WO2004063545A1 - 予混合圧縮自着火式内燃機関の制御方法 - Google Patents
予混合圧縮自着火式内燃機関の制御方法 Download PDFInfo
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- WO2004063545A1 WO2004063545A1 PCT/JP2004/000192 JP2004000192W WO2004063545A1 WO 2004063545 A1 WO2004063545 A1 WO 2004063545A1 JP 2004000192 W JP2004000192 W JP 2004000192W WO 2004063545 A1 WO2004063545 A1 WO 2004063545A1
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- timing
- valve closing
- compression ratio
- ignition
- effective compression
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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
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0242—Variable control of the exhaust valves only
- F02D13/0249—Variable control of the exhaust valves only changing the valve timing only
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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
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
- F01L13/0042—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams being profiled in axial and radial direction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
- F01L13/0047—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction the movement of the valves resulting from the sum of the simultaneous actions of at least two cams, the cams being independently variable in phase in respect of each other
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B1/00—Engines characterised by fuel-air mixture compression
- F02B1/12—Engines characterised by fuel-air mixture compression with compression ignition
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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
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0273—Multiple actuations of a valve within an engine cycle
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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
- F02D15/00—Varying compression ratio
- F02D15/04—Varying compression ratio by alteration of volume of compression space without changing piston stroke
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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
- F02D35/00—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
- F02D35/02—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions
- F02D35/025—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions by determining temperatures inside the cylinder, e.g. combustion temperatures
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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
- F02D41/30—Controlling fuel injection
- F02D41/3011—Controlling fuel injection according to or using specific or several modes of combustion
- F02D41/3017—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used
- F02D41/3035—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the premixed charge compression-ignition mode
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/45—Sensors specially adapted for EGR systems
- F02M26/46—Sensors specially adapted for EGR systems for determining the characteristics of gases, e.g. composition
- F02M26/47—Sensors specially adapted for EGR systems for determining the characteristics of gases, e.g. composition the characteristics being temperatures, pressures or flow rates
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
- F01L1/146—Push-rods
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/181—Centre pivot rocking arms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2800/00—Methods of operation using a variable valve timing mechanism
- F01L2800/10—Providing exhaust gas recirculation [EGR]
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/14—Direct injection into combustion chamber
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
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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
- F02D2041/001—Controlling intake air for engines with variable valve actuation
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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
- F02D35/00—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
- F02D35/02—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions
- F02D35/028—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for on interior conditions by determining the combustion timing or phasing
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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
- F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
- F02D41/0047—Controlling exhaust gas recirculation [EGR]
- F02D41/005—Controlling exhaust gas recirculation [EGR] according to engine operating conditions
- F02D41/0057—Specific combustion modes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
- F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
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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 control method for a homogeneous charge compression ignition internal combustion engine, and more particularly to a control method suitable for a diesel engine.
- This kind of premixed compression self-ignition type internal combustion engine was developed to improve the combustion of diesel engines.It forms a mixture of fuel and air in the combustion chamber in advance, and adiabatically compresses this mixture with a piston.
- Conventional examples include JP-A-2001-2717161, JP-A-2001-280164 and the like. Disclosure of the invention
- Self-ignition of a homogeneous charge compression ignition internal combustion engine is basically dependent on the temperature of the air-fuel mixture and the in-cylinder pressure, and the temperature and in-cylinder pressure are determined mainly by the effective compression ratio. Is done. For example, in order to avoid knocking due to premature ignition, it is necessary to suppress the rise in temperature and pressure of the air-fuel mixture during compression to below the self-ignition limit.Also, the best ignition timing, that is, near the compression top dead center In order to cause self-ignition, compression It is necessary to optimally control the temperature and pressure at the top dead center.
- the present invention changes the effective compression ratio by changing the valve closing timing of reopening of the exhaust valve, thereby enabling control so that self-ignition can be performed at an optimum timing in various operation regions, and knocking and misfiring.
- the purpose is to prevent.
- the invention according to claim 1 of the present application is directed to a control method of a premixed compression self-ignition type internal combustion engine in which air and fuel are premixed in a combustion chamber and then self-ignited by compression.
- a control method for a homogeneous charge compression ignition type internal combustion engine characterized by changing to an effective compression ratio.
- the effective compression ratio is increased in an operation region where the load is small, and the effective compression ratio is decreased as the load increases. It is characterized by controlling the valve closing timing of enlightenment.
- an optimal ignition timing can be obtained in each operation range according to the engine speed and the load. Create a re-opening valve closing time map in which the valve closing time is written, detect the engine speed and load during engine operation, and determine the re-opening valve closing time based on the valve closing time map. It is characterized by changing.
- the fuel injection start timing is set later than the reopening valve closing timing.
- the engine in the control method of the homogeneous charge compression ignition internal combustion engine according to the first aspect, is provided with an EGR device, an EGR rate is detected, and the re-enlightening is performed in an operation region where the EGR rate is high. It is characterized by increasing the effective compression ratio by making the valve closing timing of the opening earlier, and lowering the effective compression ratio by delaying the valve closing timing of the re-opening in the operating region where the EGR rate is low.
- the invention according to claim 6 is a control method for a homogeneous charge compression ignition internal combustion engine according to claim 1.
- the method when the intake air temperature is detected, when the intake air temperature is high, the effective compression ratio is lowered by delaying the reopening valve timing, and when the intake air temperature is low, the reopening valve closing time is advanced. It is characterized by:
- the cooling water temperature is detected, and when the cooling water temperature is low, the exhaust valve is closed again.
- the feature is that the effective compression ratio is increased by making the timing earlier, and when the cooling water temperature is high, the valve closing timing of the re-opening is delayed.
- the invention according to claim 8 is a control method of a premixed compression self-ignition type internal combustion engine according to any one of claims 1 to 7, wherein abnormal combustion detection sensor detects abnormal combustion such as knocking. It is characterized in that the valve closing timing of the re-opening is delayed so as to control to change to the highest effective compression ratio within a range where abnormal combustion does not occur.
- a limited effective compression ratio for suppressing a maximum in-cylinder pressure within an allowable range in each operation region is characterized in that a map is created and the closing timing of the reopening is set so as not to exceed the limited effective compression ratio in each operation region.
- the present invention relates to a control method of a premixed compression self-ignition internal combustion engine in which air and fuel are premixed in a combustion chamber and compressed to self-ignite, and the exhaust valve is temporarily stopped during a compression stroke.
- the effective compression ratio can be changed to an effective compression ratio that can obtain the optimal auto-ignition timing in the appropriate area of each vehicle by changing the valve closing timing of the re-opening freely. Because it is changed, there are the following advantages.
- the ignition timing of a homogeneous charge compression ignition internal combustion engine which had been difficult to control in the past, was controlled by adjusting the reopening of the exhaust valve, especially by adjusting the valve closing timing.
- the optimal effective compression ratio and the optimal self-ignition timing can be easily and accurately controlled in each operation region, thereby suppressing premature ignition (preventing a decrease in thermal efficiency), reducing combustion noise, and achieving a wide operating range. Low-injection combustion can be easily realized. Further, misfire due to ignition delay can be effectively prevented.
- the effective compression ratio is increased in the operating area where the load is small.
- the valve closing timing of the exhaust valve re-opening so that the effective compression ratio decreases as the load increases, the ignition delay can be corrected when the load decreases, and good ignitability can be secured.
- premature ignition can be suppressed when the load increases, and knocking and the like can be effectively prevented.
- an exhaust valve re-opening closing time map is formed based on the engine speed and load, and the exhaust valve re-opening valve closing time map is used for the exhaust valve reopening map. If the valve closing timing is changed, sensing is common in electronically controlled engines.Since the machine speed and load are used as parameters, the control logic is simplified and the operation of the exhaust valve is simplified. Can be defined.
- the effective compression ratio is increased by increasing the valve closing timing of reopening of the exhaust valve to increase the EGR ratio. If the effective compression ratio is lowered by delaying the valve closing timing for reopening the exhaust valve in the operating region with a low rate, the ignitability of the mixture (self-ignition ) Can be adjusted to the optimal ignition timing.
- the intake air (supply) temperature is detected, and when the intake air temperature is high, the effective compression ratio is lowered by delaying the valve closing timing for reopening the exhaust valve.
- the valve closing timing of re-opening is advanced, so that even if the ignitability of the air-fuel mixture changes with the change of the intake air temperature, it is corrected to the optimal ignition timing be able to.
- the cooling water temperature is detected, and when the cooling water temperature is low, the effective compression ratio is increased by increasing the valve closing timing of reopening of the exhaust valve to increase the rejection water temperature. If the valve timing of re-opening is delayed when the temperature is high, even if the ignitability of the air-fuel mixture changes due to the change of the coolant temperature, it can be corrected to the optimal ignition timing.
- FIG. 1 is a schematic view of a homogeneous charge compression ignition type diesel engine which implements a control method according to the present invention.
- FIG. 2 is a perspective view of an exhaust variable valve train.
- FIG. 3 is a cross-sectional view of a cross section perpendicular to the axis of the exhaust cam shown in FIG. 2, and is a diagram showing both exhaust power units in parallel.
- FIG. 4 is a plan view of the reopening cam of the variable valve operating device of FIG.
- FIG. 5 is a schematic cross-sectional view of a cylinder showing a biston stroke for re-enlightening.
- FIG. 6 is a flowchart showing a first control method according to the present invention.
- FIG. 7 is a diagram showing the relationship between exhaust valve re-opening and changes in in-cylinder temperature.
- FIG. 8 is a diagram showing the relationship between the in-cylinder temperature and the ignition delay.
- FIG. 9 is a diagram showing the relationship between the equivalence ratio and the auto-ignition temperature.
- FIG. 10 is a diagram showing an effective operation region with respect to changes in the engine speed and the load.
- FIG. 11 is a diagram showing a valve closing timing map.
- FIG. 12 is a diagram showing the relationship between the re-opening valve closing timing and the injection start timing.
- FIG. 13 is a flowchart showing a control method 2 according to the present invention.
- FIG. 14 is a diagram showing the relationship between the EGR rate and the ignition timing.
- FIG. 15 is a diagram showing the relationship between the EGR rate and the target effective compression ratio.
- FIG. 16 is a flowchart showing a control method 3 according to the present invention.
- FIG. 17 is a diagram showing the relationship between the intake air temperature and the ignition timing.
- FIG. 18 is a diagram showing the relationship between the intake air temperature and the target effective compression ratio.
- FIG. 19 is a flowchart showing a control method 4 according to the present invention.
- FIG. 20 is a diagram showing the relationship between the cooling water temperature and the ignition timing.
- FIG. 21 is a diagram showing the relationship between the cooling water temperature and the target effective compression ratio.
- FIG. 22 is a flowchart showing a control method 6 according to the present invention.
- FIG. 23 is a diagram showing the relationship between the ignition characteristics and the effective operating range.
- FIG. 24 is a schematic diagram illustrating a control method 7 according to the present invention.
- FIG. 25 is a diagram showing a change in the in-cylinder pressure.
- FIG. 1 to 5 show a homogeneous charge compression ignition type diesel engine for carrying out a control method according to the present invention
- FIG. 1 is a schematic view including a cylinder portion and arrangements of an intake / exhaust device and a control device.
- a piston 2 is fitted in a cylinder 1
- a combustion chamber 3 is formed by a top wall of the piston 2 and the cylinder 1.
- An intake hole 5 and an exhaust hole are formed in a ceiling surface of the combustion chamber 3. 6 is opened and an electronically controlled fuel injection valve 7 is arranged.
- An intake valve 8 and an exhaust valve 9 are arranged in the intake port 5 and the exhaust port 6, respectively, and both valves 8 and 9 are interlocked with an intake valve operating device 10 and an exhaust variable valve operating device 11 respectively. I have.
- the variable valve operating device 11 is configured to temporarily re-open the exhaust valve 9 during the compression stroke, and the valve closing timing of the re-opening is controlled by the valve closing timing changing means. It can be changed.
- an engine peripheral device an engine controller 15 is provided, and a supercharger 16, an intercooler 17, and an EGR (air gas recirculation) device 18 are provided.
- the intake hole 5 communicates with the outside air through an intake passage 20, an intercooler 17, an intake pipe 21, a compressor section 16a of a supercharger 16, and an intake pipe 22, and an exhaust hole 6 has an exhaust passage 25, a turbocharger. It communicates with the outside air through 16 turbine sections 16 b and exhaust pipes 26.
- An EGR tube 28 of the EGR device 18 communicates between the exhaust passage 25 and the intake passage 20, and the EGR tube 28 is provided with an EGR valve 30 whose opening can be adjusted.
- the engine controller 15 includes an injection device ECU (injection valve electronic control unit) 31 and a valve operating device ECU (valve operating device control unit) 32, as well as a CPU, an arithmetic device, and various storage devices.
- the output of the engine controller 15 is connected to the fuel injection valve 7 and the valve operating devices 10 and 11.
- the fuel injection valve 7 is controlled by the injection device ECU 31 to control the fuel injection amount and the injection start timing.
- the valve opening / closing timing is controlled by the valve gear ECU 32.
- the valve closing timing of the reopening of the exhaust valve 9 is controlled.
- An engine speed sensor 36 and a load sensor 37 are connected to the input section of the engine controller 15, and an EGR rate recognition device 39, an air (intake) flow rate sensor 40, an intake air temperature sensor 41, and cooling Water temperature sensor 42 and abnormal combustion detection sensor (knock sensor, etc.) 43 are connected.
- the EGR rate recognition device 39 is provided in the EGR valve 39 and detects (recognizes) the EGR rate.
- the load sensor 37 is provided in the accelerator device 44 or the fuel increasing / decreasing mechanism of the fuel injection pump, and detects the fuel injection amount as a load.
- the abnormal combustion sensor 43 is arranged in the side wall of the cylinder 1 or in the cylinder 1, and detects abnormal combustion such as knocking by detecting abnormal vibration of the cylinder 1 or abnormal pressure fluctuation in the combustion chamber. .
- the air flow sensor 40 is provided in the intake pipe 22 on the upstream side of the supercharger 16 so as to detect an air flow rate flowing in the intake pipe 22.
- the engine speed sensor 36 is disposed on a crankshaft, a gear 45 fixed to the crankshaft, a wheel, or the like, and detects the crankshaft speed (engine speed).
- Coolant temperature sensor 42 Is located, for example, in a cooling water jacket around the cylinder to detect the temperature of the cooling water around the cylinder.
- the present invention is applied to an internal combustion engine equipped with an EGR device as described above, but it is also possible to apply an internal combustion engine not equipped with an EGR device.
- variable valve system for exhaust [Specific example of variable valve system for exhaust]
- the variable exhaust valve train 11 shown in Fig. 1 is configured so that it can be reopened as described above, and the valve closing timing of the reopening can be changed. This will be described with reference to FIGS.
- the variable exhaust valve train 11 shown in FIGS. 2 to 4 is a valve train utilizing a plurality of cams.
- a camshaft 50 for the air valve is provided with an air valve.
- a first exhaust cam 52 having a main cam mountain 51 and a second exhaust cam 54 having a movable cam mountain 53 for reopening are provided.
- first exhaust cam 52 is formed integrally with the camshaft 50
- second exhaust cam 53 is formed separately from the camshaft 50 as shown in FIG.
- the shaft rotates integrally with the camshaft 50, but is fitted with a key or a spline so that the position can be changed in the axial direction.
- FIG. 4 is a plan view of the second exhaust cam 54.
- the width of the movable cam peak 53 in the circumferential direction changes along the axial direction.
- the front end 53 a in the rotation direction of the cam peak 53 is set parallel to the axial center direction so that the valve opening time of the re-opening is always near the bottom dead center.
- the rear end 53b of the cam peak 53 in the rotational direction is inclined with respect to the axial direction so that the timing can be changed arbitrarily.
- the boundary between the movable cam ridge 53 and the cam circle of the second exhaust cam 54 is shown by a solid line in order to clarify the shape of the movable cam ridge 53. It is smooth and continuous.
- variable exhaust valve train 11 shown in FIGS. 2 to 4 is merely an example, and in addition to such a structure, for example, a first exhaust valve 51 having a main thread 51 for exhaust stroke as shown in FIG.
- An exhaust cam 52 and a second exhaust cam 54 having a movable cam mountain 53 for reopening are provided.
- the second exhaust cam 54 for reopening can be rotated in the rotational direction with respect to the cam shaft 50, and the position of the movable cam mountain 53 for reopening can be changed.
- the valve closing timing By shifting in the direction of rotation, it is possible to change the valve closing timing.
- the portion corresponding to the valve opening timing at the front end in the rotation direction of the movable cam mountain 53 is formed so as to always overlap with the main cam mountain 51 of the first exhaust cam 52.
- multiple types of exhaust powers are provided, each of which has a cam mountain for the exhaust stroke and a force mountain for the re-enlightenment. It is also possible to have a structure.
- Fig. 5 shows how the exhaust valve of the engine is re-opened.
- the intake valve 8 is open, so that intake air is supplied from the intake hole 5 into the combustion chamber 3.
- the intake valve 8 is closed and the exhaust valve 9 is temporarily re-opened from near the bottom dead center, and the compression pressure in the combustion chamber 3 is increased through the exhaust hole 6. I'm pulling out.
- the exhaust valve 9 for reopening is also closed, and the intake air is substantially compressed. That is, by temporarily reopening the exhaust valve 9 from a position near the bottom dead center, the compression start timing is delayed, and the effective compression ratio can be reduced.
- Figure 8 shows the data of a preliminary experiment showing the relationship between the change in the in-cylinder temperature and the in-cylinder pressure and the ignition delay.
- the change curves Gl, G2, and G3 show that the in-cylinder pressure G1 ⁇ G2
- the relationship is The common characteristic of the change curves G1, G2, and G3 is that the higher the in-cylinder temperature, the shorter the autoignition delay. However, the pressure increases from the low-pressure curve G1 to the curves G2, G3. It can be reasoned that the ignition delay is getting shorter. (Relationship between valve closing timing of exhaust valve re-opening, in-cylinder temperature and ignition timing) Fig.
- valve closing timing 0 ec of exhaust valve re-opening (B 0 to B 3) is, for example, 0 0 , ⁇ 1, 0 2, and 0 3 show how the in-cylinder temperature (A0 to A3) changes when it changes to:
- the vertical axis shows the exhaust valve lift and the in-cylinder temperature
- the horizontal axis shows the crank angle.
- FIG. 7 four re-openings B0, Bl, B2, and B3 in which the valve closing timing ⁇ changes from ⁇ 0 to ⁇ 3 are displayed as an example.
- the valve opening timings of B0 to B3 are aligned near the bottom dead center of the compression stroke (bottom dead center of the exhaust stroke) BDC.
- the in-cylinder temperature change curves AO, Al, A2, and A3 correspond to reopening B0, B1, B2, and B3, respectively.
- Tfl, Tf2, and Tf3 indicate auto-ignition temperatures that change depending on conditions such as the equivalence ratio.
- the ignition timing is obtained from the intersection of the in-cylinder temperature change curves AO, Al, A2, A3 and the self-ignition temperatures Tfl, Tf2, Tf3. Regardless of the self-ignition temperatures Tfl, Tf2, Tf3, As the ignition timing in the in-cylinder transition curve AO corresponding to the earliest valve closing timing ⁇ 0 becomes the earliest and the valve closing timing becomes later as 01, ⁇ 2 and 03, the corresponding change curves The ignition timing of Al, A2, and A3 is sequentially delayed. In other words, the earlier the reopening valve closing time ⁇ ec is, the earlier the self-ignition time is, and the later the valve closing time ⁇ ec is, the later the self-ignition time is.
- Fig. 9 shows the relationship between the equivalence ratio and the self-ignition temperature.
- the equivalence ratio of the air-fuel mixture in the combustion chamber increases, that is, as the load increases, the self-ignition temperature decreases. That is, when the load (injection amount) increases, the self-ignition temperature decreases, and the self-ignition timing becomes earlier.
- Fig. 10 shows the effective operating range of the engine with respect to changes in the equivalence ratio (load) and engine speed.
- the effective operating area of the engine is divided into high, medium, and low effective compression ratios. This is a convenient expression, and the effective compression ratio to ensure the optimal ignition timing is actually changed steplessly.
- Fig. 11 is a map of the re-opening valve closing timing written in the storage device of the engine controller in Fig. 1. Based on the relationship described in Figs. 7 to 9, the load increases as the load increases. The valve closing time is delayed, while the engine speed is advanced as the engine speed increases, and the optimum effective compression ratio and the optimal ignition timing near top dead center are obtained in each operating condition. Is created to obtain
- the horizontal axis represents the crank angle
- the vertical axis represents the in-cylinder temperature in the upper part
- the exhaust valve lift amount in the middle part represents the fuel injection in the lower part.
- an injection timing map corresponding to the load and the engine speed is written in the storage device of the engine controller 15 in FIG. 1, but in addition to this, the injection timing map obtained from the injection timing map is also added.
- the start timing ⁇ i is compared with the valve closing timing ⁇ ec obtained from the valve closing timing map. If the injection timing ⁇ i is earlier than the valve closing timing 10 ec, the injection timing ⁇ i is as shown in Fig. 12.
- the program incorporates a control to delay the crank angle by more than 0 ec.
- Fig. 6 shows a flow chart for controlling combustion of the engine based on the engine speed N and the load (equivalent ratio) L.
- the EGR rate, intake air temperature, air flow rate and cooling water temperature are not taken into account.
- step S1 of FIG. 6 the detected engine speed N and load L are input, and in step S2-1, the input is performed by the valve gear ECU 32 (FIG. 1) based on the valve closing timing map (FIG. 11). Obtain the valve closing timing ⁇ ec at which the optimal ignition timing according to the engine speed N and load N obtained is obtained.
- step S2-2 the injection device ECU 31 (FIG. 1) determines the optimum injection timing according to the engine speed and load based on the injection timing map. Specifically, the injection start timing 0 i and the injection end timing are obtained.
- step S3 the valve closing timing 0ec is compared with the injection start timing 0i to determine whether the valve closing timing ec is earlier than the injection start timing 0i. If YES, that is, if the valve closing time 0ec is early, the process proceeds to step S4, and the fuel injection valve 7 and the exhaust gas shown in FIG. 1 are set so that the obtained valve closing time ecec and P injection time 0i are obtained.
- the variable valve operating device 11 is controlled.
- step S4 If NO in step S4, that is, if the valve closing timing ⁇ ec is later than the injection timing 0, it will pass through the injection combustion power exhaust hole 6 as it is, so in step S5, first, the injection start timing 0i And in step S6, an appropriate delay angle ⁇ ; with respect to the valve closing time 0ec is obtained.
- step S7 the injection start timing ⁇ i is shifted by an angle smaller than the valve closing time 0ec. The timing is changed to a later time, and the fuel injection valve 7 and the variable exhaust valve train 11 of FIG. 1 are controlled.
- the load increases from the state of the in-cylinder temperature change curve A2, and the self-ignition temperature falls to T f 3
- the ignition timing of self-ignition shifts from point E2 to point E4, but premature ignition may cause combustion abnormality (knocking).
- the valve closing timing e ec by delaying the valve closing timing e ec to ⁇ 3 based on the valve closing timing map, lowering the effective compression ratio and changing the in-cylinder temperature curve to A3, the ignition timing of self-ignition Moves from point E4 to point E3 near the top dead center, and the optimal ignition timing is obtained.
- the self-ignition ignition timing is the force that moves from point E2 to point E5, which is later than the top dead center. Therefore, the possibility of misfiring comes out without the ignition conditions being established.
- the valve closing timing ⁇ ec is advanced to ⁇ 1 based on the valve closing timing map, the effective compression ratio is increased, and the temperature is changed to the in-cylinder temperature change curve A1, the ignition timing of self-ignition will be at the top dead center. Moving to the nearby point E1, the optimal ignition timing is obtained.
- valve closing timing 6 ec for re-opening the exhaust valve 9 in accordance with changes in the engine speed and load, an optimal effective compression ratio is realized in each appropriate operating rate range.
- the self-ignition timing can be freely controlled to an optimal timing at or near the top dead center.
- the injection timing is divided into two injections, an initial injection Ml and a late injection M2, but the initial injection M1 is generally in the middle to early middle stages of the compression stroke. Is set.
- FIGS. 13 to 15 show control methods in which the EGR rate is added as one of the parameters to control method 1 described above. Since the basic control is explained in control method 1, duplicate explanation is omitted, and only the EGR rate is explained. As input elements, the EGR rate recognized by the EGR rate recognition device 39 in FIG. 1 and the air flow rate from the air flow rate sensor 40 are added.
- Fig. 14 shows the relationship between the EGR rate and the ignition timing of self-ignition.If the EGR rate increases, C02 during mixing in the combustion chamber increases, thereby delaying the ignition timing and reducing ignitability. Is shown.
- Fig. 15 shows the relationship between the EGR rate and the target effective compression ratio. Since the ignitability deteriorates as the EGR rate increases as described above, in order to improve the ignitability, E As the GR ratio increases, the target effective compression ratio needs to be increased. For this purpose, when a change in the EGR rate is added in the valve closing timing map as shown in Fig. 11, the valve closing timing is set to be earlier in response to an increase in the EGR rate. Increase the effective compression ratio so that the ignition timing is at the optimal position near top dead center.
- FIG. 13 is a flowchart.
- step S1-1 the engine speed N and the load L are input, and in step S1-2, the EGR rate and the air flow rate are input.
- step S2 the injection device ECU determines an optimum basic injection amount from the input engine speed NL and load L based on the injection amount map, and then proceeds to step S3.
- step S3 the equivalence ratio of the air-fuel mixture is obtained from the basic injection amount, the EGR rate, and the air flow rate, and the process proceeds to step S4.
- step S4 a required effective compression ratio is obtained from the above-obtained equivalent ratio, and the process proceeds to step S5.
- the valve closing timing 0ec is determined from the determined required effective compression ratio, and the process proceeds to step S6, where the valve closing timing 0ec for reopening the exhaust valve is changed to the determined valve closing timing.
- step S3 a provisional equivalence ratio is calculated from the injection amount and the air flow rate, and in step S4, the EGR rate is added as shown by the broken line to obtain the actual equivalence ratio of the air-fuel mixture. It is also possible.
- valve closing time 0ec when the EGR rate increases, the valve closing time 0ec is advanced to increase the effective compression ratio, and conversely, when the EGR rate decreases, the valve closing time 0ec is delayed to increase the effective compression ratio.
- the compression ratio is controlled to be low.
- FIGS. 16 to 18 show control methods in which the intake (supply air) temperature is further added to control method 2 as one of the parameters. Since the control method using parameters other than the intake air temperature has been described in the control methods 1 and 2 above, a duplicate description will be avoided, and here only the air temperature will be described. As an input element of the control, the supply (intake) temperature from the intake temperature sensor is added.
- FIG. 1 is a diesel engine provided with a supercharger 16
- “intake”, “intake temperature” and “intake temperature sensor” are respectively referred to as “supply”, The description will be made by referring to “supply air temperature” and “supply air temperature sensor”.
- Figure 17 shows the relationship between the supply air temperature and the ignition timing, and shows that the lower the supply air temperature, the later the ignition timing becomes, and the lower the ignitability.
- Figure 18 shows the relationship between the supply air temperature and the target effective compression ratio.Since the ignitability deteriorates due to the decrease in the supply air temperature as described above, in order to improve the ignitability, It is necessary to increase the target effective compression ratio in response to the decrease in For this purpose, when the change in the supply air temperature is taken into account in the valve close timing map shown in Fig. 11, the valve close timing 0 ec is set earlier so as to correspond to the lower supply air temperature. The ignition timing of self-ignition is set to the optimal position near top dead center.
- FIG. 16 is a flowchart. Steps S1-1, S1-2, S2, and S3 are the same as those in FIG. 13, and the description thereof will not be repeated.
- step S1-3 the supply air temperature is input in parallel with the engine speed and the like.
- step S4 a required effective compression ratio is determined from the equivalence ratio and the supply air temperature determined in step S3, and the process proceeds to step S5.
- step S5 the valve closing timing 0 ec is determined from the determined required effective compression ratio, and the process proceeds to step S6, where the closing timing ⁇ ec of the re-opening of the valve is changed to the determined valve closing timing.
- valve closing timing 0 ec is advanced to increase the effective compression ratio, and conversely, when the intake air temperature rises, the valve closing timing is increased. Control to delay 0 ec to lower the effective compression ratio.
- FIGS. 19 to 21 show a control method in which the cooling water temperature is further added to the control method 2 as one of the parameters.
- the control method using parameters other than the cooling water temperature has been described in control methods 1 and 2, so here, only the matters relating to the cooling water temperature will be described.
- As a control input element the coolant temperature from the coolant temperature sensor 42 in FIG. 1 is added.
- Figure 20 shows the relationship between the cooling water temperature and the self-ignition timing. The lower the cooling water temperature, the lower the temperature of the cylinder, and the lower the ignition timing and the lower the ignitability. Is shown.
- Fig. 21 shows the relationship between the cooling water temperature and the target effective compression ratio.Since the ignitability deteriorates due to the decrease in the cooling water temperature as described above, in order to improve the ignitability, It is necessary to increase the target effective compression ratio in response to the cooling water temperature drop. For this purpose, when the change in cooling water temperature is taken into account in the valve closing timing map as shown in Fig. 11, the valve closing timing 0 ec is set to be earlier in response to the lowering of the cooling water temperature. , Ignition timing of self-ignition ⁇ ⁇ ⁇ Set ec to the optimal position near top dead center.
- FIG. 19 is a flowchart. Steps S1-1, S1-2, S2, and S3 are the same as those in FIG.
- step S1-3 the cooling water temperature is input in parallel with the engine speed and the like.
- step S4 a required effective compression ratio is determined from the equivalent ratio and the cooling water temperature determined in step S3, and the process proceeds to step S5.
- step S5 the valve closing timing 0 ec is determined from the determined required effective compression ratio, and the flow advances to step S6 to change the valve closing timing ⁇ ec to the determined valve closing timing.
- valve closing timing 0 ec when the cooling water temperature decreases, the valve closing timing 0 ec is advanced to increase the effective compression ratio, and conversely, when the cooling water temperature increases, the valve closing timing 0 Control to delay ec to lower the effective compression ratio.
- FIGS. 22 and 23 show the abnormal combustion sensor 4 3 shown in FIG. 1 in addition to the control methods 1 to 4 and the like, in order to more reliably prevent knocking due to premature ignition or combustion noise due to a rapid pressure rise.
- This is a control method that adds the detection of abnormal combustion by one of the parameters.
- a knock sensor is used as the abnormal combustion sensor 43.
- the control method using parameters other than the knock sensor is described in control methods 1 to 4, so here, only the knock sensor will be described.
- Figure 23 shows the ignition characteristics.
- the horizontal axis is the effective compression ratio
- the vertical axis is the ignition timing
- Y is the ignition characteristic line for self-ignition.
- the shaded area is the effective operating area (combustible area) surrounded by the allowable ignition timing limit HI and the allowable effective compression ratio limit H2. If the ignition characteristics deviate from the effective operating area, premature ignition will occur. Knocking occurs.
- the valve closing timing ec ec of the re-opening of the exhaust valve is delayed so as to return to the same range, and control is performed so as to lower the effective compression ratio.
- control is performed so as to lower the effective compression ratio.
- lower the effective compression ratio so as to ensure the highest possible effective compression ratio within the effective operation range.
- valve closing timing is delayed so that the effective compression ratio falls near the point X2 near the limit lines Hl and H2 of the effective operation region.
- FIG. 22 is a flow chart. Steps S1 to S6 are a combination of the control methods 2 to 5, and a description thereof will be omitted.
- step S7 it is determined whether or not an abnormal detection signal has been input from the abnormal combustion detection sensor, and if abnormal combustion has not occurred, that is, if NO, the control ends as it is. If YES in step S7, that is, if knocking starts due to premature ignition, the process proceeds to step S8, delays the valve closing timing 0 ec by a predetermined angle ⁇ 0, and returns to step S6.
- abnormal control is performed by the abnormal combustion sensor. Eliminate combustion.
- an abnormal combustion sensor a sensor that detects misfires due to ignition delay can be used.
- the effective compression ratio is increased by increasing the valve closing timing of re-opening.
- the ignition time will be advanced.
- FIGS. 24 and 25 are obtained by adding, to the control methods 1 to 4, control for suppressing the in-cylinder pressure in each operation region from exceeding the maximum allowable in-cylinder pressure.
- Each luck! ⁇ ⁇ Create a limited effective compression ratio map corresponding to the maximum allowable in-cylinder pressure in the S range, and reopen the valve so that the instruction signal to the variable exhaust valve system does not exceed the value of the limited effective compression ratio map.
- the closing timing is delayed so that the cylinder pressure does not exceed the maximum allowable cylinder pressure.
- the vertical axis shows the valve lift and the cylinder pressure
- the horizontal axis shows the crank angle.
- the valve closing timing is reset to 0.
- the in-cylinder pressure P1 exceeds the maximum allowable in-cylinder pressure Pa, which affects the cylinder.
- the effective compression ratio is lowered, and the in-cylinder pressure P2 lower than the allowable maximum in-cylinder pressure Pa is reduced.
- the degree to which the effective compression ratio is reduced is such that the highest point of the in-cylinder pressure P2 stops near the allowable maximum in-cylinder Pa. Set up as round. That is, the cylinder pressure is set so as to be as high as possible within the region of the maximum allowable cylinder pressure Pa.
- FIG. 24 is a flow chart. Steps S1 to S4 are a combination of the above control methods 2 to 4, and a description thereof will be omitted.
- step S5 it is determined whether or not the required effective compression ratio is smaller than the value of the maximum effective compression ratio of the maximum effective compression ratio map. If YES, that is, if it is smaller, the process proceeds to step S6, and the valve corresponding to the required effective compression ratio is determined.
- the closing timing ⁇ ec is determined, and the engine is driven by the determined valve closing timing ⁇ ec and the injection timing 6 i.
- step S5 If NO in step S5 above, that is, if the required effective compression ratio exceeds the maximum effective compression ratio in the maximum effective compression ratio map, the process proceeds to step S7, where the required effective compression ratio is set to be smaller than the maximum effective compression ratio. Correct the ratio and return to step S5 again. In short, even if combustion is controlled based on the detection of engine speed, load, intake air temperature and EGR, etc. Lower the ratio to prevent the cylinder pressure from being affected by an excessive increase in cylinder pressure.
- the present invention is also applicable to a gas or gasoline direct injection internal combustion engine.
- control method for a homogeneous charge compression ignition internal combustion engine according to the present invention can be widely used for an internal combustion engine, but is particularly suitable for controlling a diesel engine.
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- Analytical Chemistry (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
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Abstract
Description
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Priority Applications (2)
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EP04702049A EP1586757A4 (en) | 2003-01-14 | 2004-01-14 | PROCESS FOR CONTROLLING A PREMIXED INTERNAL COMBUSTION ENGINE ENGINEER |
US10/541,375 US20060169246A1 (en) | 2003-01-14 | 2004-01-14 | Method of controlling premix compression self-igniting internal combustion engine |
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JP2003-006063 | 2003-01-14 | ||
JP2003006063A JP2004263562A (ja) | 2003-01-14 | 2003-01-14 | 予混合圧縮自着火式内燃機関の制御方法 |
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EP (1) | EP1586757A4 (ja) |
JP (1) | JP2004263562A (ja) |
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AT5217U1 (de) * | 2001-09-28 | 2002-04-25 | Avl List Gmbh | Verfahren zum geregelten betrieb einer brennkraftmaschine |
US20050183693A1 (en) * | 2004-02-25 | 2005-08-25 | Ford Global Technologies Llc | Method and apparatus for controlling operation of dual mode hcci engines |
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2003
- 2003-01-14 JP JP2003006063A patent/JP2004263562A/ja active Pending
-
2004
- 2004-01-14 EP EP04702049A patent/EP1586757A4/en not_active Withdrawn
- 2004-01-14 US US10/541,375 patent/US20060169246A1/en not_active Abandoned
- 2004-01-14 WO PCT/JP2004/000192 patent/WO2004063545A1/ja active Application Filing
- 2004-01-14 KR KR1020057012519A patent/KR20050085945A/ko not_active Application Discontinuation
- 2004-01-14 CN CNA2004800020851A patent/CN1735744A/zh active Pending
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See also references of EP1586757A4 * |
Also Published As
Publication number | Publication date |
---|---|
KR20050085945A (ko) | 2005-08-29 |
EP1586757A1 (en) | 2005-10-19 |
JP2004263562A (ja) | 2004-09-24 |
CN1735744A (zh) | 2006-02-15 |
EP1586757A4 (en) | 2010-07-07 |
US20060169246A1 (en) | 2006-08-03 |
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