respect to the operation of each actuator including the throttle 22. According to the inverse model, the operation amount of the actuator necessary for obtaining a desired pressure or flow rate can be calculated backward.
- the throttle opening calculated by the calculation element 212 is the target throttle opening (TA) for the throttle 22.
- the engine control unit 200 operates the throttle 22 according to the target throttle opening (TA).
- the calculation element 214 calculates the operation amount of the waste gate valve 24 necessary for realizing the required intake pipe pressure (PMrq).
- the operation amount of the wastegate valve 24 is a duty of a solenoid that opens and closes the wastegate valve 24.
- a value obtained by adding a predetermined value to the required intake pipe pressure (PMrq) is determined as the required supercharging pressure.
- the wastegate valve duty corresponding to the required supercharging pressure is calculated using a map or model that associates the supercharging pressure with the wastegate valve duty.
- the waste gate valve duty obtained by the calculation is a target waste gate valve duty (WGV) for the waste gate valve 24.
- the engine control unit 200 operates the waste gate valve 24 according to the target waste gate valve duty.
- the calculation element 215 calculates a valve timing suitable for the required intake air amount (KLrq). In the calculation of the valve timing, the valve timing corresponding to the required intake air amount (KLrq) is calculated using a map or model that associates the intake air amount with the valve timing. The valve timing calculated by the calculation element 215 becomes the target valve timing (VVT) for the valve timing variable device 26. The engine control unit 200 operates the variable valve timing device 26 according to the target valve timing.
- the first maximum torque calculation unit 220 includes three calculation elements 221, 222, and 223 as shown in FIG.
- the calculation element 223 calculates the supercharging pressure (Pic) acting upstream of the throttle 22 at the present time using an air model.
- the air model is a physical model that models the dynamic characteristics of pressure and flow rate in the intake passage with respect to the operation of each actuator.
- TA current throttle opening
- WSV waste gate valve opening
- VVT valve timing
- the boost pressure (Pic) calculated by the calculation element 223 is input to the calculation element 222.
- the calculation element 222 calculates the intake air amount obtained when the throttle 22 is fully opened based on the current wastegate valve duty (WGV) and valve timing (VVT) based on the supercharging pressure (Pic). To do.
- the intake air amount calculated by the calculation element 222 is the maximum value of the intake air amount that can be realized only by operating the throttle 22.
- the intake air amount calculated by the calculation element 222 is referred to as a first maximum intake air amount (KLmax1).
- the first maximum intake air amount (KLmax1) calculated by the calculation element 222 is input to the calculation element 221.
- the calculation element 221 calculates a torque that can be output by the internal combustion engine 20 based on the first maximum intake air amount (KLmax1) and the current engine speed (NE).
- the torque calculated by the calculation element 221 is the first maximum torque (TQmax1).
- the first maximum torque (TQmax1) is based on the current engine speed (NE), which can be achieved when only the opening of the throttle 22 is changed without changing the opening of the wastegate valve 24. It means the maximum torque.
- the second maximum torque calculation unit 230 includes three calculation elements 231, 232, and 233 as shown in FIG.
- the computing element 233 calculates the maximum boost pressure (Picmax) that can be realized at the current engine speed (NE) using a map.
- the supercharging pressure becomes maximum when the wastegate valve 24 is fully closed, and the maximum value varies depending on the engine speed. Further, the atmospheric pressure and the throttle opening affect the maximum value of the supercharging pressure.
- the maximum supercharging pressure is determined for each engine speed on the premise of standard atmospheric pressure and full throttle.
- the maximum boost pressure here is the maximum value of the boost pressure finally reached after the wastegate valve 24 is fully closed.
- the maximum boost pressure (Picmax) calculated by the calculation element 233 is input to the calculation element 232.
- the calculation element 232 is an intake air amount obtained when the throttle 22 is fully opened when the wastegate valve 24 is fully closed and the valve timing variable device 26 is operated to a position where the intake air amount is maximized. Is calculated based on the maximum boost pressure (Picmax).
- the intake air amount calculated by the calculation element 232 is the maximum value of the intake air amount that can be realized by operating the wastegate valve 24 in addition to the throttle 22.
- the intake air amount calculated by the calculation element 232 is referred to as a second maximum intake air amount (KLmax2).
- the second maximum intake air amount (KLmax2) calculated by the calculation element 232 is input to the calculation element 231.
- the calculation element 231 calculates a torque that can be output by the internal combustion engine 20 based on the second maximum intake air amount (KLmax2) and the current engine speed (NE).
- the torque calculated by the calculation element 231 is the second maximum torque (TQmax2).
- the second maximum torque (TQmax2) is based on the current engine speed (NE) that can be achieved when the opening of the throttle 22 is changed and the opening of the wastegate valve 24 is also changed. It means the maximum torque.
- the drive system manager 100 includes a first required torque calculation unit 110 and a second required torque calculation unit 120 as means for calculating the required torque (TQrq) to be given to the engine control unit 200.
- the first maximum torque (TQmax1) calculated by the first maximum torque calculation unit 220 is presented to the second required torque calculation unit 120.
- the second maximum torque (TQmax2) calculated by the second required torque calculation unit 120 is presented to the first required torque calculation unit 110.
- the drive system manager 100 further includes a required speed ratio calculation unit 130 that calculates a required speed ratio (GRrq) to be given to the transmission control unit 300. The function of the required gear ratio calculation unit 130 will be described later.
- the first required torque calculation unit 110 calculates a first required torque (TQrq1) composed of a torque component having a slow changing speed among the required torque for the internal combustion engine 20.
- a request (Rq0) related to the torque from the driver transmitted through the accelerator pedal opening and a request (Rq1) related to the torque from the auto cruise system are input to the first required torque calculation unit 110.
- the first required torque calculation unit 110 arbitrates these requests and determines the magnitude of the first required torque (TQrq1) based on the arbitration result.
- the second maximum torque (TQmax2) presented from the second required torque calculation unit 120 is referred to, and the magnitude of the first required torque (TQrq1) is adjusted within a range not exceeding the second maximum torque (TQmax2).
- TQrq1 the magnitude of the first demand torque (TQrq1) is determined based on the demand (Rq0) from the driver, if the demand (Rq0) corresponds to the maximum accelerator pedal opening, The first required torque (TQrq1) is sized according to the second maximum torque (TQmax2).
- the second required torque calculation unit 120 calculates a second required torque (TQrq2) composed of a torque component having a fast changing speed among the required torque for the internal combustion engine 20.
- the second required torque calculation unit 120 includes a request for torque from the sprung mass damping control system (Rq2), a request for torque from the transmission control unit (Rq3), and a request for torque from the vehicle attitude stabilization control system. (Rq4) is entered. These requirements may require that the torque be vibrated at a high frequency, or may require that the torque be changed in a pulsed manner.
- the second required torque calculation unit 120 arbitrates these requests and determines the magnitude of the second required torque (TQrq2) based on the arbitration result.
- the second required torque calculation unit 120 includes the first maximum torque (TQmax1) presented from the first request torque calculation unit 110 and the first request torque (TQrq1) calculated by the first request torque calculation unit 110. Then, the magnitude of the second required torque (TQrq2) to be finally output is adjusted.
- the second required torque calculation unit 120 adjusts the magnitude of the second required torque (TQrq2) to be finally output according to the procedure shown in the flowchart of FIG.
- step S102 it is determined whether the margin of the first maximum torque (TQmax1) with respect to the first required torque (TQrq1) is equal to or greater than zero. If the difference between the first maximum torque (TQmax1) and the first required torque (TQrq1) is zero or more, the determination in step S104 is further performed. In step S104, it is determined whether or not the difference between the first maximum torque (TQmax1) and the first required torque (TQrq1) is equal to or greater than the second required torque (TQrq2) calculated based on each request.
- step S106 is selected.
- the second required torque calculation unit 120 outputs the second required torque (TQrq2) calculated based on each request as it is.
- step S108 is selected.
- the second required torque calculation unit 120 corrects the magnitude of the second required torque (TQrq2) calculated based on each demand, and finally increases the magnitude of the second required torque (TQrq2) to be output. This is less than or equal to the difference between the first maximum torque (TQmax1) and the first required torque (TQrq1). That is, the magnitude of the second required torque (TQrq2) is corrected so that the value obtained by adding the second required torque (TQrq2) to the first required torque (TQrq1) does not exceed the first maximum torque (TQmax1).
- step S110 is selected.
- the second required torque calculation unit 120 sets the magnitude of the second required torque (TQrq2) to be output to zero.
- the drive system manager 100 adds the second request torque (TQrq2) output from the second request torque calculation unit 120 to the first request torque (TQrq1) output from the first request torque calculation unit 120. Then, the total value is given to the engine control unit 200 as the final required torque (TQrq).
- FIGS. 6 and 7 show examples of calculation results of the required torque (TQrq) given to the engine control unit 200 from the drive system manager 100, the first maximum torque (TQmax1), the second maximum torque (TQmax2), the first The calculation results of the required torque (TQrq1) and the second required torque (TQrq2) and the engine speed are shown in a time chart.
- the driver depresses the accelerator pedal at time t0.
- the accelerator pedal opening changes gently, whereas in the example shown in FIG. 7, the accelerator pedal opening changes at a high speed. That is, in the example shown in FIG. 6, the driver requests slow acceleration, and in the example shown in FIG. 6, the driver requests rapid acceleration.
- a damping torque for suppressing the pitching of the vehicle body is required from the sprung mass damping control system immediately after the driver operates the accelerator pedal.
- This damping torque is a torque that vibrates at a high frequency, and is included in the second required torque (TQrq2) and output.
- the first required torque (TQrq1) calculated based on the accelerator pedal opening does not exceed the first maximum torque (TQmax1) that can be realized only by operating the throttle 22. Furthermore, there is a sufficient margin between the first maximum torque (TQmax1) and the first required torque (TQrq1). Therefore, both the determination result in step S102 and the determination result in step S104 are affirmative, and the second required torque (TQrq2) that vibrates at a high frequency is superimposed on the first required torque (TQrq1) as it is. As a result, the engine control unit 200 is provided with a required torque (TQrq) that vibrates at a high frequency while increasing as the accelerator pedal opening increases.
- the required torque (TQrq) is within the torque range with the first maximum torque (TQmax1) as an upper limit
- the high-frequency vibration component of the required torque (TQrq) is realized by operating the throttle 22. Since the response speed of the torque with respect to the operation of the throttle 22 is fast, the internal combustion engine 20 outputs a torque including a required vibration component.
- the first required torque (TQrq1) calculated based on the accelerator pedal opening increases at a high speed and exceeds the first maximum torque (TQmax1) that can be realized only by operating the throttle 22.
- TQmax1 the first maximum torque
- the determination result of step S102 is negative, and the second required torque calculation unit 120
- the second required torque (TQrq2) that is finally output is set to zero. For this reason, in the period from the time point t1 to the time point t2, the final required torque (TQrq) is configured by only the first required torque (TQrq1).
- the second required torque (TQrq2) that vibrates at a high frequency is the second.
- the torque is output from the required torque calculation unit 130, and the second required torque (TQrq2) is superimposed on the first required torque (TQrq1).
- the required torque (TQrq) given after the time point t2 is within the torque range with the first maximum torque (TQmax1) as an upper limit, the required torque (TQrq) is given to the engine control unit 200, so that the required torque
- the high-frequency vibration component of (TQrq) is realized by the operation of the throttle 22 by the engine control unit 200.
- the transmission control unit 300 operates the automatic transmission 30 in accordance with the required gear ratio (GRrq) given from the drive system manager 100.
- the concept of the gear ratio includes a gear stage when the automatic transmission 30 is a stepped transmission.
- the drive system manager 100 includes a required gear ratio calculation unit 130.
- the required speed ratio calculating unit 130 includes a first maximum torque (TQmax1) presented from the first maximum torque calculating unit 220 of the engine control unit 200 and a first required torque calculated by the first required torque calculating unit 110 ( TQrq1) is input.
- the required gear ratio calculation unit 130 determines a required gear ratio (GRrq) to be given to the transmission control unit 300 based on various information.
- the first maximum torque (TQmax1) and the first required torque (TQrq1) are part of information used for determining the required transmission gear ratio (GRrq).
- step S202 it is determined whether or not the difference between the first maximum torque (TQmax1) and the first required torque (TQrq1) is less than a predetermined value ⁇ . If the determination result of step S202 is affirmative, step S204 is selected. When step S204 is selected, the required speed ratio calculation unit 130 increases the required speed ratio (GRrq) to be given to the transmission control unit 300 so that the automatic transmission 30 can downshift.
- step S202 the required speed ratio calculation unit 130 maintains the current required speed ratio (GRrq).
- step S202 it may be determined whether the ratio of the first maximum torque (TQmax1) to the first required torque (TQrq1) is less than a predetermined value. Whether the difference between the first maximum torque (TQmax1) and the first required torque (TQrq1) is less than a predetermined value has continued for a predetermined time, or the first maximum torque (TQmax1) with respect to the first required torque (TQrq1). It is also possible to determine whether or not the ratio of) is less than a predetermined value for a predetermined time.
- FIG. 9 and FIG. 10 show examples of the control results of the gear stage of the automatic transmission 30 and the calculation results of the first maximum torque (TQmax1), the second maximum torque (TQmax2), and the first required torque (TQrq1). It is shown in the time chart along with the engine speed.
- the driver depresses the accelerator pedal at time t0.
- the accelerator pedal opening changes gently, whereas in the example shown in FIG. 10, the accelerator pedal opening changes at a high speed. That is, in the example shown in FIG. 9, the driver requests slow acceleration, and in the example shown in FIG. 10, the driver requests rapid acceleration.
- the first required torque (TQrq1) calculated based on the accelerator pedal opening does not exceed the first maximum torque (TQmax1) that can be realized only by operating the throttle 22. Therefore, the determination result in step S202 described above is negative, and the required speed ratio (GRrq) given from the required speed ratio calculation unit 130 to the transmission control unit 300 is maintained even after the acceleration is started. As a result, the current gear stage is maintained as it is without changing the gear stage of the automatic transmission 30.
- the first required torque (TQrq1) calculated based on the accelerator pedal opening increases at a high speed and exceeds the first maximum torque (TQmax1) that can be realized only by operating the throttle 22. For this reason, in order to realize the first required torque (TQrq1), the operation of the waste gate valve 24 is required, and the increase in torque due to the turbo lag occurs.
- the determination result in step S204 described above becomes affirmative, and the required gear ratio calculation unit 130
- the required gear ratio (GRrq) given to the transmission control unit 300 is increased.
- the downshift operation of the automatic transmission 30 is performed by the transmission control unit 300, and the gear stage of the automatic transmission 30 is set lower by a predetermined stage than before acceleration.
- the engine speed is greatly increased by lowering the gear stage of the automatic transmission 30, and the turbo lag is eliminated by increasing the first maximum torque (TQmax1) accordingly.
- Embodiment 2 of the present invention will be described with reference to the drawings.
- FIG. 11 is a block diagram showing the configuration of the vehicle integrated control apparatus according to Embodiment 2 of the present invention.
- the vehicle integrated control device according to the present embodiment corresponds to a partially modified configuration of the vehicle integrated control device according to the first embodiment. For this reason, FIG. 11 shows only the configuration related to the differences from the vehicle integrated control apparatus according to the first embodiment.
- the required torque (TQrq) formed by superimposing the first required torque (TQrq1) and the second required torque (TQrq2) is transmitted from the drive system manager 100 to the engine control unit 200.
- the drive system manager 100 also gives the first required torque (TQrq1) to the engine control unit 200.
- FIG. 12 is a block diagram showing a configuration of the actuator operation unit 210 according to the present embodiment.
- the calculation element 211 calculates the required intake air amount (KLrq) from the required torque (TQrq), and the calculation element 212 calculates the required intake air pressure (KLrq) from the required intake air pressure (KLrq). PMrq) is calculated. Then, the target throttle opening (TA) is calculated from the required intake pipe pressure (PMrq) by the calculation element 212.
- the required intake air amount (KLrq1) is also calculated from the first required torque (TQrq1) by the calculation element 216.
- the required intake pipe pressure (PMrq1) is calculated from the required intake air amount (KLrq1) by the calculation element 217.
- the required intake pipe pressure (PMrq1) calculated by the calculation element 217 is input to the calculation element 214, and the target wastegate valve duty (WGV) is calculated based on the required intake pipe pressure (PMrq1).
- the required intake air amount (KLrq1) calculated by the calculation element 216 is input to the calculation element 215, and the target valve timing (VVT) is calculated based on the required intake air amount (KLrq1).
- the required intake air amount (KLrq) and the required intake pipe pressure (PMrq) calculated based on the required torque (TQrq) include a component corresponding to the torque component with a fast changing speed included in the required torque (TQrq). Yes.
- the required intake air amount (KLrq1) and the required intake pipe pressure (PMrq1) calculated based on the first required torque (TQrq1) do not include such a component with a fast changing speed. Therefore, by operating the wastegate valve 24 and the valve timing variable device 26 according to the target wastegate valve duty (WGV) and the target valve timing (VVT) determined based on these, the useless movement of these actuators is suppressed. be able to.
- Embodiment 3 FIG. Next, Embodiment 3 of the present invention will be described with reference to the drawings.
- FIG. 13 is a block diagram showing a configuration of a vehicle integrated control apparatus according to Embodiment 3 of the present invention.
- the vehicle integrated control device according to the present embodiment corresponds to a partially modified configuration of the vehicle integrated control device according to the first embodiment. For this reason, FIG. 13 shows only the configuration related to the difference from the vehicle integrated control apparatus according to the first embodiment.
- the drive system manager 100 gives the first request torque (TQrq1) and the second request torque (TQrq2) separately to the engine control unit 200.
- the actuator operation unit 210 of the engine control unit 200 calculates a required torque (TQrq) obtained by superimposing the given first required torque (TQrq1) and the second required torque (TQrq2), and the method according to the first embodiment
- the target throttle opening (TA), the target wastegate valve duty (WGV), and the target valve timing (VVT) are calculated from the required torque (TQrq) by the same method.
- the target throttle opening (TA) is calculated from the required torque (TQrq) by a method similar to the method according to the second embodiment, and the target wastegate valve duty (WGV) and the target are calculated from the first required torque (TQrq1). Calculate valve timing (VVT).
- valve timing varying device provided in the internal combustion engine in the above-described embodiment is not essential in the present invention. It suffices that the internal combustion engine includes at least a throttle and a turbocharger with a wastegate valve.
- the vehicle integrated control apparatus includes not only an internal combustion engine having a turbocharger with a wastegate valve, but also an internal combustion engine having a variable displacement turbocharger and a mechanical supercharger with an electromagnetic clutch.
- the present invention can also be applied to an internal combustion engine having an electric motor or an electric supercharger.
- any internal combustion engine having a supercharger with a control device for controlling the rotation speed of the compressor can be a control target of the vehicle integrated control apparatus according to the present invention.
- the throttle is regarded as the first actuator and the supercharger with the control device is regarded as the second actuator.
- the first actuator and the second actuator in the vehicle integrated control apparatus according to the present invention are not limited to a combination of a throttle and a supercharger with a control device.
- the intake control valve is regarded as a first actuator and the throttle is regarded as a second actuator.
- the intake valve is an intake valve having a variable lift or operating angle
- the intake valve is regarded as a first actuator and the throttle is regarded as a second actuator, and the vehicle integrated control device according to the present invention is applied. be able to.
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Abstract
Description
以下、本発明の実施の形態1について図を参照して説明する。
次に、本発明の実施の形態2について図を用いて説明する。
次に、本発明の実施の形態3について図を用いて説明する。
本発明は上述の実施の形態に限定されるものではなく、本発明の趣旨を逸脱しない範囲で種々変形して実施することができる。例えば、上述の実施の形態において内燃機関が備えるバルブタイミング可変装置は本発明においては必須ではない。少なくともスロットルとウエストゲートバルブ付きのターボ過給機とが内燃機関に備えられていればよい。
20 内燃機関
22 スロットル
24 ウエストゲートバルブ
26 バルブタイミング可変装置
28 エンジン回転数センサ
30 自動変速機
100 駆動系マネージャ
110 第1要求トルク演算ユニット
120 第2要求トルク演算ユニット
130 要求変速比演算ユニット
200 エンジン制御ユニット
210 アクチュエータ操作ユニット
220 第1最大トルク演算ユニット
230 第2最大トルク演算ユニット
300 変速機制御ユニット
Claims (15)
- 吸気通路の第1の位置に設けられて前記第1の位置の下流の圧力に作用する第1のアクチュエータと、前記吸気通路の第1の位置よりも上流の第2の位置に設けられて前記第2の位置の下流の圧力に作用する第2のアクチュエータとを有する内燃機関を動力源として備えた車両の統合制御装置において、
車両の駆動系全体の運転を管理する駆動系マネージャと、
前記内燃機関を制御するエンジン制御ユニットと、を備え、
前記エンジン制御ユニットは、
前記駆動系マネージャから与えられる要求トルクに基づいて前記第1のアクチュエータと前記第2のアクチュエータとを操作するアクチュエータ操作ユニットと、
前記第2のアクチュエータの操作量は能動的に変更せず前記第1のアクチュエータの操作量のみを能動的に変更した場合に実現できる第1の最大トルクをエンジン回転数に基づいて算出し、該第1の最大トルクを前記駆動系マネージャに対して提示する第1最大トルク演算ユニットと、
前記第1のアクチュエータの操作量と前記第2のアクチュエータの操作量の両方を能動的に変更した場合に実現できる第2の最大トルクをエンジン回転数に基づいて算出し、該第2の最大トルクを前記駆動系マネージャに対して提示する第2最大トルク演算ユニットと、を備え、
前記駆動系マネージャは、前記エンジン制御ユニットから提示される前記第1の最大トルク及び前記第2の最大トルクを参照して、前記エンジン制御ユニットに与える要求トルクを決定することを特徴とする車両統合制御装置。 - 前記駆動系マネージャは、
前記第2の最大トルクを参照して第1の要求トルクを算出する第1要求トルク演算ユニットと、
前記第1の最大トルクと前記第1の要求トルクとを参照して前記第1の要求トルクよりも変化速度の速いトルク成分である第2の要求トルクを算出する第2要求トルク演算ユニットと、
を備えることを特徴とする請求項1に記載の車両統合制御装置。 - 前記第1要求トルク演算ユニットは、前記第2の最大トルクを超えない範囲に第1の要求トルクの大きさを調整することを特徴とする請求項2に記載の車両統合制御装置。
- 前記第2要求トルク演算ユニットは、前記第1の要求トルクに対する前記第1の最大トルクの余裕を超えない範囲に第2の要求トルクの大きさを調整することを特徴とする請求項2に記載の車両統合制御装置。
- 前記第1要求トルク演算ユニットは、運転者からの要求に基づいて前記第1の要求トルクを生成することを特徴とする請求項2又は3に記載の車両統合制御装置。
- 前記第2要求トルク演算ユニットは、バネ上制振制御システム、変速機制御ユニット、及び、車両姿勢安定制御システムのうち少なくとも1つからの要求に基づいて前記第2の要求トルクを生成することを特徴とする請求項2又は4に記載の車両統合制御装置。
- 前記駆動系マネージャは、前記第1の要求トルクに前記第2の要求トルクを重ね合わせて1つの信号を生成し、該1つの信号を前記エンジン制御ユニットに与えることを特徴とする請求項2乃至6の何れか1項に記載の車両統合制御装置。
- 前記駆動系マネージャは、前記第1の要求トルクに前記第2の要求トルクを重ね合わせた信号と前記第1の要求トルクを表す信号とを生成し、それら2つの信号を前記エンジン制御ユニットに与えることを特徴とする請求項2乃至6の何れか1項に記載の車両統合制御装置。
- 前記駆動系マネージャは、前記第1の要求トルクを表す信号と前記第2の要求トルクを表す信号とを生成し、それら2つの信号を前記エンジン制御ユニットに与えることを特徴とする請求項2乃至6の何れか1項に記載の車両統合制御装置。
- 前記車両統合制御装置は、前記駆動系マネージャから与えられる要求変速比に従って自動変速機を制御する変速機制御ユニットをさらに備え、
前記駆動系マネージャは、前記変速機制御ユニットに与える前記要求変速比を決定する要求変速比演算ユニットをさらに備え、
前記要求変速比演算ユニットは、前記第1の最大トルクと前記第1の要求トルクとの差或いは比に関する所定の条件が満たされた場合に、前記要求変速比を現在よりも高い変速比に変更することを特徴とする請求項2乃至9の何れか1項に記載の車両統合制御装置。 - 前記駆動系マネージャは、前記エンジン制御ユニットに与える要求トルクに変化速度の速いトルク成分を含ませる場合には、前記第1の最大トルクを超えない範囲に前記要求トルクの大きさを調整し、前記エンジン制御ユニットに与える要求トルクに変化速度の遅いトルク成分のみを含ませる場合には、前記第2の最大トルクを超えない範囲に前記要求トルクの大きさを調整することを特徴とする請求項1に記載の車両統合制御装置。
- 前記第1のアクチュエータは、前記第1の位置の上流の圧力に対して下流の圧力を減少させるように作用するアクチュエータであり、
前記第2のアクチュエータは、前記第2の位置の上流の圧力に対して下流の圧力を上昇させるように作用するアクチュエータであることを特徴とする請求項1乃至11の何れか1項に記載の車両統合制御装置。 - 前記第2のアクチュエータは、その動作に対する前記第2の位置の下流の圧力の変化速度が前記第1のアクチュエータの動作に対する前記第1の位置の下流の圧力の変化速度よりも遅いアクチュエータであることを特徴とする請求項1乃至12の何れか1項に記載の車両統合制御装置。
- 前記第1のアクチュエータは、スロットルであり、
前記第2のアクチュエータは、コンプレッサの回転数を制御する制御デバイス付きの過給機であることを特徴とする請求項12又は13に記載の車両統合制御装置。 - 前記第2のアクチュエータは、ウエストゲートバルブ付きのターボ過給機であることを特徴とする請求項14に記載の車両統合制御装置。
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CN201280074309.4A CN104411954B (zh) | 2012-06-28 | 2012-06-28 | 车辆综合控制装置 |
US14/410,341 US9133781B2 (en) | 2012-06-28 | 2012-06-28 | Vehicle integrated control device |
EP12880196.6A EP2868906B1 (en) | 2012-06-28 | 2012-06-28 | Vehicle integrated control device |
PCT/JP2012/066573 WO2014002230A1 (ja) | 2012-06-28 | 2012-06-28 | 車両統合制御装置 |
JP2014522308A JP5999180B2 (ja) | 2012-06-28 | 2012-06-28 | 車両統合制御装置 |
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EP2868906B1 (en) | 2019-06-05 |
CN104411954B (zh) | 2017-02-22 |
JPWO2014002230A1 (ja) | 2016-05-26 |
US9133781B2 (en) | 2015-09-15 |
JP5999180B2 (ja) | 2016-09-28 |
CN104411954A (zh) | 2015-03-11 |
US20150134214A1 (en) | 2015-05-14 |
EP2868906A4 (en) | 2016-03-02 |
EP2868906A1 (en) | 2015-05-06 |
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