WO2016203634A1 - 内燃エンジンの燃料噴射制御装置及び制御方法 - Google Patents
内燃エンジンの燃料噴射制御装置及び制御方法 Download PDFInfo
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- WO2016203634A1 WO2016203634A1 PCT/JP2015/067691 JP2015067691W WO2016203634A1 WO 2016203634 A1 WO2016203634 A1 WO 2016203634A1 JP 2015067691 W JP2015067691 W JP 2015067691W WO 2016203634 A1 WO2016203634 A1 WO 2016203634A1
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- 238000002347 injection Methods 0.000 title claims abstract description 316
- 239000007924 injection Substances 0.000 title claims abstract description 316
- 239000000446 fuel Substances 0.000 title claims abstract description 142
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 62
- 238000000034 method Methods 0.000 title claims description 10
- 230000006835 compression Effects 0.000 claims description 22
- 238000007906 compression Methods 0.000 claims description 22
- 238000010926 purge Methods 0.000 claims description 14
- 230000007246 mechanism Effects 0.000 claims description 12
- 239000002828 fuel tank Substances 0.000 claims description 3
- 230000008569 process Effects 0.000 description 7
- 230000009467 reduction Effects 0.000 description 6
- 230000007423 decrease Effects 0.000 description 4
- 230000002000 scavenging effect Effects 0.000 description 4
- 239000003502 gasoline Substances 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 239000003054 catalyst Substances 0.000 description 1
- 230000003197 catalytic effect Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000000994 depressogenic effect Effects 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 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
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/04—Introducing corrections for particular operating conditions
- F02D41/045—Detection of accelerating or decelerating state
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D15/00—Varying compression ratio
- F02D15/02—Varying compression ratio by alteration or displacement of piston stroke
-
- 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
- F02D41/12—Introducing corrections for particular operating conditions for deceleration
-
- 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
- F02D41/24—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means
- F02D41/26—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using computer, e.g. microprocessor
- F02D41/263—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using computer, e.g. microprocessor the program execution being modifiable by physical parameters
-
- 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
- F02D41/30—Controlling fuel injection
- F02D41/3094—Controlling fuel injection the fuel injection being effected by at least two different injectors, e.g. one in the intake manifold and one in the cylinder
-
- 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
- F02D41/30—Controlling fuel injection
- F02D41/32—Controlling fuel injection of the low pressure type
- F02D41/34—Controlling fuel injection of the low pressure type with means for controlling injection timing or duration
-
- 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
- F02D41/30—Controlling fuel injection
- F02D41/38—Controlling fuel injection of the high pressure type
- F02D41/40—Controlling fuel injection of the high pressure type with means for controlling injection timing or duration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D43/00—Conjoint electrical control of two or more functions, e.g. ignition, fuel-air mixture, recirculation, supercharging or exhaust-gas treatment
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D43/00—Conjoint electrical control of two or more functions, e.g. ignition, fuel-air mixture, recirculation, supercharging or exhaust-gas treatment
- F02D43/04—Conjoint electrical control of two or more functions, e.g. ignition, fuel-air mixture, recirculation, supercharging or exhaust-gas treatment using only digital means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2250/00—Engine control related to specific problems or objectives
- F02D2250/31—Control of the fuel pressure
-
- 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
- F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D41/003—Adding fuel vapours, e.g. drawn from engine fuel reservoir
- F02D41/0032—Controlling the purging of the canister as a function of the engine operating conditions
-
- 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
- Y02T10/40—Engine management systems
Definitions
- the present invention relates to fuel injection control during deceleration of an internal combustion engine that includes a direct injection injector that directly injects fuel into a combustion chamber and a port injection injector that injects fuel into an intake port.
- GDI gasoline direct injection
- MPI multipoint injection
- JP2013-036447A proposes fuel injection control for an internal combustion engine for a vehicle equipped with both a direct injection injector and a port injection injector. Specifically, in the low load operation region (first execution region) of the internal combustion engine, fuel injection is performed only by the port injector, and in the operation region (second execution region) on the higher load side than the first execution region, the fuel injection is performed directly. Fuel injection is performed by the injector. Specifically, in the low load region where the engine load is relatively small in the second execution region, both the fuel injection from the port injector and the fuel injection from the direct injector are executed, and in the high load region where the engine load is high, the direct injection is performed. Only fuel injection from the injector is performed.
- the object of the present invention is to quickly reduce the fuel pressure of the direct injection injector in the deceleration state.
- the present invention provides a fuel injection control device for an internal combustion engine comprising a port injection injector for injecting fuel into an intake port and a direct injection injector for injecting fuel into a combustion chamber.
- the fuel injection control device includes a sensor that detects an operating condition of the internal combustion engine and a programmable controller.
- the controller is programmed to inject fuel into the port injector and direct injector based on operating conditions.
- the controller is further programmed to increase the injection amount of the direct injection injector when the internal combustion engine is decelerated, rather than the normal injection amount of the direct injection injector.
- FIG. 1 is a schematic configuration diagram of a fuel injection control apparatus according to an embodiment of the present invention.
- FIG. 2 is a flowchart illustrating a fuel injection control routine for deceleration of the internal combustion engine executed by the engine controller according to the embodiment of the present invention.
- FIG. 3 is a flowchart for explaining a purge valve closing and compression ratio lowering subroutine executed in the deceleration fuel injection control routine.
- FIG. 4 is a diagram showing the contents of a map relating to the use area of gasoline direct injection (GDI) and multipoint injection (MPI) stored in the engine controller.
- FIG. 5A-5F are timing charts for explaining the execution results when the engine controller executes the deceleration fuel injection control routine.
- FIG. 6A to 6F are timing charts for explaining other execution results when the engine controller executes the deceleration fuel injection control routine.
- an internal combustion engine 1 for an automobile is composed of a 4-stroke cycle turbocharged multi-cylinder spark ignition internal combustion engine having a variable compression ratio mechanism 2 using a multi-link type piston crank mechanism.
- the internal combustion engine 1 includes an intake valve 4, an exhaust valve 5, a direct injection injector 8, and a spark plug 6 facing the combustion chamber 3.
- the intake valve 4 is configured such that its opening / closing timing can be changed by a variable mechanism (not shown).
- the direct injection injector 8 is provided facing each combustion chamber 3 as a main fuel injection valve, and directly injects fuel into the combustion chamber 3.
- Each combustion chamber 3 is connected to an intake port 7 via an intake valve 4 and an exhaust port 11 via an exhaust valve 5.
- the intake port 7 is provided with a port injection injector 9 as an auxiliary fuel injection valve.
- the direct injection injector 8 and the port injection injector 9 are composed of electromagnetic or piezoelectric injection valves that open in response to a pulse width signal output from the engine controller 41, and an amount of fuel proportional to the pulse width of the pulse width signal. Inject.
- the intake port 7 is connected to an intake collector 18a and an intake passage 18 via an intake manifold.
- the intake passage 18 upstream of the intake collector 18a is provided with an electronically controlled throttle 19 whose opening degree is controlled by a control signal from the engine controller 41.
- a turbocharger compressor 20 is provided in the intake passage 18 upstream of the throttle 19. Further, an air flow meter 10 that detects the amount of intake air is disposed in the intake passage 18 upstream of the compressor 20.
- a purge valve 50 for joining the evaporated fuel in the fuel tank to the intake air is connected to the intake collector 18a.
- the exhaust port 11 is connected to an exhaust passage 12 through an exhaust manifold and an exhaust collector.
- a catalytic converter 13 made of a three-way catalyst and a turbine (not shown) are interposed in the exhaust passage 12.
- the engine controller 41 includes a microcomputer having a central processing unit (CPU), a read-only memory (ROM), a random access memory (RAM), and an input / output interface (I / O interface). It is also possible to configure the controller with a plurality of microcomputers.
- CPU central processing unit
- ROM read-only memory
- RAM random access memory
- I / O interface input / output interface
- the engine controller 41 includes a crank angle sensor 42 that detects engine rotation speed, an accelerator pedal depression amount sensor 44 that detects the depression amount of an accelerator pedal operated by a vehicle driver, and an idle switch 46 that detects idle operation of the internal combustion engine 1. Are connected by signal circuits.
- the engine controller 41 controls the fuel injection amount and the injection timing of the direct injection injector 8 and the injection injector 9 based on these detection signals.
- the engine controller 41 controls the ignition timing of the spark plug 6, the opening degree of the throttle 19, the compression ratio of the internal combustion engine 1 via the compression ratio variable mechanism 2, and the opening / closing of the purge valve 50.
- the variable compression ratio mechanism 2 is configured by a known multi-link piston crank mechanism. Specifically, the compression ratio variable mechanism 2 includes a lower link 22, an upper link 25, and a control link 27.
- the lower link 22 is rotatably supported by the crankpin 21a of the crankshaft 21.
- the upper link 25 connects the upper pin 23 engaged with one end of the lower link 22 and the piston pin 24 a of the piston 24.
- One end of the control link 27 is connected to the control pin 26 engaged with the other end of the lower link 22, and the other end is supported by the control shaft 28 so as to be swingable.
- the crankshaft 21 and the control shaft 28 are rotatably supported in a crankcase below the cylinder block 29 via a bearing structure.
- the control shaft 28 has an eccentric shaft 28a.
- the end of the control link 27 is rotatably fitted to the eccentric shaft 28a.
- the variable compression ratio mechanism 2 changes the compression ratio of the internal combustion engine 1 by moving the top dead center position of the piston 24 up and down as the control shaft 28
- an electric motor 31 having a rotating shaft parallel to the crankshaft 21 is disposed below the cylinder block 29.
- a reduction gear 32 is connected to the electric motor 31.
- the output shaft 32 a of the reduction gear 32 is arranged coaxially with the output shaft of the electric motor 31.
- the output shaft 32a of the reduction gear 32 and the control shaft 28 are parallel to each other.
- An intermediate link 35 connects the first arm 33 fixed to the output shaft 32a and the second arm 34 fixed to the control shaft 28 so that both rotate in conjunction with each other.
- the rotation of the electric motor 31 is decelerated to the reduction gear 32 and then output to the reduction gear output shaft 32a.
- the rotational displacement of the reduction gear output shaft 32a is transmitted from the first arm 33 to the second arm 34 via the intermediate link 35, and the control shaft 28 is rotationally displaced. Thereby, the compression ratio of the internal combustion engine 1 changes.
- the target compression ratio of the variable compression ratio mechanism 2 is set in the engine controller 41 based on engine operating conditions typified by engine load and engine speed.
- the engine controller 41 controls the drive of the electric motor 31 so that the target compression ratio is achieved.
- direct gasoline injection (GDI) of the direct injection injector 8 and multipoint injection (MPI) by the port injection injector 9 are performed. Both are fuel injections performed for each cylinder.
- FIG. Reference numeral 4 denotes an application area in normal operation of GDI and MPI set according to the engine speed and the engine load, and the classification of the area depends on the specifications of the internal combustion engine 1.
- FIG. 4 only GDI is applied in the low load region and high load and low rotation speed region of the engine, and GDI and MPI are used in other cases.
- the required fuel injection amount is small, and when GDI and MPI are used together, either the direct injection injector 8 or the port injection injector 9 falls below the minimum injection amount Qmin, so only GDI Has been applied.
- the maximum value of the injection amount is represented by Qmax, and the minimum value of the injection amount is represented by Qmin.
- the opening periods of the intake valve and the exhaust valve are overlapped, and the fresh air flowing from the intake port 7 is directly used as the scavenging gas as the exhaust port 11.
- the rotational speed of the turbine is increased by utilizing a so-called scavenging effect that blows through the engine, but if the MPI by the port injector 9 is passed at this time, the injected fuel from the port injector 9 can be discharged from the exhaust valve 5 Only GDI is applied.
- MPI is injected with the minimum injection amount Qmin that can be injected from the port injector 9, and the shortage is injected from the direct injector 8.
- the reason why the injection is performed from the port injector 9 with the minimum injection amount Qmin is to prevent the port injector 9 from being clogged.
- the maximum injection amount Qmax that can be injected by the direct injection injector 8 from GDI.
- the shortage is injected from the port injector 9.
- both the direct injection injector 8 and the port injection injector 9 are opened over a time corresponding to the pulse width of the injection pulse width signal output by the engine controller 41.
- An amount of fuel proportional to the pulse width is injected.
- Fuel is supplied to the direct injection injector 8 from a common rail.
- the fuel pressure of the common rail generally increases as the load increases, that is, as the fuel injection amount increases.
- the prior art injects fuel from both a direct injection injector and a port injection injector in a deceleration state from a high load.
- the engine controller 41 is used to reduce the fuel pressure applied to the direct injection injector 9 when the internal combustion engine 1 is decelerated.
- the deceleration fuel injection control routine shown in FIG. This routine is repeatedly executed at a constant cycle of, for example, 10 milliseconds while the vehicle is traveling.
- the fuel injection amounts of the direct injection injector 8 and the port injection injector 9 are controlled by an injection pulse width signal that is individually output from the engine controller 41 to these injectors.
- This deceleration fuel injection control routine does not calculate the required fuel injection amount itself. It is assumed that the fuel injection amount required by the internal combustion engine 1 is calculated by another routine based on the operating conditions of the internal combustion engine 1. This deceleration fuel injection control routine determines how the required fuel injection amount is calculated and then allocated to GDI and MPI.
- step S1 the engine controller 41 determines whether or not the internal combustion engine 1 is decelerating. Specifically, it is determined whether or not the input signal from the idle switch 46 is ON. When the idle switch 46 is ON, it means that the accelerator pedal of the vehicle is not depressed and the internal combustion engine 1 is decelerating. When the idle switch 4 is ON, the engine controller 41 performs the processes after step S2. If the idle switch 4 is not ON, the internal combustion engine 1 is not decelerating, and the engine controller 41 immediately ends the routine.
- the engine controller 41 reads the fuel injection amount calculated in another routine.
- step S3 the engine controller 41 determines whether the required fuel injection amount is equal to or less than the maximum value Qmax of the GDI injection amount.
- the injection amount of the direct injection injector 8 is synonymous with the injection amount of GDI.
- the injection amount of the port injector 9 is synonymous with the injection amount of MPI.
- the engine controller 41 executes injection by only GDI in step S8. Specifically, an injection pulse width signal corresponding to the injection amount is output from the engine controller 41 to the direct injection injector 8. On the other hand, the engine controller 41 does not output an injection pulse width signal to the port injector 9.
- step S9 the engine controller 41 completes the routine after executing the purge valve closing and compression ratio lowering subroutine.
- the purge valve closing and compression ratio lowering subroutine execution is one of the optional options for the present invention and is not an essential requirement. This subroutine will be described later.
- step S3 the engine controller 41 determines whether the fuel injection amount requested in step S4 exceeds the sum of the maximum value Qmax of the GDI injection amount and the minimum value Qmin of the MPI injection amount. Determine.
- the engine controller 41 performs GDI at the maximum value Qmax of the injection amount in step S5.
- the shortage with respect to the required injection amount is compensated by MPI injection.
- the engine controller 41 outputs an injection pulse width signal corresponding to the maximum value Qmax of the GDI injection amount to the direct injection injector 8, and outputs an injection pulse width signal corresponding to the shortage to the port injector 9. Output.
- the engine controller 41 ends the routine.
- step S4 determines whether the required injection amount is less than or equal to the sum of the maximum value Qmax of the GDI injection amount and the minimum value Qmin of the MPI injection amount. If the determination in step S4 is negative, that is, if the required injection amount is less than or equal to the sum of the maximum value Qmax of the GDI injection amount and the minimum value Qmin of the MPI injection amount, the port injector 9 is turned on in step S7. Injection is performed at the minimum value Qmin of the injection amount. Further, the direct injection injector 8 is caused to inject a difference between the required injection amount and the minimum value Qmin of the injection amount of the port injector 9. After the process of step S7, the engine controller 41 ends the routine.
- this deceleration fuel injection control routine when the required injection amount becomes less than Qmax of GDI, the injection of the port injection injector 9 is stopped, and the injection by only GDI is executed in step S8, whereby the direct injection injector The fuel pressure drop of 8 is preferentially performed.
- FIG. 1 The purge valve stop and compression ratio lowering subroutine will be described with reference to FIG.
- step S21 the engine controller 41 determines whether the required fuel injection amount is below the minimum value Qmin of the GDI injection amount.
- the engine controller 41 increases the required fuel injection amount by performing steps S22 and S23.
- step S22 the purge valve 50 is closed.
- the purge valve 50 constitutes an evaporated fuel purge system that merges the evaporated fuel in the fuel tank with the intake air.
- the required fuel injection amount is reduced accordingly. Therefore, by closing the purge valve 50, the operation of the evaporated fuel purge system is stopped, and the required fuel injection amount is increased.
- step S23 the compression ratio of the internal combustion engine 1 is lowered via the compression ratio variable mechanism 2.
- a decrease in the compression ratio results in a decrease in thermal efficiency, resulting in an increase in the required fuel injection amount.
- steps S22 and S23 both increase the required fuel injection amount.
- the chance of GDI injection by the direct injection injector 8 increases, and the fuel pressure applied to the direct injection injector 8 can be reduced.
- FIG. 5A-5F is shown in FIG. This corresponds to Case 1 of 4.
- FIG. 5C when the idle switch is switched from Off to On at time t1, the fuel injection control routine for deceleration is substantially operated. This timing corresponds to the start of deceleration in the figure.
- the fuel injection amount required at the start of deceleration is less than or equal to the GDI maximum value Qmax by the direct injection injector 8, so the total amount of fuel injection required is performed by GDI by the direct injection injector 8.
- FIG. 5E the pulse width of the injection pulse width signal output from the engine controller 41 to the direct injection injector 8 decreases, and the corresponding FIG. 5B engine torque, FIG. The engine speed shown in 5A decreases. In this way, the GDI by the direct injection injector 8 is continued, and the FIG. As shown to 5D, the fuel pressure of the direct injection injector 8 falls.
- FIG. 1 In the map of 4, in the deceleration pattern of Case 1, the GDI and MPI combined region passes during deceleration. According to the fuel injection control routine during deceleration, the engine controller 41 executes only GDI by the direct injection injector 8 by repeatedly executing steps S8 and S9 in this case as well. As a result, the fuel pressure of the direct injection injector 8 can be quickly reduced.
- Fig. The broken line shown by 5D-5F shows the fuel injection pattern during deceleration when the fuel injection control routine during deceleration is not performed.
- FIG. 1 When the engine speed and the engine load enter the GDI + MPI region in the map of 4, the GDI by the direct injection injector 8 and the MPI by the port injection injector 9 are used together.
- the amount of MPI injection by the port injector 9 is _FIG.
- the port injector 9 continues to inject at the minimum value Qmin of the injection amount even after it has decreased to the minimum value Qmin. The remainder of the required fuel injection amount is injected by GDI by the direct injection injector 8. Therefore, FIG.
- the fuel injection pulse width output to the direct injection injector 8 is shortened by an amount corresponding to the minimum value Qmin of the MPI by the port injection injector 9. As a result, FIG. As shown to 5D, the fuel pressure of the direct injection injector 8 also becomes difficult to fall.
- the FIG. In the fuel injection pattern for deceleration when not using the fuel injection control routine for deceleration, the FIG.
- the MPI by the port injector 9 stops and only the GDI by the direct injector 8 is executed again.
- This region is shown in FIG. As shown in 5E and 5F, this corresponds to the case where the amount of GDI injected by the direct injection injector 8 falls below the minimum value Qmin at time t5. In this region, MPI by the port injector 9 is stopped and only GDI by the direct injector 8 is performed.
- FIG. 1 In the internal combustion engine that performs fuel injection according to the map of FIG. 4, in the case of Case 1, the fuel pressure of the direct injection injector 8 can be quickly reduced by executing the deceleration fuel injection control routine according to the present embodiment.
- TLS is an abbreviation for Total Lean Scavenging. This is because, by overlapping the opening periods of the intake valve and the exhaust valve, the fresh air flowing in from the intake port 7 is blown out as it is to the exhaust port 11 as a scavenging gas, so that the rotational speed of the turbine is controlled. It means control of valve timing to increase. During the valve timing control, if MPI by the port injection injector 9 is passed, MPI injection fuel may be discharged from the exhaust valve in relation to the injection timing, so only GDI injection is performed. At time t2, TLS is stopped and returned to normal valve timing.
- FIG. 6A-6F is FIG. It corresponds to Case 2 of 4.
- FIG. 6C when the idle switch is switched from Off to On at time t1, the fuel injection control routine for deceleration is substantially operated. This timing corresponds to the start of deceleration in the figure.
- the fuel injection amount required at the start of deceleration exceeds the GDI maximum value Qmax by the direct injection injector 8, so FIG.
- the determination in step S3 of 2 is negative.
- the engine controller 41 determines in FIG.
- the maximum value Qmax of the GDI injection amount is injected into the direct injection injector 8, and FIG.
- the remaining fuel is injected into the port injector 9 as shown at 6F.
- the fuel pressure of the direct injection injector 8 can be efficiently reduced by performing GDI injection to the maximum while satisfying the required injection amount.
- step S4 When the required injection amount becomes equal to the sum of the maximum value Qmax of the GDI injection amount and the minimum value Qmin of the MPI injection amount, the determination in step S4 turns negative.
- FIG. The time t3 of 6A corresponds to this.
- the engine controller 41 determines in FIG. As shown in 6F, MPI is performed with the minimum value Qmin.
- step S3 If the determination in step S3 turns positive at time t4, the engine controller 41 thereafter repeats the processes in steps S8 and S9. As a result, FIG. As shown in 6F, MPI injection is stopped and all of the required injection amount is injected by GDI until the fuel injection amount becomes zero. As a result, FIG. As shown in 6D, the fuel pressure of the direct injection injector 8 can be quickly reduced.
- the GDI and MPI combined region MPI is injected with the minimum value Qmin and the shortage is GDI
- the engine controller is also used in this case. 41 repeats steps S8 and S9 to execute only GDI by the direct injection injector 8. As a result, the fuel pressure of the direct injection injector 8 can be quickly reduced.
- FIG. 6D-6F The broken line indicated by 6D-6F indicates the result of the fuel injection control during deceleration when the fuel injection control routine during deceleration is not performed. Also in this case, fuel injection is performed in the same pattern as when the deceleration time fuel injection control routine is executed until time t4. After time t4, substantially the same control as in Case 1 is performed. That is, FIG. Since the engine rotational speed and the engine load are in the region of GDI + MPI in the map of 4, the GDI by the direct injection injector 8 and the MPI by the port injection injector 9 are used together, and the port injection injector 9 continues injection at the minimum injection amount Qmin. . The remainder of the required fuel injection amount is injected by GDI by the direct injection injector 8. Therefore, FIG.
- the fuel injection pulse width output to the direct injection injector 8 is shortened by an amount corresponding to the MPI minimum value Qmin by the port injector 9. As a result, FIG. As shown to 6D, the fuel pressure of the direct injection injector 8 also becomes difficult to fall.
- the fuel pressure of the direct injection injector 8 can be quickly reduced by executing the deceleration fuel injection control routine according to the present embodiment.
- the above embodiment is an embodiment in which the present invention is applied to the internal combustion engine 1 in which the main injection is performed by the direct injection injector 8 and the secondary injection is performed by the port injection injector 9.
- the present invention can also be applied to an internal combustion engine in which main injection is performed by a port injection injector and sub-injection is performed by a direct injection injector.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Computer Hardware Design (AREA)
- Microelectronics & Electronic Packaging (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Fuel-Injection Apparatus (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Supplying Secondary Fuel Or The Like To Fuel, Air Or Fuel-Air Mixtures (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
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Description
Claims (9)
- 吸気ポートに燃料を噴射するポート噴射インジェクタと燃焼室に燃料を噴射する直噴インジェクタを備えた内燃エンジンの燃料噴射制御装置において:
内燃エンジンの運転条件を検出するセンサと;
次のようにプログラムされたプログラマブルコントローラ:
運転条件に基づき
ポート噴射インジェクタと直噴インジェクタに燃料を噴射させ;
内燃エンジンの減速時に直噴インジェクタの噴射量を通常時の直噴インジェクタの噴射量よりも増加させる、と
を備える、燃料噴射制御装置。 - コントローラは、内燃エンジンの減速時にポート噴射インジェクタの噴射を停止し、直噴インジェクタのみで噴射させるようにさらにプログラムされる、請求項1の燃料噴射制御装置。
- コントローラは、内燃エンジンの減速時において要求される噴射量が直噴インジェクタの最大噴射量以下の場合に直噴インジェクタの噴射量を増加させるようにさらにプログラムされる、請求項1または2の燃料噴射制御装置。
- コントローラは、内燃エンジンの減速時において要求される噴射量が直噴インジェクタの最大噴射量を上回る場合には、直噴インジェクタの噴射量を直噴インジェクタの最大噴射量に設定し、要求される噴射量の残りをポート噴射インジェクタの噴射量に設定するようにさらにプログラムされる、請求項1から3いずれかの燃料噴射制御装置。
- コントローラは、内燃エンジンの減速時において要求される噴射量がポート噴射インジェクタの最小噴射量と直噴インジェクタの最大噴射量との合計以下の場合には、ポート噴射インジェクタの噴射量をポート噴射インジェクタの最小噴射量に設定し、要求される噴射量の残りを直噴インジェクタの噴射量に設定するようにさらにプログラムされる、請求項4の燃料噴射制御装置。
- 内燃エンジンは燃料タンク内の蒸発燃料を吸気に合流させるパージバルブを備え、コントローラは、内燃エンジンの減速時において要求される噴射量が直噴インジェクタの最小噴射量を下回る場合には、パージバルブを閉鎖するようにさらにプログラムされる、請求項1から5のいずれかの燃料噴射制御装置。
- 内燃エンジンは圧縮比を変化させる圧縮比可変機構を備え、コントローラは、内燃エンジンの減速時において要求される噴射量が直噴インジェクタの最小噴射量を下回る場合には、圧縮比可変機構を介して圧縮比を低下させるようにさらにプログラムされる、請求項1から6のいずれかの燃料噴射制御装置。
- 吸気ポートに燃料を噴射するポート噴射インジェクタと燃焼室に燃料を噴射する直噴インジェクタを備えた内燃エンジンの燃料噴射制御装置において:
内燃エンジンの運転条件を検出する手段と;
運転条件に基づきポート噴射インジェクタと直噴インジェクタに燃料を噴射させる手段と;
内燃エンジンの減速時に、直噴インジェクタの噴射量を通常時の直噴インジェクタの噴射量よりも増加させる手段と、
を備える、燃料噴射制御装置。 - 吸気ポートに燃料を噴射するポート噴射インジェクタと燃焼室に燃料を噴射する直噴インジェクタを備えた内燃エンジンの燃料噴射制御方法において:
内燃エンジンの運転条件を検出し;
運転条件に基づきポート噴射インジェクタと直噴インジェクタに燃料を噴射させ;
内燃エンジンの減速時に、直噴インジェクタの噴射量を通常時の直噴インジェクタの噴射量よりも増加させる、
燃料噴射制御方法。
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JP2017524253A JP6380675B2 (ja) | 2015-06-19 | 2015-06-19 | 内燃エンジンの燃料噴射制御装置及び制御方法 |
MX2017016298A MX364569B (es) | 2015-06-19 | 2015-06-19 | Aparato de control y metodo de control de inyeccion de combustible del motor de combustion interna. |
EP15895654.0A EP3312407B1 (en) | 2015-06-19 | 2015-06-19 | Fuel injection control apparatus and control method of internal-combustion engine |
PCT/JP2015/067691 WO2016203634A1 (ja) | 2015-06-19 | 2015-06-19 | 内燃エンジンの燃料噴射制御装置及び制御方法 |
RU2017144481A RU2663210C1 (ru) | 2015-06-19 | 2015-06-19 | Устройство управления впрыском топлива и способ управления для двигателя внутреннего сгорания |
CN201580081049.7A CN107709742B (zh) | 2015-06-19 | 2015-06-19 | 内燃机的燃料喷射控制装置和控制方法 |
US15/736,671 US10260440B2 (en) | 2015-06-19 | 2015-06-19 | Fuel injection control device and control method for internal combustion engine |
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CN107709742A (zh) | 2018-02-16 |
MX2017016298A (es) | 2018-03-23 |
JPWO2016203634A1 (ja) | 2018-04-26 |
EP3312407A4 (en) | 2018-08-15 |
EP3312407B1 (en) | 2019-05-15 |
RU2663210C1 (ru) | 2018-08-02 |
US20180195449A1 (en) | 2018-07-12 |
JP6380675B2 (ja) | 2018-08-29 |
EP3312407A1 (en) | 2018-04-25 |
US10260440B2 (en) | 2019-04-16 |
CN107709742B (zh) | 2018-11-02 |
MX364569B (es) | 2019-05-02 |
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