WO2012131996A1 - 燃料噴射装置 - Google Patents
燃料噴射装置 Download PDFInfo
- Publication number
- WO2012131996A1 WO2012131996A1 PCT/JP2011/058269 JP2011058269W WO2012131996A1 WO 2012131996 A1 WO2012131996 A1 WO 2012131996A1 JP 2011058269 W JP2011058269 W JP 2011058269W WO 2012131996 A1 WO2012131996 A1 WO 2012131996A1
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- WIPO (PCT)
- Prior art keywords
- fuel
- fuel injection
- injection valve
- temperature
- cylinder
- Prior art date
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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
- F02D41/30—Controlling fuel injection
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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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/06—Fuel or fuel supply system parameters
- F02D2200/0602—Fuel pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/06—Fuel or fuel supply system parameters
- F02D2200/0606—Fuel temperature
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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
- F02M2700/00—Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
- F02M2700/07—Nozzles and injectors with controllable fuel supply
- F02M2700/077—Injectors having cooling or heating means
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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
- F02M2700/00—Supplying, feeding or preparing air, fuel, fuel air mixtures or auxiliary fluids for a combustion engine; Use of exhaust gas; Compressors for piston engines
- F02M2700/12—Devices or methods for making a gas mixture for a combustion engine
- F02M2700/126—Devices for the supply or mixing of air and gas
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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
- F02M53/00—Fuel-injection apparatus characterised by having heating, cooling or thermally-insulating means
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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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices
- F02M61/163—Means being injection-valves with helically or spirally shaped grooves
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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
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
- F02M61/182—Discharge orifices being situated in different transversal planes with respect to valve member direction of movement
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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
- F02M67/00—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type
- F02M67/02—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type the gas being compressed air, e.g. compressed in pumps
- F02M67/04—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type the gas being compressed air, e.g. compressed in pumps the air being extracted from working cylinders of the engine
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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
- F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
- F02M69/04—Injectors peculiar thereto
- F02M69/047—Injectors peculiar thereto injectors with air chambers, e.g. communicating with atmosphere for aerating the nozzles
Definitions
- the present invention relates to a fuel injection device.
- In-cylinder injection system that directly injects fuel into the combustion chamber for improved transient response, volumetric efficiency due to latent heat of vaporization, and significant retarded combustion for catalyst activation at low temperatures in fuel supply for internal combustion engines Is adopted.
- the fuel is burned due to the oil dilution caused by the sprayed fuel colliding with the combustion chamber wall in the form of droplets or the deterioration of the spray caused by the deposit generated around the injection valve nozzle by the liquid fuel. Fluctuations were encouraged.
- spraying In order to take measures against oil dilution and spray deterioration caused by the adoption of such an in-cylinder injection system, and to reduce ignition variation and achieve stable combustion, spraying should be performed so that the fuel in the combustion chamber vaporizes quickly. It is important to atomize.
- the atomization of the spray injected from the fuel injection valve is due to the shearing force of the thinned liquid film, due to cavitation caused by flow separation, or by atomizing the fuel adhering to the surface by ultrasonic mechanical vibration. Things are known.
- Patent Document 1 discloses a fuel injection valve in which the flow path cross-sectional area of the bubble holding flow path portion is larger than the flow path cross-sectional area of the cavitation generation flow path, and the outlet of the cavitation generation flow path is a rapidly expanding flow. Yes.
- This fuel injection valve generates cavitation in the bubble holding channel by making the outlet of the cavitation generating channel a suddenly expanding flow.
- various fuel injection valves that generate cavitation inside are proposed.
- the fuel injection valve used for in-cylinder injection is easily affected by heat from combustion.
- Patent Document 1 when a fuel injection valve that generates cavitation inside and injects fuel containing bubbles is affected by heat, the bubbles contained in the fuel expand, and the gas mixing ratio ( The void ratio may increase. That is, the bubble (gas) has a higher volume expansion coefficient than the liquid, and the void ratio tends to increase as the fuel temperature increases. As a result, in a high temperature environment, the fuel flow rate decreases, and there is a possibility that the injection amount necessary for combustion may not be ensured appropriately.
- an object of the present invention is to atomize the fuel and secure a net fuel amount in a fuel injection valve that injects fuel containing bubbles.
- a fuel injection device disclosed in the present specification is mounted on an engine body and changes a void ratio of a fuel injection valve that injects fuel containing bubbles and the fuel injected from the fuel injection valve.
- Void ratio adjusting means By changing the void ratio, it is possible to secure a net fuel amount while achieving atomization of the fuel.
- the void ratio adjusting means increases the fuel pressure of the fuel injected from the fuel injection valve when a void ratio increase request is made.
- fuel atomization is promoted. For example, when the demand for fuel atomization is high, such as when the water temperature is low, this corresponds to a request for an increase in the void ratio. Since the void ratio is increased by increasing the fuel pressure, atomization of the fuel can be promoted by increasing the fuel pressure when the void ratio is requested to increase.
- the void ratio adjusting means can adjust the void ratio of the fuel by changing the temperature of the fuel injected from the fuel injection valve.
- the void ratio varies depending on the temperature of the fuel. Therefore, the void ratio can be controlled by changing the temperature of the fuel.
- the void ratio adjusting means can increase the temperature of the fuel injected from the fuel injection valve when a void ratio increase request is made.
- the void ratio adjusting means can adjust the fuel void ratio by adjusting the temperature of the fuel injected from the fuel injection valve in accordance with the temperature of the fuel for each cylinder provided in the engine body. Usually, the longer the distance from the fuel pump that pumps fuel to the fuel injection valve, the longer the period for receiving heat in that path, and the higher the temperature of the injected fuel. If the fuel temperature varies among the fuel injectors, the void ratio may be different for each fuel injector. Therefore, by adjusting the temperature of the fuel injection valve for each cylinder, it is possible to suppress variation among the cylinders of fuel injection.
- the fuel injection valve includes an in-cylinder fuel injection valve and a port fuel injection valve
- the void ratio adjusting means changes the injection ratio between the in-cylinder fuel injection valve and the port fuel injection valve, and the in-cylinder fuel injection.
- the temperature of the fuel injected from the valve can be adjusted. If the amount of injected fuel increases, the temperature of the fuel can be lowered by its cooling effect and heat capacity.
- the void ratio can be adjusted by controlling the temperature of the fuel.
- the injection ratio of the port fuel injection valve can be increased.
- the adjustment of the void ratio is desirably performed after the engine body has been warmed up and is in a stable operating state.
- the injection ratio from the port fuel injection valve is increased, on the other hand, the injection ratio from the in-cylinder fuel injection valve is decreased and the cooling effect of the fuel is decreased. As a result, the temperature of the fuel injected from the in-cylinder fuel injection valve increases, and warming up of the engine body is promoted.
- FIG. 1 is an explanatory diagram showing a configuration example of a fuel injection device mounted on an engine body.
- FIG. 2 is an explanatory view showing a cross section of a main part of the in-cylinder fuel injection valve included in the fuel injection device of the first embodiment.
- FIG. 3 is a flowchart showing an example of control performed by the fuel injection device.
- FIG. 4A is an example of a map for obtaining a target void ratio at a low water temperature
- FIG. 4B is an example of a map for obtaining a target void ratio at a high water temperature.
- FIG. 5 is an example of a map for obtaining the base fuel pressure.
- FIG. 6 is a graph for explaining the relationship between the cooling water temperature and the fuel temperature.
- FIG. 7 is a graph for explaining the relationship between the fuel temperature, the void ratio, and the fuel flow rate in the in-cylinder fuel injection valve.
- FIG. 8 is an example of a fuel temperature calculation map.
- FIG. 9 is a graph showing the fuel temperature in the cylinder fuel injection valve when the port injection ratio is small.
- FIG. 10 is a graph showing the fuel temperature in the cylinder fuel injection valve when the port injection ratio is large.
- FIG. 11 is a graph for explaining the relationship between the fuel pressure and the void ratio.
- FIG. 1 is an explanatory diagram showing a configuration example of the fuel injection device 1 attached to the engine body 2.
- the engine body 2 includes a first cylinder # 1 to a fourth cylinder # 4.
- the first cylinder # 1 to the fourth cylinder # 4 are provided with a first intake port 101 to a fourth intake port 104, respectively.
- the fuel injection device 1 includes a first in-cylinder fuel injection valve 11 and a first port fuel injection valve 12 as fuel injection valves that supply fuel to the first cylinder # 1.
- a second in-cylinder fuel injection valve 21 and a second port fuel injection valve 22 are provided as fuel injection valves for supplying fuel to the second cylinder # 2.
- the third in-cylinder fuel injection valve 31 and the third port fuel injection valve 32 serve as fuel injection valves that supply fuel to the third cylinder # 3
- the fourth fuel injection valve serves as fuel injection valve that supplies fuel to the fourth cylinder # 4.
- An in-cylinder fuel injection valve 41 and a fourth port fuel injection valve 42 are provided.
- Each in-cylinder fuel injection valve 11, 21, 31, 41 is connected to first branch pipes 5 a 1 to 5 a 4 branched from a delivery pipe 5 connected to the fuel pump 6.
- Each port fuel injection valve 12, 22, 32, 42 is connected to a second branch pipe 5b1-5b4 branched from the first branch pipe 5a1-5a4, respectively.
- a first regulating valve 511 is provided at the branch point of the second branch pipe 5b1.
- a second regulating valve 512 is provided at the branch point of the second branch pipe 5b2.
- a third regulating valve 513 is provided at the branch point of the second branch pipe 5b3.
- a fourth adjustment valve 514 is provided at the branch point of the second branch pipe 5b4.
- the first adjustment valve 511 to the fourth adjustment valve 514 change the injection ratio between the in-cylinder fuel injection valve and the port fuel injection valve.
- the injection ratio of the port fuel injection valve may be referred to as a port injection ratio.
- the fuel injection device 1 includes an ECU 7 as a control unit.
- the ECU 7 includes a CPU (Central Processing Unit) that performs arithmetic processing, a ROM (Read Only Memory) that stores programs, and a RAM (Random Access Memory) and NVRAM (Non Volatile RAM) that store data and the like. It is a computer.
- the ECU 7 is electrically connected to each in-cylinder fuel injection valve 11, 21, 31, 41.
- the ECU 7 is electrically connected to each port fuel injection valve 12, 22, 32, 42.
- the ECU 7 is electrically connected to the first adjustment valve 511 to the fourth adjustment valve 514.
- the ECU 7 is electrically connected to the fuel pump 6 and can control the duty ratio of the fuel pump 6.
- Various sensors for controlling the operating state of the engine body are connected to the ECU 7, and the water temperature gauge 8 is also electrically connected to the ECU 7.
- the fuel pump 6 is provided on the side closer to the first cylinder # 1, and the fourth cylinder # 4 is farthest from the fuel pump 6.
- the ECU 7 that controls the duty ratio of the fuel pump 6 to adjust the fuel pressure and controls the opening and closing of the first adjusting valve 511 to the fourth adjusting valve 514 has a function of a void ratio adjusting means. That is, the ECU 7 controls the duty ratio of the fuel pump 6 and controls the temperature of the fuel by controlling the opening and closing of the first adjusting valve 511 to the fourth adjusting valve 514 to control the fuel injection valve, particularly the in-cylinder fuel. Void ratio of fuel injected from the injection valve is changed.
- FIG. 2 is an explanatory view showing a main part of the in-cylinder fuel injection valve 11 included in the fuel injection device of the first embodiment as a cross section. Since the in-cylinder fuel injection valves 11, 21, 31, and 41 are the same, the first in-cylinder fuel injection valve 11 will be described here.
- the cylinder fuel injection valve 11 includes a nozzle body 131, a needle 132, and a drive mechanism 140.
- the drive mechanism 140 controls the sliding operation of the needle 132.
- the drive mechanism 140 is a conventionally known mechanism including components suitable for the operation of the needle 132, such as an actuator using a piezoelectric element, an electromagnet, or an elastic member that applies an appropriate pressure to the needle 132.
- the distal end side indicates the lower side in the drawing
- the proximal end side indicates the upper side in the drawing.
- a nozzle hole 133 is provided at the tip of the nozzle body 131.
- the nozzle hole 133 is a single nozzle hole formed in the direction along the axis of the nozzle body 131 at the tip of the nozzle body 131.
- a seat part 134 on which the needle 132 is seated is formed inside the nozzle body 131.
- the needle 132 is slidably disposed in the nozzle body 131, thereby forming a fuel introduction path 136 between the needle 132 and the nozzle body 131.
- the in-cylinder fuel injection valve 130 is closed by seating on the seat portion 134 in the nozzle body 131.
- the needle 132 is pulled up by the drive mechanism 140 and is separated from the seat portion 134 to be opened.
- the sheet portion 134 is provided at a position recessed from the nozzle hole 133. For this reason, the nozzle hole 133 is in a state of communicating with the outside, regardless of whether the needle 132 is in the valve open state or the valve closed state.
- the injection hole 133 is in communication with the combustion chamber.
- the in-cylinder fuel injection valve 11 is provided on the upstream side of the seat portion 134 and has a swirl flow generation unit 132a that imparts a swirl flow with respect to the sliding direction of the needle 132 to the fuel introduced from the fuel introduction path 136.
- the swirl flow generator 132 a is provided at the tip of the needle 132.
- the diameter of the swirling flow generating unit 132a is larger than that of the proximal end side of the needle 132.
- the tip portion of the swirling flow generating portion 132a is seated on the seat portion 134. As described above, the swirling flow generating unit 132a is located upstream of the seat unit 134 when the valve is opened and closed.
- the swirl flow generator 132a includes a spiral groove 132b. When the fuel introduced from the fuel introduction path 136 passes through the spiral groove 132b, a swirl component is added to the fuel flow, and a swirl flow of the fuel is generated.
- the in-cylinder fuel injection valve 11 is provided on the downstream side of the seat portion 134, and the swirl speed increasing portion 135 that supplies fuel to the nozzle hole 133 while increasing the swirling speed of the swirling flow generated in the swirling flow generating portion 132a. It has.
- the turning speed increasing portion 135 is formed such that the inner peripheral diameter is reduced toward the minimum throttle portion located downstream of the seat portion 134.
- the minimum throttling portion corresponds to a position having the smallest inner peripheral diameter in the downstream portion from the seat portion 134.
- the minimum throttle portion is a nozzle hole 133.
- the minimum throttle portion is not limited to the opening of the nozzle hole 133.
- the swirl speed increasing part 135 is formed between the seat part 134 and the nozzle hole 133, and accelerates the swirl speed of the fuel that has passed through the swirl flow generating part 132a and turned into a swirl state.
- the rotational radius of the swirl flow generated by the swirl flow generation unit 132a is gradually narrowed.
- the swirling flow increases into the swirling speed by flowing into a narrowed region with a reduced diameter.
- the swirling flow whose swirling speed is increased forms an air column in the nozzle hole 133.
- the inner peripheral wall surface of the turning acceleration portion 135 has a curved surface that is convex toward the center side.
- the fuel flow and the bubble mixed flow form a cone-like spray that diffuses from the center due to the centrifugal force of the swirling flow. Therefore, since the diameter of the cone-shaped spray increases as the distance from the nozzle hole increases, the spray liquid film is stretched and thinned. Then, it cannot be maintained as a liquid film and splits. Thereafter, the spray after the splitting is reduced in diameter by the self-pressurizing effect of the fine bubbles, collapses and becomes an ultrafine spray.
- the fuel spray injected by the in-cylinder fuel injection valve 11 is atomized, rapid flame propagation in the combustion chamber is realized, and stable combustion is performed.
- the port fuel injection valves 12, 22, 32, and 42 use the same fuel injection valves as the in-cylinder fuel injection valves 11, 21, 31, and 41.
- a type of fuel injector can be used.
- the in-cylinder fuel injection valves 11, 21, 31, and 41 are not limited to the fuel injection valve of the type shown in FIG. 2, and other types of fuel injection are possible as long as they can inject fuel containing bubbles.
- a valve can also be used.
- the fuel injection device 1 is controlled by the ECU 7.
- step S01 the temperature of the coolant supplied to the engine body 1 (engine coolant temperature) Tw is acquired.
- step S02 it is determined whether the engine coolant temperature Tw is lower than a predetermined threshold value Tw1.
- the threshold value Tw1 is for determining whether or not the engine main body 1 is in a state in which the subsequent control can be appropriately performed.
- a value for determining the completion of warm-up can be used as the threshold value Tw1.
- step S03 the injection ratio from the port fuel injection valve is increased. Specifically, the port injection ratio kpfi is set to “1”. That is, the entire required fuel amount for injection is injected from the port fuel injection valves 12, 22, 32, 42 in each cylinder. Thereby, the fuel injection from the cylinder fuel injection valves 11, 21, 31, 41 is stopped. As a result, since the in-cylinder fuel injection valves 11, 21, 31, and 41 have a suppressed cooling effect by the fuel, the temperature can be raised quickly by receiving heat from the combustion gas, and stable fuel injection can be performed. Become. The process of step S03 is repeated until it is determined Yes in step S02.
- step S04 a target void ratio is calculated. Specifically, the target void ratio is determined with reference to the map.
- the target void ratio is determined from a plurality of maps selected according to the engine coolant temperature.
- FIG. 4A is an example of a map for obtaining a target void ratio at a low water temperature
- FIG. 4B is an example of a map for obtaining a target void ratio at a high water temperature.
- the target void rate is obtained from the engine load factor KL and the engine speed NE.
- the map at the time of low water temperature is divided into three regions a, b, and c.
- the map at the time of high water temperature is divided into three areas A, B, and C.
- each value has a relationship of a> b> c, A> B> C, a> A, b> B, c> C.
- the void ratio is set to be larger as the atomization is expected to be promoted. As the water temperature is lower, the lower the load and the lower the rotation, the more the atomization promotion is expected. Therefore, a large void ratio is required.
- step S05 which is performed subsequent to step S04, calculation of a base fuel pressure and a target fuel temperature, which are bases for subsequent fuel pressure setting, are performed.
- the base fuel pressure is calculated by referring to the map shown in FIG.
- the base fuel pressure is calculated from the engine load factor KL and the engine speed NE.
- the base fuel pressure increases as the load increases and the rotation speed increases.
- the target fuel temperature is calculated as the fuel temperature required to realize the target void ratio calculated in step S04.
- the required fuel temperature is calculated in order to achieve the target void rate a.
- FIG. 6 is a graph for explaining the relationship between the engine coolant temperature and the fuel temperature.
- the fuel temperature has a correlation with the engine coolant temperature, and is lower as the engine coolant temperature is lower. Referring to FIG. 7, the higher the fuel flow rate, the higher the void rate ⁇ , and the higher the fuel temperature, the higher the void rate ⁇ . For this reason, in order to achieve the same void ratio ⁇ at different fuel flow rates, it is necessary to set the fuel temperature appropriately.
- the target fuel temperature is set according to the base fuel pressure.
- step S06 the actual fuel temperature Tf is acquired.
- the actual fuel temperature Tf is determined by referring to the fuel temperature calculation map shown in FIG.
- the fuel temperature Tf is calculated from the fuel injection amount Gf (g / s).
- a fuel temperature difference ⁇ Tf between the cylinders is calculated.
- the inter-cylinder difference ⁇ Tf of the fuel temperature is the temperature of the fuel injected from the first in-cylinder fuel injection valve 11 disposed at a position close to the fuel pump 6 and the fourth cylinder disposed at the position farthest from the fuel pump 6. This is the difference from the temperature of the fuel injected from the internal fuel injection valve 41. This is because the fourth in-cylinder fuel injection valve 41 arranged at the farthest position from the fuel pump 6 has the longest heat receiving period, and the temperature of the fuel is likely to differ from the first in-cylinder fuel injection valve 11. Is taken into account.
- the fuel temperature difference between the cylinders is obtained in advance by experiment for each operating state, and is obtained by reflecting this in the fuel temperature Tf obtained in step S06.
- step S08 it is determined whether or not the fuel temperature difference ⁇ Tf calculated in step S07 is greater than a predetermined threshold value ⁇ Tf1. If the inter-cylinder difference ⁇ Tf is large and it is determined Yes, the process proceeds to step S09. In step S09, the port injection ratio kpfi is set for each cylinder. On the other hand, if the inter-cylinder difference ⁇ Tf is small and it is determined No, the process proceeds to step S10. In step S10, a common port injection ratio kpfi among all cylinders is set.
- the change of the fuel temperature by changing the port injection ratio will be described with reference to FIGS. As shown in FIG. 9, when the port injection ratio is small, the fuel temperature becomes lower as the engine becomes more heavily loaded and rotated.
- step S09 and step S10 this relationship is used to control the target fuel temperature calculated in step S05. That is, the temperature of the fuel injected from the in-cylinder fuel injection valves 11, 21, 31, 41 is adjusted according to the temperature of the fuel for each cylinder provided in the engine body, and the void ratio of the fuel is adjusted.
- step S11 a correction void ratio is calculated.
- the corrected void ratio is calculated from the fuel temperature, engine speed NE, load ratio KL, fuel pressure before correction, that is, base fuel pressure, after the processing in steps S09 and S10.
- step S12 a void rate deviation amount ⁇ calculated from the target void rate calculated in step S04 and the corrected void rate calculated in step S11 is calculated. Specifically, a difference from the target void ratio and the corrected void ratio is obtained.
- step S13 the target fuel pressure f ( ⁇ ) is calculated using the void rate deviation amount ⁇ obtained in step S12, and fuel pump duty ratio control is performed in accordance with the target fuel pressure f ( ⁇ ).
- the cylinder fuel injection valves 11, 21, 31, 41 and the port fuel injection valves 12, 22, 32, 42 are provided, but only the cylinder fuel injection valves 11, 21, 31, 41 are provided.
- the control can be simplified. That is, the control regarding the fuel temperature may be omitted, and the desired void ratio may be realized by adjusting the fuel pressure according to the duty ratio of the fuel pump.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
Abstract
Description
2 エンジン本体
♯1 第1気筒
♯2 第2気筒
♯3 第3気筒
♯4 第4気筒
11 第1筒内燃料噴射弁
12 第1ポート燃料噴射弁
21 第2筒内燃料噴射弁
22 第2ポート燃料噴射弁
31 第3筒内燃料噴射弁
32 第3ポート燃料噴射弁
41 第4筒内燃料噴射弁
42 第4ポート燃料噴射弁
5 デリバリパイプ
5a1~5a4 第1枝管
5b1~5b4 第2枝管
511 第1調整弁
512 第2調整弁
513 第3調整弁
514 第4調整弁
6 燃料ポンプ
7 ECU
8 水温計
101 第1吸気ポート
102 第2吸気ポート
103 第3吸気ポート
104 第4吸気ポート
Claims (7)
- エンジン本体に装着され、気泡を含む燃料を噴射する燃料噴射弁と、
前記燃料噴射弁から噴射される前記燃料のボイド率を変化させるボイド率調整手段と、
を備えた燃料噴射装置。 - 前記ボイド率調整手段は、ボイド率上昇要請時に前記燃料噴射弁から噴射される燃料の燃圧を上昇させる請求項1記載の燃料噴射装置。
- 前記ボイド率調整手段は、前記燃料噴射弁から噴射される燃料の温度を変更して前記燃料のボイド率を調整する請求項1又は2に記載の燃料噴射装置。
- 前記ボイド率調整手段は、ボイド率上昇要請時に前記燃料噴射弁から噴射される燃料の温度を上昇させる請求項1乃至3のいずれか一項に記載の燃料噴射装置。
- 前記ボイド率調整手段は、前記エンジン本体が備える気筒毎の燃料の温度に応じて前記燃料噴射弁から噴射される燃料の温度を調整し、前記燃料のボイド率を調整する請求項3又は4に記載の燃料噴射装置。
- 前記燃料噴射弁は、筒内燃料噴射弁とポート燃料噴射弁とを含み、前記ボイド率調整手段は、筒内燃料噴射弁とポート燃料噴射弁との噴射比率を変更して前記筒内燃料噴射弁から噴射される燃料の温度を調整する請求項2乃至5のいずれか一項に記載の燃料噴射装置。
- 前記エンジン本体に供給される冷却水の温度が予め定めた閾値よりも低いときは、前記ポート燃料噴射弁の噴射比率を大きくする請求項6記載の燃料噴射装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2011800698501A CN103459825A (zh) | 2011-03-31 | 2011-03-31 | 燃料喷射装置 |
EP11862040.0A EP2693041A4 (en) | 2011-03-31 | 2011-03-31 | FUEL INJECTION DEVICE |
PCT/JP2011/058269 WO2012131996A1 (ja) | 2011-03-31 | 2011-03-31 | 燃料噴射装置 |
US14/001,718 US9194323B2 (en) | 2011-03-31 | 2011-03-31 | Fuel injection device |
JP2013507002A JP5780294B2 (ja) | 2011-03-31 | 2011-03-31 | 燃料噴射装置 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2011/058269 WO2012131996A1 (ja) | 2011-03-31 | 2011-03-31 | 燃料噴射装置 |
Publications (1)
Publication Number | Publication Date |
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WO2012131996A1 true WO2012131996A1 (ja) | 2012-10-04 |
Family
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2011/058269 WO2012131996A1 (ja) | 2011-03-31 | 2011-03-31 | 燃料噴射装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US9194323B2 (ja) |
EP (1) | EP2693041A4 (ja) |
JP (1) | JP5780294B2 (ja) |
CN (1) | CN103459825A (ja) |
WO (1) | WO2012131996A1 (ja) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3303822B1 (en) | 2015-05-29 | 2021-05-19 | Bombardier Recreational Products Inc. | Internal combustion engine having two fuel injectors per cylinder and control method therefor |
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2011
- 2011-03-31 EP EP11862040.0A patent/EP2693041A4/en not_active Withdrawn
- 2011-03-31 JP JP2013507002A patent/JP5780294B2/ja not_active Expired - Fee Related
- 2011-03-31 US US14/001,718 patent/US9194323B2/en not_active Expired - Fee Related
- 2011-03-31 WO PCT/JP2011/058269 patent/WO2012131996A1/ja active Application Filing
- 2011-03-31 CN CN2011800698501A patent/CN103459825A/zh active Pending
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Also Published As
Publication number | Publication date |
---|---|
JPWO2012131996A1 (ja) | 2014-07-24 |
US20140014069A1 (en) | 2014-01-16 |
US9194323B2 (en) | 2015-11-24 |
EP2693041A4 (en) | 2015-04-22 |
CN103459825A (zh) | 2013-12-18 |
JP5780294B2 (ja) | 2015-09-16 |
EP2693041A1 (en) | 2014-02-05 |
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