WO2019043853A1 - 内燃機関 - Google Patents
内燃機関 Download PDFInfo
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- WO2019043853A1 WO2019043853A1 PCT/JP2017/031268 JP2017031268W WO2019043853A1 WO 2019043853 A1 WO2019043853 A1 WO 2019043853A1 JP 2017031268 W JP2017031268 W JP 2017031268W WO 2019043853 A1 WO2019043853 A1 WO 2019043853A1
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- WIPO (PCT)
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- energy
- drive energy
- turbo
- angular velocity
- compressor wheel
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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
- F02D45/00—Electrical control not provided for in groups F02D41/00 - F02D43/00
Definitions
- the present invention relates to an internal combustion engine.
- WO 2017/104030 A1 discloses an internal combustion engine capable of calculating kinetic energy of a turbo rotating body.
- the present invention has been made focusing on such problems, and has an object to effectively utilize exhaust energy when driving a turbo rotating body.
- an internal combustion engine includes an engine body having a plurality of cylinders, a turbine wheel driven by exhaust gas discharged from each cylinder of the engine body, and a turbine wheel And a compressor wheel including at least one blade for compressing air drawn into each cylinder of the engine body, and a predetermined position in the housing for housing the compressor wheel,
- the angular velocity of the compressor wheel is calculated based on the detection result of the passage detection sensor that detects that the blade of the compressor wheel has passed and the passage detection sensor, and the turbo rotor is driven based on the angular velocity of the compressor wheel.
- a drive energy estimation device configured to calculate energy;
- the driving energy of the turbo rotating body is reduced so that the difference value between the actual driving energy of the turbo rotating body calculated by the Ruge estimation device and the reference driving energy of the turbo rotating body calculated based on the operating state of the engine main body
- a controller configured to control parameters that affect the
- exhaust energy can be effectively utilized in driving the turbo rotating body.
- FIG. 1 is a schematic block diagram of an internal combustion engine according to an embodiment of the present invention.
- FIG. 2A is a schematic cross-sectional view of a compressor.
- FIG. 2B is a schematic plan view of the compressor wheel.
- FIG. 3 is a diagram for explaining the detection principle of an eddy current sensor as a passage detection sensor.
- FIG. 4A is a view showing transition of an output value when an eddy current sensor is used as a passage detection sensor.
- FIG. 4B is a diagram showing the transition of the output value when an eddy current sensor is used as the passage detection sensor.
- FIG. 5 is a diagram showing the transition of the angular velocity and kinetic energy of the rotating body of the exhaust gas turbocharger in one cycle of the internal combustion engine.
- FIG. 1 is a schematic block diagram of an internal combustion engine according to an embodiment of the present invention.
- FIG. 2A is a schematic cross-sectional view of a compressor.
- FIG. 2B is a schematic plan view of the compressor
- FIG. 6 is a diagram for explaining the method of calculating the combustion energy of each cylinder and the combustion interval of each cylinder.
- FIG. 7 is a flowchart illustrating angular velocity calculation control of a compressor wheel according to an embodiment of the present invention.
- FIG. 8 is a flowchart illustrating drive energy estimation control of a turbo rotor according to an embodiment of the present invention.
- FIG. 9 is a flowchart illustrating control of an internal combustion engine according to an embodiment of the present invention.
- FIG. 1 is a schematic block diagram of an internal combustion engine 100 according to an embodiment of the present invention.
- the internal combustion engine 100 includes an engine body 1, a fuel injection device 2, an intake device 3, an exhaust device 4, and an electronic control unit 200 for controlling the internal combustion engine 100.
- the engine body 1 burns fuel in a combustion chamber formed in each of the cylinders 10 to generate power for driving, for example, a vehicle.
- the engine body 1 performs compression self-ignition combustion of the fuel in the combustion chamber, but the method of combustion of the fuel is not particularly limited, and the fuel may be spark-ignited combustion in the combustion chamber.
- the fuel injection device 2 includes an electronically controlled fuel injection valve 20, a common rail 21, a supply pump 22, and a fuel tank 23.
- One fuel injection valve 20 is provided for each cylinder 10 so as to face the combustion chamber of each cylinder 10.
- the valve opening time (injection time) and the valve opening timing (injection time) of the fuel injection valve 20 are changed by the control signal from the electronic control unit 200, and when the fuel injection valve 20 is opened, the fuel injection valve 20 Fuel is injected.
- Each fuel injection valve 20 is connected to the common rail 21 via an injection pipe 24.
- the common rail 21 is connected to the fuel tank 23 via a pressure feed pipe 25.
- a supply pump 22 for pressurizing the fuel stored in the fuel tank 23 and supplying it to the common rail 21 is provided in the middle of the pressure feed pipe 25.
- the common rail 21 temporarily stores the high pressure fuel pumped from the supply pump 22. When the fuel injection valve 20 is opened, the high pressure fuel stored in the common rail 21 is injected from the fuel injection valve 20 into the combustion chamber via the injection pipe 24.
- the supply pump 22 is configured to be able to change the discharge amount, and the discharge amount of the supply pump 22 is changed by a control signal from the electronic control unit 200.
- the discharge amount of the supply pump 22 By controlling the discharge amount of the supply pump 22, the fuel pressure in the common rail 21, that is, the injection pressure of the fuel injection valve 20 is controlled.
- the intake device 3 is a device for guiding intake air into a cylinder, and includes an intake passage 30, an intake manifold 31, and an EGR passage 32.
- One end of the intake passage 30 is connected to the air cleaner 34, and the other end is connected to the intake collector 31 a of the intake manifold 31.
- an airflow meter 211, a compressor 6 of the turbocharger 5, an intercooler 35, and a throttle valve 36 are provided in this order from the upstream side.
- the air flow meter 211 detects the flow rate (hereinafter referred to as “intake amount”) of the intake air drawn into the intake passage 30 via the air cleaner 34.
- the compressor 6 includes a compressor housing 61 and a compressor wheel 62 disposed in the compressor housing 61.
- the compressor wheel 62 is rotationally driven by the turbine wheel 72 of the turbocharger 5 coaxially mounted via the shaft 8 and compresses and discharges the intake air flowing into the compressor housing 61.
- the passage detection sensor 301 is attached to the compressor housing 61.
- An output signal of the passage detection sensor 301 is input to the amplifier unit 300.
- the amplifier unit 300 is based on the output result of the passage detection sensor 301. It is configured to be able to carry out various calculations. Details of the passage detection sensor 301 and the amplifier unit 300 will be described later with reference to FIG.
- the intercooler 35 is a heat exchanger for cooling the intake air compressed by the compressor 6 to a high temperature, for example, by the traveling wind or cooling water.
- the throttle valve 36 adjusts the amount of intake air introduced into the intake manifold 31 by changing the passage sectional area of the intake passage 30.
- the throttle valve 36 is driven to open and close by a throttle actuator (not shown), and the opening degree (throttle opening degree) is detected by a throttle sensor (not shown).
- the intake manifold 31 is connected to the engine body 1 and equally distributes the intake air flowing from the intake passage 30 to the cylinders 10.
- the EGR passage 32 is a passage for returning a part of the exhaust gas discharged from each cylinder 10 to the intake passage 30 or the intake manifold 31.
- the EGR passage 32 includes the exhaust manifold 41 and the intake manifold 31. Although it is configured to communicate with the intake collector 31a and return a part of the exhaust gas discharged from each cylinder 10 to the intake collector 31a by a pressure difference, the invention is not limited to this, for example, the exhaust passage 42 and the intake passage 30. And may communicate with each other.
- the exhaust flowing into the EGR passage 32 is referred to as "external EGR gas".
- EGR external EGR in which the external EGR gas is recirculated to the intake collector 31a and hence to the cylinders 10, it is possible to reduce the combustion temperature and suppress the emission of nitrogen oxides (NOx).
- An EGR cooler 37 and an EGR valve 38 are provided in the EGR passage 32 sequentially from the upstream side.
- the EGR cooler 37 is a heat exchanger for cooling the external EGR gas with, for example, traveling air or cooling water.
- the EGR valve 38 is a solenoid valve that can adjust the opening degree continuously or stepwise, and the opening degree is controlled by the electronic control unit 200. By controlling the opening degree of the EGR valve 38 and adjusting the flow rate of the external EGR gas to be recirculated to the intake collector 31a, the EGR rate (the ratio of the EGR gas occupied in the intake) is controlled.
- the exhaust device 4 includes an exhaust manifold 41 and an exhaust passage 42.
- the exhaust manifold 41 is connected to the engine body 1 and collects the exhaust gas discharged from the cylinders 10 and introduces the exhaust gas into the exhaust passage 42.
- the exhaust passage 42 is provided with a turbine 7 of the turbocharger 5 and an exhaust post-treatment device 43 in this order from the upstream side.
- the turbine 7 includes a turbine housing 71 and a turbine wheel 72 disposed in the turbine housing 71.
- the turbine wheel 72 is rotationally driven by the energy of the exhaust flowing into the turbine housing 71, and drives the coaxially mounted compressor wheel 62.
- the exhaust post-treatment device 43 is a device for purifying the exhaust gas and discharging it to the outside air, and includes various catalysts for purifying the harmful substances, a filter for collecting the harmful substances, and the like.
- the electronic control unit 200 is composed of a digital computer, and includes a ROM (read only memory), a RAM (random access memory), a CPU (microprocessor), an input port and an output port connected to each other by a duality bus.
- ROM read only memory
- RAM random access memory
- CPU microprocessor
- the electronic control unit 200 In addition to the output signal of the air flow meter 211 described above, the electronic control unit 200 generates an output pulse every time the crankshaft of the engine body 1 rotates, for example, 15 °, as a signal for calculating the engine rotation speed.
- engine cooling water temperature a temperature of cooling water for cooling the engine main body
- control components such as the fuel injection valve 20, the supply pump 22, the step motor of the throttle valve 36, and the EGR control valve 38 are electrically connected to the electronic control unit 200 through the output port.
- the electronic control unit 200 is connected to the amplifier unit 300 by a CAN (Controller Area Network) communication line, and can mutually transmit and receive data by CAN communication.
- CAN Controller Area Network
- FIG. 2A is a schematic cross-sectional view of the compressor 6.
- FIG. 2B is a schematic plan view of the compressor wheel (impeller) 62.
- the compressor wheel 62 has a central body 621 connected to the turbine wheel 72 (see FIG. 1) of the turbocharger 5 via the shaft 8 and a diameter of the compressor wheel 62 from above the surface of the central body 621. And a plurality of directionally and axially extending blades 622.
- the central body 621 is fixed to the shaft 8 such that its axis L is coaxial with the axis of the shaft 8.
- the compressor wheel 62 is disposed inside the compressor housing 61 so as to be rotatable about the axis L. In addition, when the compressor wheel 62 rotates, the radial end of the blade 622 moves circumferentially along the inner peripheral surface of the compressor housing 61 with a slight gap from the inner peripheral surface. , And disposed inside the compressor housing 61.
- the compressor wheel 62 has twelve blades 622 of the same shape arranged at equal intervals.
- the blades 622 are respectively numbered B1 to B12 for the sake of clarity.
- the number of blades 622 is not limited to twelve and may be more or less than twelve.
- each blade 622 is configured to extend in the radial direction and the axial direction of the compressor wheel 62.
- the plurality of blades 622 may have any shape such as a curved shape as long as the fluid flowing into the compressor 6 can be compressed.
- the blades 622 may not necessarily be arranged at equal intervals, and some or all of the blades 622 may have shapes different from those of other blades.
- the compressor housing 61 has a central passage 611 extending through the center of the compressor housing 61 and an annular passage 612 extending around the central passage 611.
- One end of the central passage 611 is open and constitutes an inlet 613 into which fluid flows.
- an annular passage 612 is disposed around the other end of the central passage 611, and the compressor wheel 62 is disposed in the central passage 611 inside the annular passage 612.
- a passage detection sensor 301 is attached to the compressor housing 61 in order to detect that the blade 622 has passed through a predetermined angular position (predetermined position) in the compressor housing 61.
- the passage detection sensor 301 detects that the blade 622 has passed in front of the detection unit of the passage detection sensor 301.
- the passage detection sensor 301 faces the radial end surface 622 a of the blade 622 of the compressor wheel 62 and is substantially parallel to the normal direction of the radial end surface 622 a of the blade 622.
- the passage detection sensor 301 is attached to the compressor housing 61 so as to be located on the inlet side of the compressor wheel 62.
- the passage detection sensor 301 is attached to the compressor housing 61 so as to be adjacent to the inlet end surface 622 b of the blade 622 of the compressor wheel 62.
- the blades 622 of the compressor wheel 62 gradually increase in temperature from the inlet side to the outlet side. This is because the fluid flowing through the compressor wheel 62 is pressurized from the inlet side to the outlet side.
- the passage detection sensor 301 is attached to the compressor housing 61 so as to be located on the inlet side of the compressor wheel 62, and therefore, is disposed in a relatively low temperature area. Therefore, the influence of heat on the passage detection sensor 301 can be reduced.
- the output value of the passage detection sensor 301 is input to the amplifier unit 300.
- the amplifier unit 300 is integrated with an amplifier for amplifying the output value of the passage detection sensor 301 and a CPU (microprocessor) for calculating the angular velocity of the compressor wheel 62 and the like using the output value amplified by the amplifier. is there.
- the passage detection sensor 301 and the amplifier unit 300 are separated, but the passage detection sensor 301 may be incorporated with the amplifier unit 300, and the passage detection sensor 301 and the amplifier unit 300 may be integrated.
- the electronic control unit 200 may have the function of the amplifier unit 300.
- an eddy current sensor is used as the passage detection sensor 301.
- the eddy current sensor is a sensor that outputs a voltage value corresponding to the distance between the sensor detection unit and the metal substance to be measured.
- the detection principle of the eddy current sensor will be briefly described below with reference to FIG.
- the eddy current sensor has a coil 301a at its detection portion that generates a magnetic field by an AC excitation current.
- an eddy current Y is generated in the blade 622 so as to cancel the magnetic field generated by the coil 301a.
- the intensity of the magnetic field X changes due to the eddy current generated in the blade 622, and as a result, the value of the current flowing through the coil 301a changes. Therefore, it is possible to detect whether or not the blade 622 has passed by detecting a change in voltage value caused by a change in current value flowing to the coil 301 a by the eddy current sensor.
- any sensor may be used as the passage detection sensor 301 for detecting the passage of the blade 622 as long as the passage of the blade 622 can be detected.
- an electromagnetic pickup (MPU) sensor is mentioned, for example.
- the MPU sensor is a sensor having a magnet and a detection coil in its detection unit.
- the magnetic flux penetrating the detection coil changes, and the induced electromotive force of the detection coil changes accordingly.
- the passage of the blade 622 in front of the detection unit of the MPU sensor can be detected.
- an eddy current sensor is used as the passage detection sensor 301 will be described.
- FIGS. 4A and 4B are diagrams showing the transition of the output value (voltage value) of the passage detection sensor 301 when an eddy current sensor is used as the passage detection sensor 301.
- FIG. 4A shows the transition of the output value when the angular velocity of the compressor wheel 62 is relatively slow (for example, the rotation number of the compressor wheel 62 is 200,000 [rpm]), and
- FIG. 4B shows the case where the angular velocity of the compressor wheel 62 is relatively fast.
- the transition of the output value in case the rotation speed of the compressor wheel 62 is 400,000 [rpm] is shown, respectively.
- the output value increases as the distance between the detection unit of the passage detection sensor 301 and the object passing in front of it (the blade 622 in the present embodiment) decreases. Therefore, when the blade 622 passes in front of the detection portion of the passage detection sensor 301, the output value of the passage detection sensor 301 rapidly increases.
- the convexly varying output in FIGS. 4A and 4B means that the blade 622 has passed.
- the numbers B1 to B12 in FIGS. 4A and 4B are the numbers of the blades 622 that have passed in front of the detection unit of the passage detection sensor 301.
- any one of the blades 622 (hereinafter referred to as “reference Each blade 622 passes in front of the passage detection sensor 301 based on the time interval between the passage of the blade) and the passage of the blade passing in front of the passage detection sensor 301 next to the reference blade.
- the angular velocity of the compressor wheel 62 can be accurately calculated each time.
- the angular velocity of the compressor wheel 62 can be accurately calculated.
- kinetic energy KE of the turbo rotating body can be calculated by the following equation (1).
- I is the moment of inertia of the turbo rotor
- ⁇ is the angular velocity of the turbo rotor.
- the moment of inertia I of the turbo rotor can be obtained in advance by calculation or the like from the shape and material of the turbo rotor. Since the angular velocity of the turbo rotor is equal to the angular velocity of the compressor wheel 62, when the angular velocity of the compressor wheel 62 can be accurately calculated, the motion of the turbo rotor at the time when the angular velocity of the compressor wheel 62 is determined The energy KE can be calculated accurately.
- FIG. 5 is a diagram showing the transition of the angular velocity ⁇ of the turbo rotating body and the kinetic energy KE in one cycle of the internal combustion engine 100. As shown in FIG. The horizontal axis in FIG. 5 indicates the crank angle of the engine body 1. The solid line in FIG. 5 indicates the kinetic energy KE of the turbo rotor, and the broken line indicates the angular velocity ⁇ of the turbo rotor.
- the angular velocity ⁇ of the turbo rotating body changes in accordance with the crank angle of the engine body 1.
- the exhaust valve of the first cylinder is opened and the exhaust gas flows out from the combustion chamber, the exhaust gas flowing into the turbine 7 of the turbocharger 5 increases.
- the angular velocity of the turbine wheel 72 increases, and the angular velocity of the compressor wheel 62 also increases accordingly.
- the kinetic energy KE of the turbo rotating body also increases.
- the angular velocity of the compressor wheel 62 rises and then falls, and along with this, the kinetic energy KE of the turbo rotor also increases and then decreases.
- such an angular velocity ⁇ and kinetic energy KE shift similarly in the exhaust strokes of the other cylinders 10 as well. Therefore, in the four-cylinder internal combustion engine 100, the angular velocity ⁇ of the turbo rotating body and the kinetic energy KE fluctuate up and down largely four times in one cycle of the internal combustion engine 100. That is, during one cycle of the internal combustion engine 100, the angular velocity ⁇ and the kinetic energy KE of the turbo rotating body fluctuate up and down a plurality of times according to the number of cylinders of the internal combustion engine 100.
- the amount of increase in kinetic energy KE of the turbo rotor during the exhaust stroke of cylinder No. 4 (hereinafter referred to as “drive energy of turbo rotor”) ⁇ KE is Of the exhaust gas exhausted from the combustion chamber, it is proportional to the energy of the exhaust gas used to drive the turbo rotating body.
- the amount of increase in kinetic energy of the turbo rotor during the exhaust stroke of the first cylinder, the third cylinder and the second cylinder (drive energy ⁇ KE of the turbo rotor) is respectively the first cylinder, the third cylinder and the second cylinder.
- the exhaust gas discharged from the combustion chamber of the cylinder it is proportional to the energy of the exhaust gas used to drive the turbo rotating body.
- the electronic control unit 200 controls the flow rate of the cooling water for cooling the engine body 1 so that the temperature (cooling water temperature) of the engine body 1 becomes a predetermined target temperature.
- the operation of the engine body 1 is performed with the temperature of the engine body 1 lower than the target temperature.
- the engine main body 1 may be operated with the temperature of the engine main body 1 being higher than the target temperature.
- the drive energy ⁇ KE of the turbo rotating body changes according to the temperature of the engine body 1 even if the engine operating conditions (engine rotational speed and engine load) are the same. Specifically, it was found that the drive energy ⁇ KE of the turbo rotating body tends to be smaller as the temperature of the engine body 1 is lower even if the engine operating condition is the same.
- the drive energy ⁇ KEact approaches the reference drive energy ⁇ KEstd.
- the exhaust energy can be effectively utilized in driving the turbo rotating body if it is possible to control the parameters that affect the
- the flow rate of the external EGR gas (the opening degree of the EGR valve 38) can be mentioned.
- the flow rate of the exhaust flowing into the turbine 7 can be controlled to control the differential pressure across the turbine 7, thereby increasing or decreasing the drive energy ⁇ KE. It is.
- the opening degree of the waste gate valve may be mentioned.
- the opening degree of the waste gate valve it is possible to control the differential pressure across the turbine 7 in the same manner as when controlling the flow rate of the external EGR gas, and thereby the drive energy ⁇ KE can be increased or decreased. It is.
- the opening degree of the nozzle vane may be mentioned. By controlling the opening degree of the nozzle vanes, it is possible to control the flow velocity of the exhaust blown to the turbine wheel 72 to control the differential pressure across the turbine 7 and to increase or decrease the drive energy ⁇ KE.
- parameters that affect the drive energy ⁇ KE include a fuel injection amount and an intake air amount.
- a fuel injection amount and an intake air amount By increasing or decreasing the fuel injection amount and the intake air amount, it is possible to increase or decrease the drive energy ⁇ KE by increasing or decreasing the combustion energy generated when the fuel is burned in the combustion chamber of each cylinder 10 and hence the exhaust energy itself. It is.
- the flow rate of the external EGR gas is reduced to increase the flow rate of the exhaust flowing into the turbine 7 without increasing the combustion energy.
- the differential pressure across the turbine 7. Thereby, the deterioration of the fuel efficiency can be suppressed, and the energy of the exhaust can be diverted to the driving energy to be effectively used.
- the fuel injection amount is controlled to reduce the combustion energy itself generated when the fuel is burned in the combustion chamber of each cylinder 10 It is desirable to reduce the excess exhaust energy. According to this configuration, the fuel injection amount can be suppressed to improve the fuel efficiency while effectively utilizing the exhaust energy without waste when driving the turbo rotating body.
- the electronic control unit 200 controls a parameter that affects the drive energy ⁇ KE so that the actual drive energy ⁇ KEact approaches the reference drive energy ⁇ KEstd.
- FIG. 6 is a diagram for explaining a method of calculating the drive energy ⁇ KE of the turbo rotating body.
- the horizontal axis in FIG. 6 indicates the crank angle of the engine body 1.
- the solid line in FIG. 6 indicates the kinetic energy of the turbo rotor, and the broken line indicates the angular velocity of the turbo rotor.
- angular acceleration ⁇ ′ the differential value of the angular velocity ⁇ of the turbo rotor
- amplifier unit 300 each time to calculate an angular velocity omega of the compressor wheel 62, sets the angular velocity omega angular velocity present value omega z of the turbo rotation body, the angular velocity angular acceleration differential value of current value omega z Calculated as the current value ⁇ z '.
- the amplifier unit 300 the absolute value of the angular acceleration current value omega z 'is an angular velocity current value omega z when it becomes below the extreme value determination threshold is preset near zero value, the exhaust of each cylinder 10 Angular velocity at the beginning of the stroke (hereinafter referred to as “minimum angular velocity”) ⁇ L, or angular velocity at a certain point during the exhaust stroke of each cylinder 10 at which the kinetic energy KE of the turbo rotor reaches a maximum value (maximum value) (hereinafter referred to as “maximum angular velocity ') Set as ⁇ H.
- angular velocity current value omega z when the absolute value of the angular acceleration current value omega z 'is equal to or less than extremum determination threshold, whether the angular velocity present value omega z is minimal angular .omega.L, or a maximum angular velocity ⁇ H
- the determination can be made by determining whether or not the angular acceleration previous value ⁇ z-1 ′ calculated immediately before is a positive value.
- amplifier unit 300 sets the angular velocity present value omega z when the absolute value of the angular acceleration current value omega z 'is equal to or less than extremum determining threshold minimum angular velocity .omega.L.
- the angular acceleration previous value ⁇ z-1 ′ is a positive value, ie, when the slope of the broken line in FIG. 6 is positive, it can be determined that the angular velocity ⁇ changes from rising to falling.
- the angular velocity current value omega z when the absolute value of the angular acceleration current value omega z 'is equal to or less than extremum determination threshold is set to the maximum angular velocity .omega.H.
- angular velocity calculation control of the compressor wheel 62 performed by the amplifier unit 300 will be described.
- step S1 the amplifier unit 300 reads the output value of the passage detection sensor 301.
- step S2 the amplifier unit 300 determines whether the elapsed time measurement start flag F1 is set to 0.
- the elapsed time measurement start flag F1 is a flag whose initial value is set to 0, and when the elapsed time measurement start flag F1 is set to 0, the passage detection sensor 301 detects the passage of the blade 622 And set to 1. Then, when the angular velocity and the number of revolutions of the compressor wheel 62 are estimated, they are returned to 0 again. If the elapsed time measurement start flag F1 is set to 0, the amplifier unit 300 proceeds to the process of step S2. On the other hand, if the elapsed time measurement start flag F1 is set to 1, the amplifier unit 300 proceeds to the process of step S5.
- step S3 the amplifier unit 300 determines whether the passage of the blade 622 is detected.
- the blade 622 whose passage is detected in this step S3 becomes any one blade of the plurality of blades, that is, the reference blade.
- the amplifier unit 300 proceeds to the process of step S4.
- the amplifier unit 300 ends the current process.
- step S4 the amplifier unit 300 sets the elapsed time measurement start flag F1 to 1, the reference blade starts measuring the elapsed time t e1 from through the front of the detection portion of the passage detection sensor 301.
- step S5 the amplifier unit 300 calculates a material obtained by integrating the sampling cycle t Smp to the previous value of the elapsed time t e1 as elapsed time t e1.
- the initial value of the elapsed time t e is zero.
- step S6 the amplifier unit 300 determines whether or not the passage detection sensor 301 detects the passage of the blade 622.
- the amplifier unit 300 proceeds to the process of step S7.
- the amplifier unit 300 ends the current process.
- step S7 the amplifier unit 300 calculates the blade passage number i after the reference blade passes in front of the detection unit of the passage detection sensor 301. Specifically, the amplifier unit 300 calculates the blade passage number i by adding 1 to the previous value of the blade passage number i. The initial value of the blade passage number i is zero.
- step S8 the amplifier unit 300 determines whether the blade 622 whose passage has been detected in step S6 is a reference blade. Specifically, the amplifier unit 300 determines whether or not the blade passage number i is a value obtained by multiplying the total number of blades (12 in the present embodiment) by a positive integer n.
- a positive integer n is set, for example, to 1, it can be determined whether or not the compressor wheel 62 has made one revolution in step S8. If, for example, it has been set to 2, whether the compressor wheel 62 has made two revolutions in step S8 It can be determined whether or not. That is, according to the positive integer n, the timing for estimating the angular velocity and the number of rotations of the compressor wheel 62 can be adjusted, and the estimated number of data for the angular velocity and the number of rotations of the compressor wheel 62 per unit time can be adjusted it can.
- the positive integer n is set to 1, but the positive integer n may be set to a value larger than 1 in accordance with the arithmetic capability of the CPU of the amplifier unit 300 and the like.
- step S6 If the blade 622 whose passage has been detected in step S6 is the reference blade, the amplifier unit 300 proceeds to the process of step S9. On the other hand, if the blade 622 whose passage has been detected in step S6 is not the reference blade, the amplifier unit 300 ends the current process.
- step S9 the amplifier unit 300 sets the elapsed time t e1 calculated in step S5 as a reference blade passing time t m. That is, since the amplifier unit 300 sets the positive integer n to 1 in the present embodiment, it is detected that the reference blade first passes in front of the detection unit of the passage detection sensor 301, and then the reference blade time to pass in front of the detecting portion of the passage detection sensor 301 (time the compressor wheel 62 is required for one rotation) is set as a reference blade passing time t m.
- step S10 the amplifier unit 300, based on the reference blade passing time t m, to calculate the angular velocity of the compressor wheel 62. Specifically, the amplifier unit 300 calculates the angular velocity ⁇ of the compressor wheel 62 by substituting the reference blade passing time t m into the following equation (4). Note In step S10, by substituting the reference blade passing time t m the following equation (5), may be calculated together rotational speed N of the compressor wheel 62.
- step S11 the amplifier unit 300 returns the elapsed time t e1 , the blade passage number i, and the elapsed time measurement start flag F1 to the initial values of 0, respectively.
- step S21 the amplifier unit 300 determines whether or not the angular velocity ⁇ of the compressor wheel 62 is newly calculated by the control of the angular velocity calculation of the compressor wheel 62 described above. If the angular velocity ⁇ of the compressor wheel 62 is newly calculated, the amplifier unit 300 proceeds to the process of step S22. On the other hand, if the angular velocity ⁇ of the compressor wheel 62 is not newly calculated, the amplifier unit 300 ends the current process.
- step S22 the amplifier unit 300 reads the angular velocity ⁇ of the compressor wheel 62 that is newly calculated, and the reference blade passing time t m that is used in the calculation, the.
- step S23 the amplifier unit 300 determines whether or not there are two or more data of the angular velocity ⁇ of the compressor wheel 62 read so far. If the data of the angular velocity ⁇ of the compressor wheel 62 read so far is two or more, the amplifier unit 300 proceeds to the process of step S23. On the other hand, when the data of the angular velocity ⁇ of the compressor wheel 62 read so far is 2 points or more, the amplifier unit 300 ends the current process.
- step S24 the amplifier unit 300 calculates an angular acceleration current value ⁇ z 'of the turbo rotating body.
- Amplifier unit 300 Specifically, the angular velocity omega of the newly read compressor wheel 62 now and angular current value omega z of the turbo rotation body, the angular velocity omega of the compressor wheel 62 is loaded before one time, It is assumed that the angular velocity previous value ⁇ z-1 of the turbo rotating body. Then, the amplifier unit 300 substitutes the current angular velocity value ⁇ z , the previous angular velocity value ⁇ z-1 and the reference blade passage time t m read in step S22 into the following equation (6) to obtain the current angular acceleration of the turbo rotor Calculate the value ⁇ z '.
- step S25 the amplifier unit 300 determines whether or not the absolute value of the current value of angular acceleration ⁇ z 'of the turbo rotating body is equal to or less than the extreme value determination threshold.
- the amplifier unit 300 proceeds to the process of step S26 if the angular acceleration current value ⁇ z 'of the turbo rotating body is equal to or less than the extreme value determination threshold value.
- amplifier unit 300 ends the current process if angular acceleration current value ⁇ z 'of the turbo rotating body is larger than the extreme value determination threshold.
- step S26 the amplifier unit 300 determines whether the angular acceleration previous value ⁇ z-1 'of the turbo rotating body is a negative value. If the angular acceleration previous value ⁇ z-1 'of the turbo rotating body is a negative value, the amplifier unit 300 proceeds to the process of step S27. On the other hand, if the angular acceleration previous value ⁇ z-1 ′ of the turbo rotating body is a positive value, the amplifier unit 300 proceeds to the process of step S29.
- step S27 the amplifier unit 300 sets the angular velocity present value omega z turbo rotating body set in step S24 as a minimum angular velocity .omega.L.
- step S28 the amplifier unit 300 sets the flag F2 to one.
- the flag F2 is a flag whose initial value is set to 0.
- step S29 the amplifier unit 300 determines whether the flag F2 is set to 1. If the flag F2 is set to 1, the amplifier unit 300 proceeds to the process of step S30. On the other hand, if the flag F2 is set to 0, the present process is ended.
- step S30 the amplifier unit 300 sets the angular velocity present value omega z of the set turbo rotating body step S24 as the maximum angular velocity .omega.H.
- step S31 amplifier unit 300 substitutes minimum angular velocity ⁇ L and maximum angular velocity ⁇ H set in step S27 and step S30 into equation (7) below to increase the amount of kinetic energy of the turbo rotator, ie, the turbo rotator Drive energy .DELTA.KE is calculated.
- ⁇ KE I ⁇ ⁇ ( ⁇ H 2 ⁇ L 2 ) / 2 ⁇ (7)
- step S32 the amplifier unit 300 returns the flag F2 to the initial value 0.
- control of the internal combustion engine 100 (control of parameters affecting the drive energy ⁇ KE) performed by the electronic control unit 200 will be described with reference to FIG.
- the electronic control unit 200 repeatedly executes this routine in a predetermined operation cycle.
- step S41 the electronic control unit 200 refers to a map created in advance by experiment etc., and based on the engine operating state, the turbo in the engine operating state when the temperature of the engine body 1 is controlled to the target temperature.
- the reference drive energy ⁇ KEstd of the rotating body is calculated.
- step S42 the electronic control unit 200 reads the drive energy ⁇ KE of the turbo rotating body calculated by the amplifier unit 300 as the actual drive energy ⁇ KEact.
- step S43 the electronic control unit 200 determines whether the absolute value of the difference value P obtained by subtracting the actual drive energy ⁇ KEact from the reference drive energy ⁇ KEstd is smaller than a predetermined value ⁇ corresponding to an error. If the absolute value of the difference value P is less than the predetermined value ⁇ , the electronic control unit 200 ends the current process. On the other hand, if the absolute value of difference value P is greater than or equal to predetermined value ⁇ , electronic control unit 200 proceeds to the process of step S44.
- step S44 the electronic control unit 200 determines whether the difference value P is a positive value. If the difference value P is a positive value, that is, if the actual drive energy ⁇ KEact is smaller than the reference drive energy ⁇ KEstd, the electronic control unit 200 proceeds to the process of step S45. On the other hand, if the difference value P is a negative value, that is, if the actual drive energy ⁇ KEact is larger than the reference drive energy ⁇ KEstd, the electronic control unit 200 proceeds to the process of step S46.
- step S45 the electronic control unit 200 controls a parameter that affects the actual drive energy ⁇ KEact such that the actual drive energy ⁇ KEact approaches the reference drive energy ⁇ KEstd, that is, the actual drive energy ⁇ KEact increases.
- the electronic control unit 200 reduces the flow rate of the external EGR gas by reducing the opening degree of the EGR valve 38 and increases the flow rate of the exhaust flowing into the turbine 7.
- step S46 the electronic control unit 200 controls a parameter that affects the actual drive energy ⁇ KEact such that the actual drive energy ⁇ KEact approaches the reference drive energy ⁇ KEstd, that is, the actual drive energy ⁇ KEact decreases.
- the electronic control unit 200 controls the fuel injection amount and the intake air amount to reduce combustion energy. Since the exhaust energy which was excess can be reduced by this, a fuel consumption can be improved, utilizing exhaust energy effectively without waste when driving a turbo rotating body.
- the internal combustion engine 100 is integrated with the engine body 1 having a plurality of cylinders 10, the turbine wheel 72 driven by the exhaust gas discharged from each cylinder 10 of the engine body 1, and the turbine wheel 72. And a compressor wheel 62 having at least one blade 622 and compressing air drawn into each cylinder 10 of the engine body 1, and a housing 61 for housing the compressor wheel 62 and the compressor wheel 62.
- the angular velocity ⁇ of the compressor wheel 62 is calculated based on the detection results of the passage detection sensor 301 which detects that the blade 622 of the compressor wheel 62 has passed at a predetermined position in the Based on the angular velocity ⁇ of 62, the driving energy of the turbo rotating body This is calculated based on the amplifier unit (drive energy estimation device) 300 configured to calculate gear ⁇ KE, the actual driving energy ⁇ KE act of the turbo rotating body calculated by the amplifier unit 300, and the operating state of the engine body 1
- An electronic control unit 200 (control device) configured to control a parameter affecting the drive energy ⁇ KE of the turbo rotor so that the difference value P between the turbo rotor and the reference drive energy ⁇ KEstd becomes smaller Prepare.
- the actual drive energy ⁇ KEact when the temperature of the engine body 1 is lower than the target temperature, or when there is a difference between the actual drive energy ⁇ KEact and the reference drive energy ⁇ KEstd that is greater than the difference considered to be an error, the actual drive Since the energy ⁇ KEact can be brought close to the reference driving energy ⁇ KEstd, exhaust energy can be effectively utilized when driving the turbo rotating body.
- the electronic control unit 200 changes the combustion energy generated when the fuel is burned in the combustion chamber of each cylinder 10 of the engine body 1 Instead, the flow rate or the flow rate of the exhaust flowing into the turbine wheel 72 is controlled as a parameter that affects the drive energy ⁇ KE of the turbo rotating body.
- the energy of the exhaust can be turned to the driving energy and effectively used without deteriorating the fuel consumption.
- the fuel injection amount is controlled as a parameter affecting the drive energy ⁇ KE of the turbo rotating body.
- the fuel injection amount can be reduced to reduce the combustion energy and hence the excess exhaust energy. Therefore, the fuel injection amount can be suppressed to improve the fuel consumption while effectively utilizing the exhaust energy without waste when driving the turbo rotating body.
- the compressor wheel 62 of the compressor 6 of the turbocharger 5 is mentioned as an example of a rotating body, but any rotating body having a blade 622 can calculate the angular velocity is there. Therefore, for example, it is also possible to calculate the angular velocity of an axial flow compressor or the like.
- the compression self-ignition combustion is performed in the engine main body 1
- the spark ignition combustion may be performed in the engine main body 1.
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Abstract
Description
図1は、本発明の一実施形態による内燃機関100の概略構成図である。
図2Aは、コンプレッサ6の概略断面図である。図2Bは、コンプレッサホイール(インペラ)62の概略平面図である。
またコンプレッサハウジング61には、コンプレッサハウジング61内の所定の角度位置(所定位置)をブレード622が通過したことを検出するために、通過検出センサ301が取り付けられる。通過検出センサ301は、通過検出センサ301の検知部の前をブレード622が通過したことを検出する。本実施形態では、通過検出センサ301は、コンプレッサホイール62のブレード622の径方向端面622aに対面するように且つブレード622の径方向端面622aの法線方向と略平行となるように、コンプレッサハウジング61に取り付けられている。
このように通過検出センサ301の検知部の前をブレード622が通過したことを正確に検出することができると、コンプレッサホイール62の角速度を正確に算出することができるようになる。
ターボチャージャ5の内部では、コンプレッサホイール62、タービンホイール72及びシャフト8が一体となって回転する。これら3つを一体のものとしてターボ回転体と称すると、このターボ回転体の運動エネルギKEは、下記式(1)によって算出することができる。
図5は、内燃機関100の1サイクルにおけるターボ回転体の角速度ωと運動エネルギKEとの推移を示す図である。図5中の横軸は機関本体1のクランク角を示している。図5中の実線はターボ回転体の運動エネルギKEを、破線はターボ回転体の角速度ωをそれぞれ示している。
図6は、ターボ回転体の駆動エネルギΔKEの算出方法について説明する図である。図6中の横軸は機関本体1のクランク角を示している。図6中の実線はターボ回転体の運動エネルギを、破線はターボ回転体の角速度をそれぞれ示している。
以下、本実施形態による通過検出センサ301の出力値を利用した内燃機関100の制御について説明する。
<角速度算出制御>
N=60/tm …(5)
次に、図8を参照して、アンプユニット300が実施するターボ回転体の駆動エネルギΔKEの推定制御について説明する。アンプユニット300は、このルーチンを所定の演算周期(=サンプリング周期tsmp)で繰り返し実行する。
次に、図9を参照して、電子制御ユニット200が実施する内燃機関100の制御(駆動エネルギΔKEに影響を与えるパラメータの制御)について説明する。電子制御ユニット200は、このルーチンを所定の演算周期で繰り返し実行する。
本実施形態では電子制御ユニット200は、燃料噴射量及び吸入空気量を制御して燃焼エネルギを少なくする。これにより過剰だった排気エネルギを減少させることができるので、ターボ回転体を駆動するにあたって排気エネルギを無駄なく有効に活用しつつ、燃費を改善させることができる。
1 機関本体
61 コンプレッサハウジング(ハウジング)
62 コンプレッサホイール
622 ブレード
72 タービンホイール
200 電子制御ユニット(制御装置)
300 アンプユニット(駆動エネルギ推定装置)
301 通過検出センサ
Claims (3)
- 複数の気筒を有する機関本体と、
前記機関本体の各気筒から排出される排気によって駆動されるタービンホイールと、当該タービンホイールと一体となって回転し、少なくとも1つのブレードを有して前記機関本体の各気筒に吸入される空気を圧縮するコンプレッサホイールと、を含むターボ回転体と、
前記コンプレッサホイールを収容するハウジング内の所定位置を、当該コンプレッサホイールのブレードが通過したことを検出する通過検出センサと、
前記通過検出センサの検出結果に基づいて、前記コンプレッサホイールの角速度を算出すると共に、当該コンプレッサホイールの角速度に基づいて、前記ターボ回転体の駆動エネルギを算出するように構成された駆動エネルギ推定装置と、
駆動エネルギ推定装置によって算出された前記ターボ回転体の実駆動エネルギと、前記機関本体の運転状態に基づいて算出される前記ターボ回転体の基準駆動エネルギとの差分値が小さくなるように、前記ターボ回転体の駆動エネルギに影響を与えるパラメータを制御するように構成された制御装置と、
を備える内燃機関。 - 前記制御装置は、
前記実駆動エネルギが、前記基準駆動エネルギよりも小さいときは、前記機関本体の各気筒の燃焼室で燃料を燃焼させたときに生じる燃焼エネルギを変化させずに、前記ターボ回転体の駆動エネルギに影響を与えるパラメータとして、前記タービンホイールに流入する排気の流量又は流速を制御するように構成される、
請求項1に記載の内燃機関。 - 前記制御装置は、
前記実駆動エネルギが、前記基準駆動エネルギよりも大きいときは、前記機関本体の各気筒の燃焼室で燃料を燃焼させたときに生じる燃焼エネルギが小さくなるように、前記ターボ回転体の駆動エネルギに影響を与えるパラメータとして燃料噴射量を制御するように構成される、
請求項1又は請求項2に記載の内燃機関。
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JP2008223527A (ja) * | 2007-03-09 | 2008-09-25 | Toyota Motor Corp | ターボ過給機制御システム |
JP2013104333A (ja) * | 2011-11-11 | 2013-05-30 | Yanmar Co Ltd | エンジン |
JP2013194682A (ja) * | 2012-03-22 | 2013-09-30 | Yanmar Co Ltd | 多気筒エンジン |
WO2017104030A1 (ja) | 2015-12-16 | 2017-06-22 | 株式会社 電子応用 | 内燃機関 |
JP2017115758A (ja) * | 2015-12-25 | 2017-06-29 | マツダ株式会社 | エンジンの排気制御装置 |
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JP2008223527A (ja) * | 2007-03-09 | 2008-09-25 | Toyota Motor Corp | ターボ過給機制御システム |
JP2013104333A (ja) * | 2011-11-11 | 2013-05-30 | Yanmar Co Ltd | エンジン |
JP2013194682A (ja) * | 2012-03-22 | 2013-09-30 | Yanmar Co Ltd | 多気筒エンジン |
WO2017104030A1 (ja) | 2015-12-16 | 2017-06-22 | 株式会社 電子応用 | 内燃機関 |
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