WO2009130792A1 - 内燃機関の過給機制御装置 - Google Patents
内燃機関の過給機制御装置 Download PDFInfo
- Publication number
- WO2009130792A1 WO2009130792A1 PCT/JP2008/058134 JP2008058134W WO2009130792A1 WO 2009130792 A1 WO2009130792 A1 WO 2009130792A1 JP 2008058134 W JP2008058134 W JP 2008058134W WO 2009130792 A1 WO2009130792 A1 WO 2009130792A1
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- WO
- WIPO (PCT)
- Prior art keywords
- control
- air amount
- turbocharger
- supercharger
- superchargers
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/007—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in parallel, e.g. at least one pump supplying alternatively
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/001—Engines characterised by provision of pumps driven at least for part of the time by exhaust using exhaust drives arranged in parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/16—Other safety measures for, or other control of, pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
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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
- F02D41/18—Circuit arrangements for generating control signals by measuring intake air flow
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to an apparatus for controlling two superchargers arranged in parallel in an intake passage and an exhaust passage.
- Patent Document 1 describes an example of an internal combustion engine in which a primary turbocharger and a secondary turbocharger having a larger capacity are arranged in parallel. At least the primary turbocharger is variable. It is configured as a nozzle-type supercharger. In this document, the supercharging pressure is appropriately controlled by controlling the variable nozzle opening of the turbocharger in accordance with the rotational speed of the internal combustion engine.
- the present invention has been made in order to solve the above-described problems, and is capable of supercharging an internal combustion engine that can control a supercharging pressure over a wide range using a variable supercharging mechanism without generating a surge. It is an object to provide a machine control device.
- a supercharger control device for an internal combustion engine includes first and second superchargers arranged in parallel to an intake passage and an exhaust passage, the first supercharger, and the first supercharger.
- Control means for performing air amount ratio control for controlling the air amount of the first and second superchargers so that the air amount ratio of the second supercharger falls within a predetermined range.
- the first and second superchargers are arranged in parallel to the intake passage and the exhaust passage. And the air quantity of the 1st and 2nd supercharger is controlled so that the air quantity ratio of the 1st supercharger and the 2nd supercharger may be in a predetermined range. This prevents a surge from occurring in the first and second superchargers.
- At least one of the first and second superchargers includes a variable supercharging mechanism, and the control means includes the first and second superchargers.
- a target air amount ratio is determined, and the variable supercharging mechanism is controlled so that an actual air amount ratio of the first and second superchargers becomes the target air amount ratio.
- an air amount ratio that does not cause a surge in each of the first and second superchargers is set as a target air amount ratio, and the variable supercharging mechanism is controlled with that as a target.
- the supercharger control device includes air amount detection means for detecting the air amount of the first and second superchargers, and the control means is detected by the air amount detection means.
- the actual air amount ratio is determined based on the air amount.
- the second supercharger has a larger capacity than the first supercharger
- the control means includes the first and second superchargers.
- the control unit executes the supercharging pressure control for feedback control of the air amount so that the supercharging pressures of the second supercharger each become a target supercharging pressure. Is made smaller than the feedback control amount of the first supercharger. Thereby, the difference in the sensitivity of the feedback control resulting from the difference in the capacity of the supercharger can be adjusted.
- the first and second superchargers include a variable supercharging mechanism
- the control means includes the first and second superchargers.
- the air pressure ratio control is executed in one of the first and second superchargers, and the air pressure feedback control is performed in the other one of the first and second turbochargers so that the supercharging pressure becomes the target supercharging pressure. I do.
- one of the two superchargers performs the supercharging pressure control and the other performs the air amount control, so that it is possible to perform the supercharging pressure control over a wide range and with high accuracy while preventing the occurrence of a surge.
- control means executes the air amount ratio control when the internal combustion engine is decelerated.
- the control means executes the air amount ratio control when the internal combustion engine is decelerated.
- FIG. 1 is a schematic view showing a configuration of a vehicle to which a supercharger control device for an internal combustion engine according to the present embodiment is applied.
- solid arrows indicate gas flow
- broken arrows indicate signal input / output.
- the vehicle mainly includes an air cleaner 2, an intake passage 3, a first turbocharger 4, a second turbocharger 5, an intake air switching valve 6, a reed valve 7, an internal combustion engine 8, and the like. , A supercharging pressure sensor 9, an exhaust passage 10, an EGR passage 11, an EGR valve 14, an exhaust switching valve 15, an exhaust bypass valve 16, and an ECU (Engine Control Unit) 50.
- an air cleaner 2 an intake passage 3, a first turbocharger 4, a second turbocharger 5, an intake air switching valve 6, a reed valve 7, an internal combustion engine 8, and the like.
- a supercharging pressure sensor 9 an exhaust passage 10, an EGR passage 11, an EGR valve 14, an exhaust switching valve 15, an exhaust bypass valve 16, and an ECU (Engine Control Unit) 50.
- the air cleaner 2 purifies the air (intake air) acquired from the outside and supplies it to the intake passage 3.
- the intake passage 3 is branched into intake passages 3a and 3b on the way.
- An air flow meter 17 is provided upstream of the branch position of the intake passage 3, and an air flow meter 18 is provided in the intake passage 3 a.
- the air flow meters 17 and 18 detect the flow rates of intake air (fresh air) flowing through the intake passages 3 and 3a, respectively, and supply detection signals S17 and S18 to the ECU 50.
- the air flow meter 17 outputs a detection signal S17 indicating the total intake flow rate flowing through the intake passages 3a and 3b
- the air flow meter 18 outputs a detection signal S18 indicating the intake flow rate flowing through the intake passage 3a.
- the ECU 50 can calculate the intake flow rate flowing through the intake passage 3b by calculating the difference between the detection signals S17 and S18.
- the compressor 4a of the turbocharger 4 is disposed in the intake passage 3a, and the compressor 5a of the turbocharger 5 is disposed in the intake passage 3b.
- the compressors 4a and 5a compress the intake air that passes through the intake passages 3a and 3b, respectively.
- a throttle valve 19 is provided downstream from the joining position of the intake passages 3a and 3b.
- the throttle valve 19 is a valve for controlling the intake flow rate, and its opening degree is controlled by a control signal S19 supplied from the ECU 50.
- the intake passage 3b is provided with an intake switching valve 6 and a reed valve 7.
- the intake switching valve 6 is configured to be opened and closed by a control signal S6 supplied from the ECU 50 so that the flow rate of intake air passing through the intake passage 3b can be adjusted. For example, by opening and closing the intake air switching valve 6, it is possible to switch the intake air flow / blockage in the intake passage 3b.
- the reed valve 7 is configured to open when the pressure in the passage exceeds a predetermined value.
- a boost pressure sensor 9 is provided at a position downstream of the throttle valve 19 in the intake passage 3.
- the supercharging pressure sensor 9 detects the pressure of supercharged intake air (hereinafter also referred to as “actual supercharging pressure”) and supplies a detection signal S9 corresponding to the actual supercharging pressure to the ECU 50.
- the internal combustion engine 8 is configured as a V-type 8-cylinder engine in which four cylinders (cylinders) 8La and 8Ra are provided in each of the left and right banks (cylinder groups) 8L and 8R.
- the internal combustion engine 8 is a device that generates power by burning an air-fuel mixture of intake air and fuel supplied from the intake passage 3.
- the internal combustion engine 8 is constituted by, for example, a gasoline engine or a diesel engine.
- the exhaust gas generated by the combustion in the internal combustion engine 8 is discharged to the exhaust passage 10.
- this invention is not limited to comprising the internal combustion engine 8 by 8 cylinders.
- the EGR passage 11 is connected to the exhaust passage 10.
- the EGR passage 11 has one end connected to the exhaust passage 10 and the other end connected to the intake passage 3.
- the EGR passage 11 is a passage for returning exhaust gas (EGR gas) to the intake system.
- the EGR passage 11 is provided with an EGR cooler 12, an EGR valve 14, a bypass passage 11a, and a bypass valve 13.
- the EGR cooler 12 is a device that cools the EGR gas
- the EGR valve 14 is a valve that adjusts the flow rate of the EGR gas that passes through the EGR passage 11, in other words, a valve that adjusts the amount of EGR gas recirculated to the intake system.
- the opening degree of the EGR valve 14 is controlled by a control signal S14 supplied from the ECU 50.
- the bypass passage 11a is a passage that bypasses the EGR cooler 12, and a bypass valve 13 is provided. The flow rate of the EGR gas passing through the bypass passage 11a is adjusted by the bypass valve 13.
- the exhaust passage 10 is branched into exhaust passages 10a and 10b, and the turbine 4b of the turbocharger 4 is disposed in the exhaust passage 10a.
- the turbine 5b of the turbocharger 5 is disposed in the exhaust passage 10b. Is arranged.
- the turbines 4b and 5b are rotated by exhaust gas passing through the exhaust passages 10a and 10b, respectively.
- the rotational torque of the turbines 4b and 5b is transmitted to the compressor 4a in the turbocharger 4 and the compressor 5a in the turbocharger 5 to rotate and rotate (ie, supercharged).
- the first turbocharger 4 is configured as a low-capacity low-speed supercharger with a large supercharging capability in the low and medium speed range, and the second turbocharger 5 is supercharged in the medium and high speed range. It is configured as a large-capacity, high-speed supercharger with a large supply capacity.
- the turbochargers 4 and 5 include variable nozzles (VN: Variable Nozzle) 4c and 5c as variable supercharging mechanisms, respectively.
- VN Variable Nozzle
- the opening of the variable nozzles 4c and 5c is adjusted by control signals S4 and S5 supplied from the ECU 50.
- S4 and S5 supplied from the ECU 50.
- By closing the variable nozzle the supercharging pressure of the turbocharger increases, and by opening the variable nozzle, the supercharging pressure decreases.
- both turbochargers 4 and 5 are configured as variable turbochargers including variable nozzles 4c and 5c.
- turbochargers are provided in each embodiment of the present invention described later. There are cases where only 4 is configured as a variable turbocharger, and where both turbochargers 4 and 5 are configured as variable turbochargers.
- the exhaust passage 10b is provided with an exhaust switching valve 15 and an exhaust bypass passage 10ba.
- the exhaust gas switching valve 15 is controlled to be opened and closed by a control signal S15 supplied from the ECU 50, and is configured to be able to adjust the flow rate of the exhaust gas passing through the exhaust passage 10b. For example, by opening and closing the exhaust gas switching valve 15, it is possible to switch the flow / blocking of the exhaust gas in the exhaust passage 10b.
- the exhaust bypass passage 10ba is configured as a passage that bypasses the exhaust passage 10b in which the exhaust switching valve 15 is provided. Specifically, the exhaust bypass passage 10ba is configured to have a smaller passage diameter than the exhaust passage 10b in which the exhaust switching valve 15 is provided.
- An exhaust bypass valve 16 is provided in the exhaust bypass passage 10ba. The exhaust bypass valve 16 adjusts the flow rate of the exhaust gas passing through the exhaust bypass passage 10ba.
- ECU50 is comprised including CPU, ROM, RAM, an A / D converter, etc. which are not illustrated.
- the ECU 50 performs in-vehicle control based on outputs supplied from various sensors in the vehicle. Specifically, the ECU 50 acquires the actual boost pressure from the boost pressure sensor 9, and based on the actual boost pressure and the like, the intake air switching valve 6, the EGR valve 14, the exhaust gas switching valve 15, and the exhaust gas bypass. Control the valve 16 and the like.
- the ECU 50 controls the intake switching valve 6, the exhaust switching valve 15, and the exhaust bypass valve 16 to operate only the first turbocharger 4 (referred to as “one turbo mode”). And a mode for switching between a mode for operating both the first and second turbochargers 4 and 5 (referred to as “two turbo mode”).
- the ECU 50 executes switching from the single turbo mode to the double turbo mode and switching from the double turbo mode to the single turbo mode based on the operating state, for example, the engine speed and the required torque. To do. Basically, supercharging is performed in the single turbo mode in the low speed rotation region of the internal combustion engine, and supercharging is performed in the two turbo mode during acceleration or in the high speed rotation region.
- the mode is switched by the ECU 50 controlling the intake switching valve 6, the exhaust switching valve 15, and the exhaust bypass valve 16.
- the ECU 50 controls the intake switching valve 6, the exhaust switching valve 15, and the exhaust bypass valve 16 from closed to open.
- the ECU 50 basically performs switching by opening the exhaust bypass valve 16, the exhaust switching valve 15, and the intake switching valve 6 in this order. More specifically, the exhaust bypass valve 16 is first opened little by little, the exhaust switching valve 15 is opened when a predetermined condition is satisfied in this state, and then the intake switching valve 6 is opened.
- the exhaust bypass valve 16 is first opened a little by supplying the turbocharger 5 with a relatively small flow rate of exhaust gas (because the diameter of the exhaust bypass passage 10ba is small). Is to gradually operate (ie, run up). In other words, by opening the exhaust gas switching valve 15 first, it is possible to prevent a relatively large flow rate of exhaust gas from flowing into the turbocharger 5 at a stretch and causing a torque shock or the like.
- the ECU 50 controls the intake switching valve 6, the exhaust switching valve 15, and the exhaust bypass valve 16 from open to closed in the same manner as described above.
- FIG. 2 is a graph showing the relationship between the variable nozzle opening and the boost pressure of each turbocharger when the two turbochargers are variable turbochargers.
- the horizontal axis represents the variable nozzle (VN) opening of the first turbocharger 4
- the vertical axis represents the supercharging pressure.
- the graph 60a shows the supercharging pressure when the variable nozzle opening of the second turbocharger 5 is fully closed
- the graph 60b shows the variable nozzle opening of the second turbocharger 5 being intermediate open
- the graph 60c shows the supercharging pressure when the variable nozzle opening degree of the second turbocharger 5 is fully open.
- the supercharging pressure indicated by each of the graphs 60a to 60c is the supercharging pressure of the entire system, that is, the supercharging pressure by the two turbochargers.
- FIG. 2 shows that the supercharging pressure can be controlled over a wide range by configuring both turbochargers as variable turbochargers. That is, if only the first turbocharger 4 is configured as a variable turbocharger, the second turbocharger 5 is equivalent to fully closing the variable nozzle.
- the controllable range is limited to the range indicated by the graph 60 a, that is, the range of the supercharging pressure indicated by the arrow 85.
- the second turbocharger 5 is also configured as a variable turbocharger
- the range of the graphs 60a to 60c, that is, the arrows are controlled by controlling the variable nozzle openings of the two turbochargers.
- the supercharging pressure can be controlled in a wide range indicated by 86.
- FIG. 3 shows operation limit characteristics of the first turbocharger 4 and the second turbocharger 5, specifically, surge limit characteristics and rotation limit characteristics.
- the horizontal axis indicates the amount of air flowing through each turbocharger, and the vertical axis indicates the pressure ratio.
- the “pressure ratio” refers to the ratio of the supercharging pressure to the atmospheric pressure, and the two turbochargers have the same value.
- ⁇ Turbochargers have rotation limits. If the pressure ratio or the air amount of the turbocharger increases beyond the rotation limit, the turbocharger may be damaged.
- a solid line graph 81 shows the rotation limit characteristic of the first turbocharger 4
- a broken line graph 82 shows the rotation limit characteristic of the second turbocharger. The reason why the two rotation limit characteristics are different is that the capacities of the two turbochargers are different. In order to prevent the turbocharger from being damaged, it is necessary to maintain the operating point determined by the air amount and the pressure ratio in the lower left region from the rotation limit characteristic.
- a solid line graph 71 indicates the surge limit characteristic of the first turbocharger 4
- a broken line graph 72 indicates the surge limit characteristic of the second turbocharger 5.
- the air amounts of the two turbochargers may be controlled to be equal.
- the capacity of the two turbochargers is different as described above. Accordingly, when the air amounts of the two turbochargers are made equal, the surge limit characteristic 72 of the second turbocharger 5 has the surge of the first turbocharger 4 as understood from FIG. Since it is in the region on the right side of the limit characteristic 71, the second turbocharger 5 having a large capacity is more likely to surge. Therefore, in the present invention, the air amount of each turbocharger is controlled so that the two turbochargers have the same margin with respect to their respective surge limits. Specifically, as shown in FIG.
- the first turbocharger 4 operates at an operating point P1 having a predetermined margin (hereinafter referred to as “surge margin”) M1 from the surge limit characteristic 71. Control the amount of air.
- This air amount control is realized by controlling the variable nozzle opening.
- the two turbochargers operate in a state having an equivalent margin with respect to their respective surge limits, and it is possible to prevent a surge from occurring in any of the turbochargers.
- the air amount GA1 for operating the first turbocharger 4 at the operating point P1 is a value within a predetermined range, more preferably a predetermined target air amount ratio (GA1 / GA2), or
- the variable nozzle openings of the first and second turbochargers are controlled. Thereby, generation
- specific control in each embodiment will be described.
- the first turbocharger 4 is configured as a variable turbocharger
- the second turbocharger 5 is a turbocharger having no variable nozzle.
- the ECU 50 controls the opening of the variable nozzle 4c so that the actual supercharging pressure of the first turbocharger 4 matches the target supercharging pressure.
- the target boost pressure is determined based on the operating state, for example, based on the engine speed and the required torque. This control is called “supercharging pressure control” or “supercharging pressure feedback (F / B) control”.
- the ratio of the amount of air flowing through the turbochargers 4 and 5 varies according to the opening degree of the variable nozzle 4c of the turbocharger 4. Specifically, when the variable nozzle 4c is closed, the amount of air in the first turbocharger 4 decreases, and the amount of air in the second turbocharger 5 increases accordingly. Conversely, when the variable nozzle is opened, the air amount of the first turbocharger 4 increases, and the air amount of the second turbocharger 5 decreases accordingly.
- the amount of air is excessively reduced, a surge occurs as described above.
- the air amount ratio of the two turbochargers is set so that the surge margins of the two turbochargers are equal, specifically as described with reference to FIG.
- the opening degree of the variable nozzle 4c of the first turbocharger is controlled so that becomes a predetermined target air amount ratio. This control is called “air amount ratio control”.
- FIG. 4 is a graph showing an operating state of the first turbocharger according to the first embodiment.
- FIG. 4 (A) shows the time change of the supercharging pressure of the first turbocharger
- FIG. 4 (B) shows the first change with respect to the total air amount GAall (the sum of the air amounts of the first and second turbo).
- the time change of the ratio of the air amount GA1 of one turbo ie, the air amount ratio GA1 / GAall
- FIG. 4C shows the time change of the variable nozzle opening of the first turbocharger.
- FIGS. 4A to 4C it is assumed that the operation is performed in the single turbo mode until time tc and the mode is switched to the two turbo mode at time tc.
- the opening degree of the variable nozzle 4c is controlled by the supercharging pressure control so that the actual supercharging pressure becomes the target supercharging pressure.
- the A broken line 94a in FIG. 4B indicates an air amount ratio of the first turbocharger 4 in the single turbo mode. This air amount ratio corresponds to the air amount when the actual supercharging pressure becomes equal to the target supercharging pressure.
- the variable nozzle 4c is controlled so that the air amounts of the first and second turbochargers coincide with a predetermined air amount ratio at which the respective surge margins are equal.
- a broken line 94b indicates the air amount ratio of the first turbocharger at this time.
- the opening degree of the variable nozzle 4c of the first turbocharger 4 is controlled by the supercharging pressure control. From time tc, the opening degree of the variable nozzles 4c and 5c is controlled so that the first and second turbochargers have a predetermined target air amount ratio in which the respective surge margins are equal. .
- FIG. 5 is a flowchart of supercharger control according to the first embodiment.
- the ECU 50 determines whether or not the operating state of the internal combustion engine is in the single turbo mode operating range (step S101). When the operating range is in the single turbo mode, the ECU 50 executes supercharging pressure control (step S103). On the other hand, when the operating range is not in the single turbo mode (step S101; No), the ECU 50 determines whether the operating range is in the dual turbo mode (step S102). If it is in the two-turbo mode operating range, the ECU 50 executes air amount ratio control (step S104). On the other hand, when the operating range is not in the two turbo mode (step S102; No), the mode switching control between the single turbo mode and the two turbo mode is performed (step S105).
- FIG. 6 is a flowchart of the supercharging pressure control.
- the ECU 50 determines a target boost pressure based on the operating state of the internal combustion engine, specifically, the engine speed, the required torque, and the like (step S201).
- the ECU 50 acquires the actual boost pressure from the detection signal S9 from the boost pressure sensor 9 (step S202).
- the ECU 50 feedback-controls the variable nozzle opening of the turbocharger so that the actual supercharging pressure becomes equal to the target supercharging pressure.
- step S203 when the actual supercharging pressure is lower than the target supercharging pressure (step S203; Yes), the ECU 50 closes the variable nozzle opening of the turbocharger by a predetermined amount (step S204).
- step S204 when the actual supercharging pressure is higher than the target supercharging pressure (step S204; No), the ECU 50 opens the variable nozzle opening of the turbocharger by a predetermined amount (step S205).
- the variable nozzle opening is feedback-controlled so that the actual supercharging pressure becomes equal to the target supercharging pressure. Note that during actual driving of the vehicle, the driving state changes from moment to moment, and the target supercharging pressure fluctuates, so the variable nozzle opening is adjusted to follow it.
- FIG. 7 is a flowchart of the air amount ratio control.
- the ECU 50 determines a target air amount ratio (step S301). Specifically, this is performed as described with reference to FIGS. That is, the ECU 50 acquires in advance the limit characteristics 71, 72, 81, 82 of the two turbochargers illustrated in FIG. 3, and holds them in a state such as a map. Then, the ECU 50 determines the current pressure ratio based on the detection signal S9 from the supercharging pressure sensor 9 and the atmospheric pressure. Thereby, the broken line 75 in FIG. 3 is determined.
- the ECU 50 determines the operating point P1 of the first turbocharger 4 so as to have a predetermined surge margin M1 from the surge limit indicated by the surge limit characteristic 71 on the broken line 75, and the surge limit characteristic 72 is
- the description of FIG. 4 is for the latter case.
- the ECU 50 obtains the actual air amount ratio (also referred to as “actual air amount ratio”) based on the detection signals S17 and S18 from the air flow meters 17 and 18 (step S302). ). Then, the ECU 50 controls the variable nozzle opening of the turbocharger so that the actual air amount ratio becomes equal to the target air amount ratio. Specifically, when the actual air amount ratio is smaller than the target air amount ratio (step S303; Yes), the ECU 50 closes the variable nozzle opening of the turbocharger by a predetermined amount (step S304).
- the actual air amount ratio is smaller than the target air amount ratio (step S303; Yes)
- the ECU 50 closes the variable nozzle opening of the turbocharger by a predetermined amount (step S304).
- step S304 when the actual air amount ratio is larger than the target air amount ratio (step S304; No), the ECU 50 opens the variable nozzle opening of the turbocharger by a predetermined amount (step S305).
- the variable nozzle opening degree is feedback-controlled so that the actual air amount ratio becomes equal to the target air amount ratio. Note that the supercharging pressure fluctuates during actual driving of the vehicle, and the target air amount ratio changes accordingly, so that the variable nozzle opening is adjusted to follow it.
- the target air amount ratio is determined, and the variable nozzle opening is controlled so that the actual air amount ratio becomes equal to the target air amount ratio.
- feed-forward control may be performed on the variable nozzle opening so that an air amount ratio in a predetermined range that is acceptable as a result is obtained.
- the air amount ratio control is executed in the two-turbo mode. While being able to control in a wide range, it is possible to prevent the occurrence of surge in each turbocharger.
- the second embodiment is an example in which both turbochargers are variable turbochargers.
- the supercharging pressure control is executed as in the first embodiment.
- one of the two turbochargers performs the supercharging pressure control, and the other executes the air amount ratio control.
- the contents of the supercharging pressure control and the air amount ratio control are the same as in the first embodiment.
- FIG. 8 is a supercharger control flowchart according to the second embodiment.
- the ECU 50 determines whether or not the operating state of the internal combustion engine is in the single turbo mode operating range (step S401). If the operating range is in the single turbo mode, the ECU 50 executes supercharging pressure control (step S403). On the other hand, when it is not the operating range of the single turbo mode (step S401; No), the ECU 50 determines whether or not it is the operating range of the double turbo mode (step S402). When it is not in the operation range of the two turbo mode (step S402; No), the ECU 50 performs mode switching control between the single turbo mode and the two turbo mode (step S406).
- the ECU 50 executes the air amount ratio control with one turbocharger (step S404) and the supercharging pressure control with the other turbocharger (step S405). ).
- the turbocharger performs the supercharging pressure control by controlling the variable nozzle opening so as to obtain the target supercharging pressure after accepting the change.
- the air amount ratio on the turbocharger side that is executing the air amount ratio control is changed accordingly.
- the turbocharger accepts the change and controls the air pressure ratio by controlling the variable nozzle opening so that the target air amount ratio is obtained.
- the two turbochargers always perform their own control while accepting the influence of the control by the other party. Therefore, it is possible to prevent the occurrence of surge while accurately controlling the supercharging pressure over a wide range.
- FIG. 9 is a diagram for explaining how a surge occurs during deceleration.
- a graph 71 shows the surge limit characteristic
- a graph 81 shows the rotation limit characteristic.
- each turbocharger is a variable turbocharger
- the pressure ratio can be reduced by opening the variable nozzle and surge can be prevented.
- the capacity of the two turbochargers is If they are different, if the variable nozzles of the two turbochargers are simply fully opened, the supercharging pressure rises conversely due to the deviation of the exhaust gas amount, and a surge tends to occur. Therefore, in the third embodiment, the air amount ratio control is performed so as to ensure the surge margin of each turbocharger when the internal combustion engine is decelerated.
- FIG. 10 is a flowchart of supercharger control according to the third embodiment.
- the ECU 50 determines whether or not the operating state of the internal combustion engine is in the two-turbo mode operating range (step S501). If it is in the two-turbo mode operating range, the ECU 50 determines whether or not the vehicle is decelerating (step S502). For example, when the throttle opening is fully closed and the engine speed is equal to or lower than a predetermined speed, the ECU 50 determines that the vehicle is in a deceleration state.
- step S504 If it is determined that the vehicle is decelerating (step S502; Yes), the ECU 50 executes air amount ratio control (step S504).
- the air amount ratio control method here is basically the same as in the first and second embodiments.
- two turbochargers are added in addition to the condition that the surge margins of the two turbochargers are equal as in the first and second embodiments. You may add the conditions that the quantity of exhaust gas which flows into the turbine of a machine becomes the same or near quantity. By adding this condition, it is possible to suppress the deviation of the exhaust gas flow rate between the two turbochargers, and to reliably reduce the pressure ratio and prevent surges.
- step S501 when the operating range is not in the two-turbo mode (step S501; No) and when not in the deceleration state (step S502; No), the ECU 50 executes supercharging pressure control (step S503).
- This supercharging pressure control is the same as in the first and second embodiments. In the example shown in FIG. 10, the supercharging pressure control is executed when the vehicle is not in a deceleration state. Instead, the air amount ratio control may be executed even when the vehicle is not in a deceleration state. .
- the basic control contents are the same between the deceleration state and the case where the deceleration state is not, but the amount of exhaust gas flowing through the turbines of the two turbochargers is the same or close, for example.
- the target air amount ratio may be varied by adding a condition such as
- the two turbochargers are variable turbochargers. Also in this case, basically the same control as the flowchart shown in FIG. 10 is executed. However, as a condition for determining the target air amount ratio, the condition that the surge margins of the two turbochargers are equal, and the amount of exhaust gas flowing through the turbines of the two turbochargers are the same or close to each other. In addition to the above condition, a condition may be added in which the variable nozzle of each turbocharger is set to an opening degree that is as close to full opening as possible so that the supercharging pressure becomes low.
- variable nozzle of the first turbocharger 4 having a small capacity is fully opened and the variable nozzle of the second turbocharger 5 having a large capacity is opened. It is preferable to set the opening to be slightly closed from fully open. Thereby, the deviation of the exhaust gas flow rate between the two turbochargers can be suppressed, and the pressure ratio can be reliably reduced to prevent a surge.
- the two turbochargers are both variable turbochargers
- the same air amount ratio control may be performed in the other turbocharger, or the supercharging pressure control may be performed in the other turbocharger as in the second embodiment.
- the two turbochargers execute the supercharging pressure control.
- the decelerating state is reached, one turbocharger continues the supercharging pressure control and the other turbocharger It is good also as performing said air quantity ratio control with a supercharger.
- the occurrence of a surge is surely prevented by executing the air amount ratio control when the vehicle is decelerated, which is particularly susceptible to a surge.
- the two turbochargers are both configured as variable turbochargers.
- supercharging pressure control is executed by two turbochargers.
- the supercharging pressure can be accurately controlled over a wide range covered by the graphs 60a to 60c. Therefore, in the second embodiment, in order to maximize the control range of the supercharging pressure, the supercharging pressure control is executed by two turbochargers in the two turbo mode.
- the control amount is adjusted based on the difference in the capacity of the turbocharger. That is, since the turbocharger having a larger capacity has higher sensitivity of the supercharging pressure with respect to the control amount of the variable nozzle, the control amount (feedback control amount) of the variable nozzle opening is reduced.
- the control amount of the second turbocharger having a large capacity is made smaller than the control amount of the first turbocharger having a small capacity.
- the contents of the supercharging pressure control are the same as those described in the first embodiment.
- the above example is for the case where the two turbochargers both perform the supercharging pressure control, but the same idea may be applied to the above second embodiment.
- the two turbochargers control different target values, that is, the target supercharging pressure and the target air amount ratio, the influence of one control on the other increases, and interference easily occurs. It is possible.
- a method of lowering the gain of each supercharging pressure control is conceivable. However, the followability to the target is lowered.
- the control amount is adjusted according to the capacity of each turbocharger. . Specifically, the control amount by the second turbocharger having a large capacity is made smaller than the control amount of the first turbocharger. Thereby, interference in the case where two controls are simultaneously performed can be suppressed, and a wide range of supercharging pressure control can be performed while suppressing interference between the two turbochargers.
- the present invention can be used to control a vehicle equipped with an internal combustion engine having a plurality of superchargers.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
Description
3 吸気通路
4、5 ターボ過給機
4a、5a コンプレッサ
4b、5b タービン
4c、5c 可変ノズル
6 吸気切替弁
8 内燃機関
8a 気筒
9 過給圧センサ
10 排気通路
11 EGR通路
14 EGR弁
15 排気切替弁
16 排気バイパス弁
50 ECU
まず、本実施形態に係る内燃機関の過給機制御装置が適用されたシステムの全体構成について説明する。
次に、本発明の第1実施形態について説明する。
第1実施例では、第1のターボ過給機4のみを可変ターボ過給機として構成し、第2のターボ過給機5は可変ノズルを有しないターボ過給機とする。この場合、1個ターボモードにおいては、ECU50は、第1のターボ過給機4の実過給圧が、目標過給圧と一致するように可変ノズル4cの開度を制御する。なお、目標過給圧は、運転状態等、例えばエンジン回転数及び要求トルクに基づいて決定される。この制御を、「過給圧制御」又は「過給圧フィードバック(F/B)制御」と呼ぶ。
第2実施例は、2つのターボ過給機がともに可変ターボ過給機である場合の例である。1個ターボモードでは第1実施例と同様に過給圧制御を実行する。一方、2個ターボモードでは、2つのターボ過給機のうちの一方で過給圧制御を実行し、他方で空気量比制御を実行する。なお、過給圧制御及び空気量比制御の内容は第1実施例と同様である。
第3実施例は、車両が加速状態から減速状態に移行するときのサージ発生を防止するものである。図9は減速時にサージが発生する様子を説明する図である。グラフ71はサージ限界特性を示し、グラフ81は回転限界特性を示す。
次に、本発明の第2実施形態について説明する。第2実施形態では、2つのターボ過給機をともに可変ターボ過給機として構成する。そして、2個ターボモードでは2つのターボ過給機でともに過給圧制御を実行する。
Claims (6)
- 吸気通路及び排気通路に並列に配置された第1及び第2の過給機と、
前記第1の過給機と前記第2の過給機の空気量比が所定範囲内となるように、前記第1及び第2の過給機の空気量を制御する空気量比制御を実行する制御手段と、を備えることを特徴とする内燃機関の過給機制御装置。 - 前記第1及び前記第2の過給機の少なくとも一方は可変過給機構を備え、
前記制御手段は、前記第1及び第2の過給機の目標空気量比を決定し、前記第1及び第2の過給機の実際の空気量比が前記目標空気量比となるように前記可変過給機構を制御することを特徴とする請求の範囲第1項に記載の内燃機関の過給機制御装置。 - 前記第1及び前記第2の過給機の空気量を検出する空気量検出手段を備え、
前記制御手段は、前記空気量検出手段が検出した空気量に基づいて、前記実際の空気量比を決定することを特徴とする請求の範囲第2項に記載の内燃機関の過給機制御装置。 - 前記第2の過給機は前記第1の過給機より大容量であり、
前記制御手段は、前記第1及び第2の過給機の過給圧がそれぞれ目標過給圧となるように空気量をフィードバック制御する過給圧制御を実行し、
前記制御手段は、前記過給圧制御を実行するときには、前記第2の過給機のフィードバック制御量を前記第1の過給機のフィードバック制御量よりも小さくすることを特徴とする請求の範囲第1項に記載の内燃機関の過給機制御装置。 - 前記第1及び前記第2の過給機は可変過給機構を備え、
前記制御手段は、前記第1及び第2の過給機のうちの一方において前記空気量比制御を実行し、前記第1及び第2の過給機のうちの他方において、過給圧が目標過給圧となるように空気量をフィードバック制御する過給圧制御を行うことを特徴とする請求の範囲第1項に記載の内燃機関の過給機制御装置。 - 前記制御手段は、前記内燃機関の減速時に前記空気量比制御を実行することを特徴とする請求の範囲第1項に記載の内燃機関の過給機制御装置。
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CN200880106443A CN101802362A (zh) | 2008-04-25 | 2008-04-25 | 内燃机的增压器控制装置 |
PCT/JP2008/058134 WO2009130792A1 (ja) | 2008-04-25 | 2008-04-25 | 内燃機関の過給機制御装置 |
US12/676,081 US20110036332A1 (en) | 2008-04-25 | 2008-04-25 | Supercharger control device for internal combustion engine |
EP08752168A EP2267284A4 (en) | 2008-04-25 | 2008-04-25 | CHARGER CONTROL FOR INTERNAL COMBUSTION ENGINE |
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PCT/JP2008/058134 WO2009130792A1 (ja) | 2008-04-25 | 2008-04-25 | 内燃機関の過給機制御装置 |
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JP2011256743A (ja) * | 2010-06-07 | 2011-12-22 | Toyota Motor Corp | 過給器の制御装置 |
US20120317979A1 (en) * | 2010-12-17 | 2012-12-20 | Audi Ag | Arrangement of two independently operated turbochargers for a combustion engine, and method of operating the two turbochargers |
US20130111901A1 (en) * | 2011-11-07 | 2013-05-09 | Ford Global Technologies, Llc | Pulsation absorption system for an engine |
CN107476877A (zh) * | 2016-06-07 | 2017-12-15 | 本田技研工业株式会社 | 内燃机的增压系统 |
WO2020022212A1 (ja) * | 2018-07-27 | 2020-01-30 | 株式会社豊田自動織機 | 過給システム |
JP2020197166A (ja) * | 2019-06-03 | 2020-12-10 | 株式会社豊田自動織機 | 過給システム |
WO2020246105A1 (ja) * | 2019-06-03 | 2020-12-10 | 株式会社豊田自動織機 | 過給システム |
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WO2012176490A1 (ja) * | 2011-06-22 | 2012-12-27 | 日産自動車株式会社 | 過給機付内燃機関の吸気装置 |
EP2826981A4 (en) * | 2012-03-14 | 2017-08-09 | Nissan Motor Co., Ltd | Diesel engine control device and control method |
US9133757B2 (en) * | 2012-10-10 | 2015-09-15 | Ford Global Technologies, Llc | Engine control system and method |
CN105247194B (zh) * | 2013-05-24 | 2018-10-09 | 丰田自动车株式会社 | 内燃机的控制装置 |
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JP2011256743A (ja) * | 2010-06-07 | 2011-12-22 | Toyota Motor Corp | 過給器の制御装置 |
US20120317979A1 (en) * | 2010-12-17 | 2012-12-20 | Audi Ag | Arrangement of two independently operated turbochargers for a combustion engine, and method of operating the two turbochargers |
US20130111901A1 (en) * | 2011-11-07 | 2013-05-09 | Ford Global Technologies, Llc | Pulsation absorption system for an engine |
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CN107476877B (zh) * | 2016-06-07 | 2020-08-18 | 本田技研工业株式会社 | 内燃机的增压系统 |
WO2020022212A1 (ja) * | 2018-07-27 | 2020-01-30 | 株式会社豊田自動織機 | 過給システム |
JP2020197166A (ja) * | 2019-06-03 | 2020-12-10 | 株式会社豊田自動織機 | 過給システム |
WO2020246105A1 (ja) * | 2019-06-03 | 2020-12-10 | 株式会社豊田自動織機 | 過給システム |
JP2020197167A (ja) * | 2019-06-03 | 2020-12-10 | 株式会社豊田自動織機 | 過給システム |
JP7099406B2 (ja) | 2019-06-03 | 2022-07-12 | 株式会社豊田自動織機 | 過給システム |
JP7159980B2 (ja) | 2019-06-03 | 2022-10-25 | 株式会社豊田自動織機 | 過給システム |
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EP2267284A4 (en) | 2012-01-11 |
EP2267284A1 (en) | 2010-12-29 |
US20110036332A1 (en) | 2011-02-17 |
CN101802362A (zh) | 2010-08-11 |
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