WO2012086059A1 - 内燃機関の制御装置 - Google Patents
内燃機関の制御装置 Download PDFInfo
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- WO2012086059A1 WO2012086059A1 PCT/JP2010/073346 JP2010073346W WO2012086059A1 WO 2012086059 A1 WO2012086059 A1 WO 2012086059A1 JP 2010073346 W JP2010073346 W JP 2010073346W WO 2012086059 A1 WO2012086059 A1 WO 2012086059A1
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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
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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
- F02D41/008—Controlling each cylinder individually
- F02D41/0087—Selective cylinder activation, i.e. partial cylinder operation
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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
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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
- F02D41/06—Introducing corrections for particular operating conditions for engine starting or warming up
- F02D41/062—Introducing corrections for particular operating conditions for engine starting or warming up for starting
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
- F02D41/1444—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases
- F02D41/1459—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being a hydrocarbon content or concentration
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1497—With detection of the mechanical response of the engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
- F02D17/02—Cutting-out
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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
- F02D2200/021—Engine temperature
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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
- F02D2200/0611—Fuel type, fuel composition or fuel quality
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/10—Parameters related to the engine output, e.g. engine torque or engine speed
- F02D2200/101—Engine speed
Definitions
- the present invention relates to a control device for an internal combustion engine.
- a part of the fuel injected from the fuel injector into the intake port is vaporized as it is, but the rest is temporarily attached to the wall surface of the intake port (including the intake valve; the same applies hereinafter).
- the fuel adhering to the intake port is vaporized due to the negative pressure in the intake pipe or the action of heat from the wall surface of the intake port, and forms an air-fuel mixture with the vaporized component of the fuel newly injected from the fuel injector.
- the amount of fuel injected from the fuel injector and adhering to the intake port balances the amount of fuel adhering to the intake port to vaporize. For this reason, by injecting fuel corresponding to the stoichiometric air-fuel ratio from the fuel injector, the air-fuel ratio of the air-fuel mixture formed in the cylinder can be made the stoichiometric air-fuel ratio.
- Patent Document 1 a technique related to fuel supply at the time of starting a multi-cylinder internal combustion engine disclosed in Patent Document 1 (hereinafter referred to as a conventional technique).
- a conventional technique As described in Patent Document 1, it is not always necessary to supply fuel to all cylinders in order to start a multi-cylinder internal combustion engine. Even if the fuel supply to some cylinders is stopped, the internal combustion engine is It is possible to start. If the fuel supply to some cylinders is stopped and the engine is started, unburned HC discharged at the time of starting can be greatly reduced.
- the above prior art is an invention made on the basis of such knowledge, and determines a cylinder to be supplied with fuel and a cylinder to which the supply of fuel is to be stopped based on the result of cylinder discrimination at start-up, and according to the determination
- the fuel supply to each cylinder is controlled. More specifically, in the above prior art, the fuel supply pattern between the cylinders is determined according to the water temperature at the start. There are multiple fuel supply patterns depending on the water temperature, the number of cylinders that stop supplying fuel is high in patterns that support high water temperatures, and the number of cylinders that stop supplying fuel is low in patterns that support low water temperatures. Is set. After the start is completed (when the engine speed exceeds 400 rpm), fuel is supplied to all the cylinders.
- Japanese Unexamined Patent Publication No. 8-338282 Japanese Unexamined Patent Publication No. 2004-270471 Japanese Unexamined Patent Publication No. 2007-285265
- a large amount of fuel is supplied to the cylinder that supplies fuel from the start of the initial fuel supply.
- the amount of fuel supplied to that cylinder (hereinafter referred to as a delay cylinder) is the first of the cylinders that have been supplying fuel from the beginning. Compared to the amount of fuel supplied.
- the reason why the initial fuel supply amount of the delay cylinder can be reduced is as follows. In the delay cylinder, idling without combustion is performed in a period before fuel supply starts, but the in-cylinder temperature rises due to idling. Further, since the engine rotational speed increases during the period before the fuel supply in the delay cylinder starts, a negative pressure is generated in the intake pipe accordingly. As a result, an environment in which fuel vaporization is promoted is created when the fuel is initially supplied to the delay cylinder. For this reason, the amount of fuel initially supplied to the delay cylinder is small. Therefore, the discharge of unburned HC can be further reduced.
- the start completion is determined based on the fact that the engine speed has exceeded a predetermined value (400 rpm).
- a predetermined value 400 rpm.
- the fuel supply to the delay cylinder is started and the operation shifts to all cylinder operation. To do.
- the start timing of fuel supply to the delay cylinder is determined by such a method, the amount of unburned HC discharged cannot be reduced sufficiently. That is, there is room for improvement in the above-described conventional technology.
- the present invention has been made in view of the above points, and an object of the present invention is to provide a control device for an internal combustion engine that can suppress the discharge of unburned HC accompanying the start of the internal combustion engine.
- a first invention is a control device for an internal combustion engine,
- fuel supply control means that initially supplies fuel only to some cylinders and delays fuel supply to delay cylinders that are other cylinders;
- Representative temperature acquisition means for acquiring a representative temperature of the internal combustion engine;
- a delay cylinder start rotation speed that is an engine rotation speed at a timing when a cycle in which the delay cylinder first burns starts, and a predicted value of an engine output gas HC amount that is an HC amount that is output from the internal combustion engine when the engine is started,
- An engine output gas HC amount predicting means for calculating the relationship of Target rotational speed calculation means for calculating a target rotational speed that is a target value of the delayed cylinder start rotational speed based on the relationship calculated by the engine output gas HC amount prediction means;
- the fuel supply control means determines a timing for starting fuel supply to the delay cylinder so that the delay cylinder start rotation speed is close to the target rotation speed.
- the second invention is the first invention, wherein The fuel supply control means forcibly starts fuel supply to the delay cylinder regardless of the engine speed when a predetermined time limit is passed.
- the third invention is the second invention, wherein The apparatus further comprises combustion number correction means for correcting the number of combustions in the whole internal combustion engine scheduled within the time limit based on the predetermined parameter and the target rotational speed.
- An alcohol concentration acquisition means for acquiring the alcohol concentration of the fuel supplied to the internal combustion engine; The alcohol concentration is included in the predetermined parameter.
- the target rotational speed calculation means sets the delayed cylinder start rotational speed at a portion where the gradient of the predicted value of the engine output gas HC amount suddenly changes in the relationship as the target rotational speed.
- the timing for starting the fuel supply to the delay cylinder is controlled on the basis of the predetermined parameters including the representative temperature of the internal combustion engine, so that the end of the exhaust passage (tail pipe) is It is possible to reliably reduce the amount of unburned HC discharged to the tank.
- the second aspect of the invention it is possible to reliably prevent a state in which the internal combustion engine is vibrated for a long time from starting.
- the third aspect of the present invention it is possible to more reliably achieve both of preventing the state of large vibration of the internal combustion engine from continuing for a long time and reducing the amount of unburned HC discharged into the atmosphere. can do.
- the above-described effect can be reliably obtained even when the fuel having various alcohol concentrations is used.
- the amount of unburned HC discharged into the atmosphere at the time of starting can be reduced more reliably.
- Embodiment 1 of this invention It is a figure for demonstrating the system configuration
- FIG. 1 is a diagram for explaining a system configuration according to the first embodiment of the present invention.
- the system of the present embodiment includes an internal combustion engine 1 (hereinafter simply referred to as an engine).
- the engine 1 is a V-type eight-cylinder four-stroke reciprocating engine having eight cylinders. In the following description, the numbers of the cylinders are expressed as # 1 to # 8.
- the engine 1 is a spark ignition type engine having an ignition plug (not shown) in each cylinder.
- the engine 1 can be operated with 100% gasoline as fuel, and can also be operated with an alcohol-containing fuel obtained by mixing gasoline and alcohol (ethanol, methanol, etc.).
- the number of cylinders and the cylinder arrangement of the engine in the present invention are not limited to the V-type 8 cylinders, and may be, for example, in-line 6 cylinders, V-type 6 cylinders, V-type 10 cylinders, V-type 12 cylinders, or the like. Good.
- Each cylinder and the surge tank 3 are connected by an intake branch pipe 4.
- the surge tank 3 and each intake branch pipe 4 are collectively referred to as an intake pipe.
- a fuel injector 6 is attached to each intake branch pipe 4. Each fuel injector 6 injects fuel into the intake port of the corresponding cylinder.
- the surge tank 3 is connected to an air cleaner (not shown) via an intake duct 7.
- a throttle 8 is disposed in the intake duct 7.
- an exhaust manifold 5 is provided for each bank on the exhaust side of the engine 1.
- An exhaust passage (not shown) is connected to each exhaust manifold 5.
- An exhaust purification catalyst (not shown) for purifying exhaust gas is disposed in the exhaust passage.
- the system of the present embodiment further includes various sensors and an ECU (Electronic Control Unit) 10.
- an intake pipe pressure sensor 20 that detects the pressure (intake pipe pressure) in the surge tank 3
- a water temperature sensor 21 that detects the coolant temperature of the engine 1
- a crank that detects the rotation angle of the crankshaft of the engine 1.
- An angle sensor 22, a cylinder discrimination sensor 23, an air flow meter 24 that detects the intake air amount of the engine 1, and a fuel property sensor 25 that detects the alcohol concentration of fuel supplied to the engine 1 are provided.
- the ECU 10 controls operations of various actuators including the fuel injector 6 based on signals from various sensors.
- the system of the present embodiment includes a starter (not shown) such as a cell motor that rotationally drives the crankshaft of the engine 1 when the engine 1 is started.
- the temperature of the intake port is usually approximately the same as the engine coolant temperature.
- the engine cooling water temperature detected by the water temperature sensor 21 is used as the representative temperature of the engine 1.
- the temperature used as the representative temperature of the engine 1 is not limited to the engine coolant temperature.
- the intake port temperature may be directly detected by a sensor, and the detected intake port temperature may be used as the representative temperature of the engine 1.
- the fuel property sensor 25 is installed in any part of the fuel supply path from the fuel tank to the fuel injector 6.
- various known types such as an optical type and a capacitance type can be used.
- the alcohol concentration of the fuel is directly detected by the fuel property sensor 25.
- the method for acquiring the alcohol concentration of the fuel in the present invention is not limited to the method using the fuel property sensor 25.
- the alcohol concentration of the fuel may be detected (estimated) from the learned value in the air-fuel ratio feedback control. That is, since the value of the theoretical air-fuel ratio is different between gasoline and alcohol, the value of the theoretical air-fuel ratio of the alcohol-containing fuel differs depending on the alcohol concentration. For this reason, it is possible to acquire the alcohol concentration of the fuel based on the theoretical air-fuel ratio value learned by feeding back a signal from an air-fuel ratio sensor (not shown) provided in the exhaust passage of the engine 1. is there.
- FIG. 2 is a diagram illustrating an example of a cylinder that performs fuel injection and a cylinder that does not perform fuel injection when the engine is started. As shown in FIG. 2, it is assumed that the ignition order of the engine 1 of the present embodiment is # 1- # 8- # 7- # 3- # 6- # 5- # 4- # 2. In the example shown in FIG. 2, fuel is injected into the four cylinders # 1, # 4, # 6, and # 7 from the beginning of the engine start (first cycle).
- the four cylinders # 2, # 3, # 5, and # 8 are set as delay cylinders. In the example shown in FIG. 2, by selecting the delay cylinder in this way, the combustion interval becomes equal even in the period before the fuel supply to the delay cylinder is started. .
- the number of delay cylinders is not limited to four. Further, the number of delay cylinders may be increased or decreased according to conditions such as engine coolant temperature.
- the fuel injections # 8, # 3, # 5, and # 2 are not performed (injection cut) in the first cycle when the engine is started.
- fuel injections of # 8 and # 3 are not performed (injection cut), and fuel injection is performed for # 5 and # 2. That is, in the example shown in FIG. 2, fuel injection to the delay cylinder is started from # 5 of the second cycle, and thereafter, fuel injection is performed to all cylinders.
- a period until fuel injection for the delay cylinder is started is referred to as a “delay period”.
- the delay period can be expressed by the number of cycles as follows. Since the engine 1 has 8 cylinders, the number of cycles can be counted in 1/8 increments.
- the delay period is (1 + 5/8) cycles.
- the point in time when all the retarded cylinders have completed one combustion is referred to as the completion of the start of the engine 1. That is, the engine start is completed when all the cylinders of the engine 1 have completed at least one combustion. In the period until the engine start is completed, it is desirable to control the fuel injection timing for each cylinder so that the fuel injection is completed before the intake valve is opened.
- the fuel injector 6 directly enters the cylinder, the fuel is ignited without being sufficiently atomized, and the amount of unburned HC (unburned fuel component) is likely to increase.
- the inventors have determined the timing at which the delay cylinder starts the first combustion cycle (that is, the length of the delay period). It was found that the amount of unburned HC discharged into the atmosphere changed significantly.
- FIG. 3 is a diagram for explaining the relationship between the length of the delay period and the amount of unburned HC emitted when the engine 1 is started.
- the delay period of zero means that fuel is supplied to all cylinders from the beginning of engine start.
- a graph indicated by A in FIG. 3 indicates the total amount of unburned HC discharged from the engine 1 when the engine 1 is started (hereinafter referred to as “engine exhaust gas HC amount”).
- This engine exhaust gas HC amount is the amount of HC before being purified by the exhaust purification catalyst.
- the engine output gas HC amount means the total amount of unburned HC discharged from the engine 1 until the start of the engine 1 is completed or until a predetermined time elapses from the start. Shall. As shown in this graph, the engine output gas HC amount decreases as the delay period increases. This is due to the following reason.
- the engine output gas HC amount is greatly affected by the engine rotation speed (hereinafter referred to as “delay cylinder start rotation speed”) at the timing when the cycle in which the delay cylinder first burns starts.
- the “timing at which the cycle in which the delayed cylinder first burns” corresponds to the timing at which the intake valve # 5 in the second cycle is opened in the example shown in FIG.
- the higher the delay cylinder start rotational speed the higher the piston speed in the intake stroke of the first combustion cycle of the delay cylinder, so the flow velocity of air passing through the intake valve (hereinafter referred to as “intake valve peripheral flow velocity”) increases. . For this reason, vaporization of the fuel adhering to the wall surface of the intake port or the intake valve is promoted.
- the higher the delay cylinder start rotational speed the stronger the tumble (vertical vortex) formed by the air-fuel mixture flowing into the cylinder in the first combustion cycle of the delay cylinder. For this reason, the higher the delay cylinder start rotational speed, the more fuel vaporization is promoted in the delay cylinder that starts combustion, and combustion is improved by strong tumble. Less. Therefore, the engine output gas HC amount is also reduced. Conversely, the lower the delay cylinder start rotational speed, the more unburned HC discharged from the delay cylinder, and the engine exhaust gas HC amount also increases.
- FIG. 4 is a diagram showing the relationship between the length of the delay period and the delay cylinder start rotational speed.
- the delayed cylinder start rotational speed (200 rpm) when the length of the delay period is zero means the rotational speed of the crankshaft by the starter.
- the engine speed increases due to the torque generated by combustion of cylinders other than the delay cylinder.
- the longer the delay period the higher the delayed cylinder start rotational speed.
- the longer the delay period the smaller the engine output gas HC amount.
- the shorter the delay period the greater the engine output gas HC amount.
- the longer the delay period the more the engine exhaust gas HC amount can be reduced.
- only the cylinders other than the delay cylinders are in combustion operation, so that the thermal energy supplied to the exhaust purification catalyst is smaller than when all the cylinders are in combustion operation.
- the longer the delay period is, the longer the warm-up of the exhaust purification catalyst is delayed. If the exhaust purification catalyst warms up late, the amount of HC purified by the exhaust purification catalyst decreases, so the amount of HC discharged into the atmosphere from the tail pipe at the end of the exhaust passage (hereinafter referred to as “tail HC amount”). Increase). B in FIG.
- FIG 3 is a graph showing a tendency of the increase amount of the tail HC amount due to the delay in warming up of the exhaust purification catalyst. As this graph shows, the longer the delay period, the greater the increase in the amount of tail HC due to the delay in warming up the exhaust purification catalyst.
- FIG. 5 is a diagram showing the relationship between the accumulated tail HC amount at the time of starting the engine 1 (for example, until 20 seconds have passed since the engine start) and the length of the delay period.
- the relationship between the accumulated tail HC amount (hereinafter simply referred to as “integrated tail HC amount”) and the delay period at the start of the engine 1 shows a tendency as shown in FIG. 5 for the reason described based on FIG. . That is, up to a certain limit, the longer the delay period, the lower the integrated tail HC amount. This is due to the influence of a decrease in the engine exhaust gas HC amount due to the longer delay period.
- the integrated tail HC amount increases. This is an influence of the delay in warming up the exhaust purification catalyst due to the longer delay period.
- the delay period is 1.25 to 1.5 cycles
- the integrated tail HC amount is minimal, so the optimum delay period is 1.25 to 1.5 cycles.
- the optimal delay period that minimizes the integrated tail HC amount is different. Value.
- the reason why the integrated tail HC amount is minimized when the delay period is 1.25 to 1.5 cycles in the example shown in FIG. 5 can be explained as follows.
- a point at which the slope changes suddenly hereinafter referred to as “slope change point”.
- the position of the inclination change point substantially coincides with the position where the integrated tail HC amount is minimized.
- the slope of decrease in the engine output gas HC amount is steep, whereas in the range before the slope change point, the slope of decrease in the engine output gas HC amount becomes gentle.
- the position of the inclination change point appearing in the delay cylinder start rotation speed graph shown in FIG. Therefore, the position of the slope change point that appears in the graph of the engine output gas HC amount indicated by A in FIG. 3 also varies depending on conditions such as the engine coolant temperature at the time of engine start and the alcohol concentration of fuel.
- the vicinity of the slope change point that appears in the engine output gas HC amount graph indicated by A in FIG. 3 is a position where the integrated tail HC amount is minimized. This holds regardless of conditions such as the engine coolant temperature at the time of engine start and the alcohol concentration of the fuel.
- FIG. 6 is a graph showing the relationship between the engine output gas HC amount and the delay cylinder start rotational speed. Also in the graph shown in FIG. 6, a slope change point corresponding to the slope change point of the engine output gas HC amount graph indicated by A in FIG. 3 appears. As shown in FIG. 6, the delayed cylinder start rotational speed corresponding to this inclination change point is defined as ⁇ .
- the fuel supply to the delay cylinder is started, if the delay cylinder start rotational speed is controlled to be close to ⁇ , the delay period is made to coincide with the position of the slope change point in the graph of the engine output gas HC amount in FIG. Therefore, the integrated tail HC amount can be minimized. Therefore, in the present embodiment, the fuel supply to the delay cylinder is started so that the delay cylinder starts the first combustion cycle at the timing when ⁇ is the target rotation speed and the engine rotation speed is equal to or higher than the target rotation speed ⁇ . It was decided to control.
- FIG. 7 is a diagram for explaining the timing of starting the fuel supply to the delay cylinder.
- the “number of injection cuts” on the horizontal axis indicates the number of injection cuts for the delay cylinder. That is, in the example shown in FIG. 2, # 8 in the first cycle is the first injection cut, # 3 is the second injection cut, # 5 is the third injection cut, and # 2 Is the fourth injection cut. Then, # 8 in the second cycle is the fifth injection cut, and # 3 is the sixth injection cut.
- the “engine speed” on the vertical axis is the engine speed at the timing when the intake valve opens in a cycle corresponding to each injection cut. In the example shown in FIG. 7, the engine rotational speed corresponding to the sixth injection cut is equal to or higher than the target rotational speed ⁇ .
- the injection cut of the delay cylinder is stopped, and the fuel injection to the delay cylinder is started. That is, in the example shown in FIG. 2, fuel is supplied from the fuel injector 6 to all the cylinders after # 3, which is scheduled for the sixth injection cut.
- FIG. 8 is a flowchart of a routine executed by the ECU 10 in the present embodiment in order to realize the above function.
- the routine shown in FIG. 8 it is first determined whether or not the engine 1 is requested to be started (step 100).
- the value of the engine cooling water temperature detected by the water temperature sensor 21 and the value of the alcohol concentration of the fuel detected by the fuel property sensor 25 are respectively obtained (Ste 102).
- the relationship between the predicted value of the engine output gas HC amount and the delay cylinder start rotational speed is calculated (step 104).
- the relationship calculated in step 104 is represented by a map as shown in FIG.
- the ECU 10 stores information regarding these tendencies in advance.
- step 104 based on the information and the values of the engine cooling water temperature and the alcohol concentration acquired in step 102, a map of predicted values of the engine output gas HC amount as shown in FIG. 6 (hereinafter referred to as “engine output gas”). HC amount prediction map ”) is calculated.
- the amount of engine exhaust gas HC decreases as the intake air amount increases. This is because as the amount of intake air increases, the flow velocity around the intake valve increases and the vaporization of the fuel adhering to the wall surface of the intake port and the intake valve is promoted.
- the map of the predicted value of the engine output gas HC amount may be further corrected according to the intake air amount detected by the intake pipe pressure sensor 20 or the air flow meter 24. If the intake air amount at the time of starting is substantially constant every time, this correction may not be performed.
- the target rotational speed ⁇ is calculated (step 106).
- the value of the delayed cylinder start rotational speed at the inclination change point of the engine output gas HC amount prediction map calculated in step 104 is set as the target rotational speed ⁇ .
- a point where the second-order differential value is maximum can be specified as the inclination change point in the engine output gas HC amount prediction map.
- step 108 the engine 1 is started (step 108).
- step 108 the following processing is performed.
- the engine 1 is cranked by the starter.
- cylinder discrimination is performed based on a signal from the cylinder discrimination sensor 23, and fuel is supplied to the cylinders other than the delay cylinder by the fuel injector 6.
- the cylinder group to be the delay cylinder may be determined in advance or may be determined based on the result of cylinder discrimination. In the case of determining a delay cylinder based on the result of cylinder discrimination, for example, the following may be performed.
- a cylinder that can be burned first and a cylinder whose ignition order is alternated from this cylinder are set as fuel supply targets, and the other cylinders are set as delay cylinders.
- the ECU 10 starts fuel supply to the delay cylinder so that the first combustion cycle of the delay cylinder starts at the timing when the engine rotation speed becomes equal to or higher than the target rotation speed ⁇ calculated in step 106 (step 110). More specifically, for example, the following control is performed.
- a map as shown in FIG. 7 (hereinafter referred to as an “engine speed prediction map”) for predicting an increase in engine speed at the start based on the values of the engine coolant temperature and the alcohol concentration acquired in step 102. Is calculated as follows. The higher the engine coolant temperature, the more easily the fuel is vaporized, so the amount of fuel combusted in the cylinder increases.
- the higher the engine coolant temperature the greater the torque generated by one combustion, and therefore the higher the engine speed tends to increase. That is, as the engine coolant temperature is higher, the inclination of the engine rotation speed prediction map tends to be steeper. Conversely, the lower the engine coolant temperature, the slower the engine speed increases, so the inclination of the engine speed prediction map tends to be gentler. Further, at low temperatures, the higher the alcohol concentration of the fuel, the more difficult it is to vaporize the fuel, and there is a tendency for the torque generated by one combustion to decrease. For this reason, as the alcohol concentration is higher, the inclination of the engine rotation speed prediction map tends to be gentler.
- the ECU 10 stores information regarding these tendencies in advance.
- an engine speed prediction map is calculated. Subsequently, by applying the target rotational speed ⁇ calculated in step 106 to the calculated engine rotational speed prediction map, the engine rotational speed is equal to or higher than the target rotational speed ⁇ in the same manner as described with reference to FIG. Find the number of injection cuts that Then, from the time when the engine rotational speed becomes equal to or higher than the target rotational speed ⁇ , the injection cut of the delay cylinder is stopped and fuel injection is started to the delay cylinder. That is, thereafter, fuel injection is performed on all cylinders.
- the delay cylinder immediately starts the first combustion cycle when the engine rotational speed becomes equal to or higher than the target rotational speed ⁇ .
- the accumulated tail HC amount (that is, the amount of unburned HC discharged into the atmosphere when the engine 1 is started) is close to the minimum value, so that the accumulated tail HC amount can be reliably reduced.
- step 110 instead of the above control, the following control may be performed.
- control is performed so that fuel injection from the fuel injector 6 is completed before the intake valve is opened.
- a predetermined timing for example, in the middle of the exhaust stroke of the previous cycle
- ⁇ be a predicted value of the range in which the engine speed increases from the fuel injection set timing until the intake valve opens. It takes a short time from the fuel injection set timing to the opening of the intake valve, and the increase in the engine speed during that period is not so large.
- the value of ⁇ may be a fixed value set in advance.
- ⁇ since the increase speed of the engine rotational speed is affected by the engine coolant temperature and the alcohol concentration of the fuel as described above, ⁇ may be corrected according to these values when the accuracy is further increased. Good.
- the actual engine speed NE detected by the crank angle sensor 22 is acquired immediately before the fuel injection set timing of each delay cylinder, and the success or failure of the following equation is determined. NE ⁇ ⁇ (1)
- the starting rotational speed is controlled to be equal to or higher than the target rotational speed ⁇ .
- control is not necessarily required.
- the fuel supply start timing for the delay cylinder may be controlled so that the difference between the start rotation speed and the target rotation speed ⁇ is smaller than a predetermined reference value. In such a case, the starting rotational speed may be less than the target rotational speed ⁇ .
- the water temperature sensor 21 is the “representative temperature acquisition means” in the first invention
- the fuel property sensor 25 is the “alcohol concentration acquisition means” in the fourth invention
- the ECU 10 executes the routine of FIG. 8
- the “fuel supply control means” in the first aspect of the invention executes the processing of step 104 described above, so that “the engine output gas HC amount in the first aspect of the invention”.
- the “prediction means” executes the processing of step 106, thereby realizing the “target rotation speed calculation means” in the first and fifth inventions.
- Embodiment 2 the second embodiment of the present invention will be described with reference to FIG. 9 and FIG. 10. The description will focus on the differences from the first embodiment described above, and the same matters will be described. Simplify or omit.
- the delay period becomes longer as the engine rotational speed increases more slowly.
- the delay period only some of the cylinders burn, so the combustion interval is longer than when all cylinders are operating.
- the rotational fluctuation becomes larger than when all cylinders are operated, and the engine 1 is likely to vibrate. For this reason, if the delay period becomes too long, the state of large vibration will continue for a long time, which is not preferable.
- start time limit a time limit for starting fuel supply to the delay cylinder
- FIG. 9 is a diagram for explaining fuel supply control at start-up in the present embodiment.
- the start deadline is set by the number of cycles. In the example shown in FIG. 9, the start deadline is set to (1 + 5/8) cycles. In the second cycle # 5, this start deadline is passed. Therefore, in this example, after # 5 of the second cycle, fuel supply to the delay cylinder is forcibly started and all cylinder operation is performed regardless of the engine speed.
- the ECU 10 performs the control of the routine of FIG. 8 of the first embodiment described above, and when the fuel supply to the delay cylinder is not started by the start time limit, after the start time limit, the ECU 10 performs the control for the delay cylinder. Control to forcibly start fuel supply. According to such control, since all cylinder operation is forcibly performed after the start deadline, it is possible to reliably prevent the state in which the vibration of the engine 1 is large from continuing for a long time at the start.
- the engine rotational speed tends to increase slowly.
- the target rotational speed ⁇ is high, it takes time until the engine rotational speed reaches the target rotational speed ⁇ . In these cases, it can be predicted that there is a high possibility that the engine rotational speed will not reach the target rotational speed ⁇ by the start deadline. Therefore, in these cases, the increase in the engine speed is promoted by increasing the number of combustions in the entire engine 1 (hereinafter referred to as “the number of combustions”) scheduled within the start deadline.
- FIG. 10 is a map for correcting the combustion number based on the engine coolant temperature and the target rotational speed ⁇ .
- a region where the combustion number is increased by 2 a region where the combustion number is increased by 1, a region where the combustion number is not increased or decreased, and a region where the combustion number is decreased by 1 are set.
- the engine coolant temperature acquired in step 102 and the target rotational speed ⁇ calculated in step 106 are displayed on the map shown in FIG.
- the number of combustion is corrected. For example, when the engine coolant temperature is 0 ° C. and the target rotational speed ⁇ is the value shown in FIG.
- the combustion number can be increased as the engine coolant temperature is lower, and the combustion number can be increased as the target rotational speed ⁇ is higher. For this reason, when the engine coolant temperature is low or the target rotational speed ⁇ is high, the engine rotational speed can be increased. Even in these cases, the engine rotational speed is set to the target by the start deadline. The rotational speed ⁇ can be reached. For this reason, the integrated tail HC amount at the time of starting can be reliably reduced.
- the number of combustion can be reduced.
- the engine coolant temperature is high or the target rotational speed ⁇ is low, it can be predicted that the time required for the engine rotational speed to reach the target rotational speed ⁇ is short and that there is a margin before the start deadline.
- the number of combustions is reduced, it can be determined that the engine rotational speed can reach the target rotational speed ⁇ by the start deadline. Therefore, by reducing the number of combustions in such a case, it is possible to further reduce the integrated tail HC amount at the time of starting.
- the combustion number is corrected based on the engine coolant temperature and the target rotational speed ⁇ has been described above.
- the combustion number may be further corrected based on the alcohol concentration of the fuel. That is, when the alcohol concentration is high, the number of combustion may be corrected so as to be larger than when the alcohol concentration is low.
- the “combustion number correcting means” in the third aspect of the present invention is realized by the ECU 10 correcting the combustion number based on the map shown in FIG.
- Embodiment 3 FIG. Next, a third embodiment of the present invention will be described with reference to FIG. 11. The description will focus on the differences from the above-described embodiments, and the description of the same matters will be simplified or omitted. To do.
- FIG. 11 is a diagram for explaining the configuration of the exhaust system of the engine 1 of the present embodiment.
- # 1 and # 7 share the exhaust manifold 51
- # 3 and # 5 share the exhaust manifold 52.
- the exhaust manifolds 51 and 52 are connected to the exhaust purification catalyst 31.
- # 2 and # 8 share the exhaust manifold 53
- # 4 and # 6 share the exhaust manifold.
- the exhaust manifolds 53 and 54 are connected to the exhaust purification catalyst 32.
- # 2, # 3, # 5, and # 8 are set as delay cylinders, and # 1, # 4, # 6, and # 7 are initially started.
- air is discharged from the exhaust valve of the delay cylinder that does not burn.
- the exhaust gases (burned gas) # 1 and # 7 burned in the left bank are sent to the exhaust purification catalyst 31 through the exhaust manifold 51.
- the air discharged from # 3 and # 5 which does not burn is sent to the exhaust purification catalyst 31 through the exhaust manifold 52.
- the combusted # 4 and # 6 exhaust gases (burned gas) are sent to the exhaust purification catalyst 32 through the exhaust manifold 54, and are exhausted from the unburned # 2 and # 8. Is sent to the exhaust purification catalyst 32 through the exhaust manifold 53. In this way, it is possible to prevent high-temperature burned gas from mixing with low-temperature air. For this reason, HC oxidation (post-combustion) can be efficiently generated while the burned gas passes through the exhaust manifolds 51 and 54, so that a high-temperature gas can flow into the exhaust purification catalysts 31 and 32. it can.
- high-temperature burned gas passes through the exhaust manifolds 51 and 54 having a small surface area, and air passes through the exhaust manifolds 52 and 53 having a large surface area. For this reason, the heat radiation from the exhaust manifolds 51 and 54 through which the high-temperature burned gas passes can be reduced, and the temperature of the burned gas can be kept high. For this reason, in the present embodiment, warming up of the exhaust purification catalysts 31 and 32 can be promoted. As a result, the integrated tail HC amount at the time of starting can be further reduced.
- Embodiment 4 FIG. Next, the fourth embodiment of the present invention will be described with reference to FIG. 12. The description will focus on the differences from the above-described embodiments, and the description of the same matters will be simplified or omitted. To do.
- FIG. 12 is a view for explaining the configuration of the exhaust system of the engine 1 of the present embodiment.
- # 1 and # 3 share the exhaust manifold 55, and # 5 and # 7 share the exhaust manifold 56. .
- the exhaust manifolds 55 and 56 are connected to the exhaust purification catalyst 31.
- # 2 and # 4 share the exhaust manifold 57, and # 6 and # 8 share the exhaust manifold 58.
- the exhaust manifolds 57 and 58 are connected to the exhaust purification catalyst 32.
- # 1, # 2, # 3, and # 4 are set as delay cylinders, and fuel is supplied to # 5, # 6, # 7, and # 8 from the start.
- fuel is supplied to # 5, # 6, # 7, and # 8 from the start.
- the heat radiation from the exhaust manifolds 56 and 58 through which the high-temperature burned gas passes can be reduced, and the temperature of the burned gas can be kept high.
- the warm-up of the exhaust purification catalysts 31 and 32 can be promoted as in the third embodiment.
- the integrated tail HC amount at the time of starting can be further reduced.
- Embodiment 3 shown in FIG. 11 the exhaust manifolds 51 and 53 are connected to two cylinders that are not adjacent to each other.
- each of the exhaust manifolds 55 to 58 is connected to two adjacent cylinders. Therefore, the handling of the exhaust manifolds 55 to 58 can be simplified and the shape can be easily manufactured.
- # 5, # 6, # 7, and # 8 are combustion cylinders, so the combustion intervals are not equal. For this reason, regarding the vibration reduction during the delay period, the configuration of the third embodiment is excellent.
Abstract
Description
多気筒内燃機関が始動されるときに、当初は一部の気筒に対してのみ燃料を供給し、それ以外の気筒である遅延気筒に対する燃料供給を遅れて開始する燃料供給制御手段と、
前記内燃機関の代表温度を取得する代表温度取得手段と、
前記遅延気筒が最初に燃焼するサイクルが開始するタイミングでの機関回転速度である遅延気筒開始回転速度と、機関始動の際に前記内燃機関から出るHC量であるエンジン出ガスHC量の予測値との関係を、少なくとも前記代表温度を含む所定のパラメータに基づいて算出するエンジン出ガスHC量予測手段と、
前記エンジン出ガスHC量予測手段により算出された関係に基づいて、前記遅延気筒開始回転速度の目標値である目標回転速度を算出する目標回転速度算出手段と、
を備え、
前記燃料供給制御手段は、前記遅延気筒開始回転速度が前記目標回転速度付近となるように、前記遅延気筒に対する燃料供給を開始するタイミングを決定することを特徴とする。
前記燃料供給制御手段は、所定の期限を過ぎる場合には、機関回転速度にかかわらず、前記遅延気筒に対する燃料供給を強制的に開始することを特徴とする。
前記所定のパラメータと、前記目標回転速度とに基づいて、前記期限内において予定される前記内燃機関全体での燃焼の数を補正する燃焼数補正手段を更に備えることを特徴とする。
前記内燃機関に供給される燃料のアルコール濃度を取得するアルコール濃度取得手段を更に備え、
前記所定のパラメータに前記アルコール濃度が含まれることを特徴とする。
前記目標回転速度算出手段は、前記関係において前記エンジン出ガスHC量の予測値の傾きが急変する部分の遅延気筒開始回転速度を前記目標回転速度とすることを特徴とする。
図1は、本発明の実施の形態1のシステム構成を説明するための図である。図1に示すように、本実施形態のシステムは、内燃機関1(以下、単にエンジンという)を備えている。エンジン1は、8個の気筒を有するV型8気筒の4ストロークレシプロエンジンである。以下の説明では、各気筒の番号を#1~#8と表す。また、このエンジン1は、各気筒に点火プラグ(図示せず)を備える火花点火式のエンジンである。エンジン1は、100%ガソリンを燃料として運転可能であり、また、ガソリンとアルコール(エタノール、メタノールなど)とを混合したアルコール含有燃料によっても運転可能になっている。なお、本発明におけるエンジンの気筒数および気筒配置は、V型8気筒に限定されるものではなく、例えば直列6気筒、V型6気筒、V型10気筒、V型12気筒などであってもよい。
NE≧α-δ ・・・(1)
次に、図9および図10を参照して、本発明の実施の形態2について説明するが、上述した実施の形態1との相違点を中心に説明し、同様の事項については、その説明を簡略化または省略する。
次に、図11を参照して、本発明の実施の形態3について説明するが、上述した実施の形態との相違点を中心に説明し、同様の事項については、その説明を簡略化または省略する。
次に、図12を参照して、本発明の実施の形態4について説明するが、上述した実施の形態との相違点を中心に説明し、同様の事項については、その説明を簡略化または省略する。
3 サージタンク
4 吸気枝管
5 排気マニホールド
6 燃料インジェクタ
7 吸気ダクト
8 スロットル
10 ECU
20 吸気管圧センサ
21 水温センサ
22 クランク角センサ
23 気筒判別センサ
24 エアフローメータ
25 燃料性状センサ
31,32 排気浄化触媒
51,52,53,54,55,56,57,58 排気マニホールド
Claims (5)
- 多気筒内燃機関が始動されるときに、当初は一部の気筒に対してのみ燃料を供給し、それ以外の気筒である遅延気筒に対する燃料供給を遅れて開始する燃料供給制御手段と、
前記内燃機関の代表温度を取得する代表温度取得手段と、
前記遅延気筒が最初に燃焼するサイクルが開始するタイミングでの機関回転速度である遅延気筒開始回転速度と、機関始動の際に前記内燃機関から出るHC量であるエンジン出ガスHC量の予測値との関係を、少なくとも前記代表温度を含む所定のパラメータに基づいて算出するエンジン出ガスHC量予測手段と、
前記エンジン出ガスHC量予測手段により算出された関係に基づいて、前記遅延気筒開始回転速度の目標値である目標回転速度を算出する目標回転速度算出手段と、
を備え、
前記燃料供給制御手段は、前記遅延気筒開始回転速度が前記目標回転速度付近となるように、前記遅延気筒に対する燃料供給を開始するタイミングを決定することを特徴とする内燃機関の制御装置。 - 前記燃料供給制御手段は、所定の期限を過ぎる場合には、機関回転速度にかかわらず、前記遅延気筒に対する燃料供給を強制的に開始することを特徴とする請求項1記載の内燃機関の制御装置。
- 前記所定のパラメータと、前記目標回転速度とに基づいて、前記期限内において予定される前記内燃機関全体での燃焼の数を補正する燃焼数補正手段を更に備えることを特徴とする請求項2記載の内燃機関の制御装置。
- 前記内燃機関に供給される燃料のアルコール濃度を取得するアルコール濃度取得手段を更に備え、
前記所定のパラメータに前記アルコール濃度が含まれることを特徴とする請求項1乃至3の何れか1項記載の内燃機関の制御装置。 - 前記目標回転速度算出手段は、前記関係において前記エンジン出ガスHC量の予測値の傾きが急変する部分の遅延気筒開始回転速度を前記目標回転速度とすることを特徴とする請求項1乃至4の何れか1項記載の内燃機関の制御装置。
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CN201080067085.5A CN102918241B (zh) | 2010-12-24 | 2010-12-24 | 内燃机的控制装置 |
US13/393,738 US8671902B2 (en) | 2010-12-24 | 2010-12-24 | Control apparatus for internal combustion engine |
BR112012007070-3A BR112012007070B1 (pt) | 2010-12-24 | 2010-12-24 | Aparelho de controle para motor de combustão interna |
JP2012510829A JP5136722B2 (ja) | 2010-12-24 | 2010-12-24 | 内燃機関の制御装置 |
EP10857092.0A EP2657491B1 (en) | 2010-12-24 | 2010-12-24 | Apparatus for controlling internal combustion engine |
IN1963DEN2012 IN2012DN01963A (ja) | 2010-12-24 | 2010-12-24 | |
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JP4924486B2 (ja) * | 2008-03-07 | 2012-04-25 | 日産自動車株式会社 | 車両用内燃機関の吸気制御装置 |
DE102013213697B4 (de) * | 2013-07-12 | 2016-10-27 | Mtu Friedrichshafen Gmbh | Verfahren zum Betreiben einer quantitätsgeregelten Brennkraftmaschine und quantitätsgeregelte Brennkraftmaschine |
US10746108B2 (en) * | 2014-10-20 | 2020-08-18 | Ford Global Technologies, Llc | Methods and system for reactivating engine cylinders |
CN104454168B (zh) * | 2014-12-26 | 2017-02-22 | 长城汽车股份有限公司 | 发动机缸内温度预测装置、预测方法、发动机及车辆 |
JP6235053B2 (ja) * | 2016-02-01 | 2017-11-22 | 株式会社ケーヒン | 内燃機関制御装置 |
JP6418206B2 (ja) * | 2016-08-10 | 2018-11-07 | トヨタ自動車株式会社 | エンジンの始動制御装置 |
DE102018208891A1 (de) * | 2018-06-06 | 2019-12-12 | Ford Global Technologies, Llc | Direkteinspritzende Brennkraftmaschine mit zwei Ventilen je Zylinder |
GB2590952B (en) * | 2020-01-09 | 2022-09-07 | Perkins Engines Co Ltd | Selective cylinder deactivation, particularly in turbocharged diesel engines with high power density |
GB2595290B (en) * | 2020-05-21 | 2023-10-18 | Perkins Engines Co Ltd | Fixed-speed engines |
US11519354B1 (en) | 2021-08-06 | 2022-12-06 | Ford Global Technologies, Llc | Methods and system for stopping an engine |
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CN102918241A (zh) | 2013-02-06 |
EP2657491A4 (en) | 2014-11-19 |
BR112012007070A2 (pt) | 2016-04-19 |
JP5136722B2 (ja) | 2013-02-06 |
CN102918241B (zh) | 2014-01-29 |
BR112012007070B1 (pt) | 2020-09-15 |
EP2657491B1 (en) | 2016-11-02 |
EP2657491A1 (en) | 2013-10-30 |
US20130255630A1 (en) | 2013-10-03 |
JPWO2012086059A1 (ja) | 2014-05-22 |
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US8671902B2 (en) | 2014-03-18 |
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