WO2014196572A1 - 内燃機関の制御装置 - Google Patents
内燃機関の制御装置 Download PDFInfo
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- WO2014196572A1 WO2014196572A1 PCT/JP2014/064863 JP2014064863W WO2014196572A1 WO 2014196572 A1 WO2014196572 A1 WO 2014196572A1 JP 2014064863 W JP2014064863 W JP 2014064863W WO 2014196572 A1 WO2014196572 A1 WO 2014196572A1
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- engine
- internal combustion
- combustion engine
- crank angle
- cylinder
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W20/00—Control systems specially adapted for hybrid vehicles
- B60W20/10—Controlling the power contribution of each of the prime movers to meet required power demand
- B60W20/15—Control strategies specially adapted for achieving a particular effect
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/44—Series-parallel type
- B60K6/445—Differential gearing distribution type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/24—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the combustion engines
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60L—PROPULSION OF ELECTRICALLY-PROPELLED VEHICLES; SUPPLYING ELECTRIC POWER FOR AUXILIARY EQUIPMENT OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRODYNAMIC BRAKE SYSTEMS FOR VEHICLES IN GENERAL; MAGNETIC SUSPENSION OR LEVITATION FOR VEHICLES; MONITORING OPERATING VARIABLES OF ELECTRICALLY-PROPELLED VEHICLES; ELECTRIC SAFETY DEVICES FOR ELECTRICALLY-PROPELLED VEHICLES
- B60L50/00—Electric propulsion with power supplied within the vehicle
- B60L50/10—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines
- B60L50/16—Electric propulsion with power supplied within the vehicle using propulsion power supplied by engine-driven generators, e.g. generators driven by combustion engines with provision for separate direct mechanical propulsion
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/08—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of electric propulsion units, e.g. motors or generators
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W20/00—Control systems specially adapted for hybrid vehicles
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W20/00—Control systems specially adapted for hybrid vehicles
- B60W20/40—Controlling the engagement or disengagement of prime movers, e.g. for transition between prime movers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
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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
- F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
- F02D29/02—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto peculiar to engines driving vehicles; peculiar to engines driving variable pitch propellers
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2510/00—Input parameters relating to a particular sub-units
- B60W2510/06—Combustion engines, Gas turbines
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2510/00—Input parameters relating to a particular sub-units
- B60W2510/06—Combustion engines, Gas turbines
- B60W2510/0685—Engine crank angle
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/06—Combustion engines, Gas turbines
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W2710/00—Output or target parameters relating to a particular sub-units
- B60W2710/08—Electric propulsion units
- B60W2710/083—Torque
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
- B60Y2300/00—Purposes or special features of road vehicle drive control systems
- B60Y2300/45—Engine shutdown at standstill
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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
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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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
- Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
- Y02T10/84—Data processing systems or methods, management, administration
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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
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S903/00—Hybrid electric vehicles, HEVS
- Y10S903/902—Prime movers comprising electrical and internal combustion motors
- Y10S903/903—Prime movers comprising electrical and internal combustion motors having energy storing means, e.g. battery, capacitor
Definitions
- the present invention relates to a control device applied to a three-cylinder internal combustion engine in which an electric motor is connected to a crankshaft so that power can be transmitted.
- Patent Document 1 A control device that is applied to an internal combustion engine mounted on a hybrid vehicle and that stops the internal combustion engine at a target stop crank angle by reducing the number of revolutions of the internal combustion engine with a motor / generator when the internal combustion engine is stopped is known ( Patent Document 1).
- Patent Documents 2 to 4 exist as prior art documents related to the present invention.
- the vicinity of the top dead center of the compression stroke is set as the target stop crank angle.
- control is not performed so that a specific cylinder set in advance when the internal combustion engine is stopped becomes the compression stroke. Therefore, there is a possibility that the cylinder that becomes the compression stroke when the internal combustion engine is stopped is different every time.
- Patent Documents 3 and 4 in a three-cylinder internal combustion engine, a plowing motion occurs, and this plowing motion causes vibration at the time of starting. The phase of the plowing motion changes according to the cylinder that first applies torque to the crankshaft at the start. Therefore, in the apparatus of Patent Document 1, there is a possibility that a large vibration is generated at the time of starting.
- an object of the present invention is to provide a control device for an internal combustion engine that can reduce vibration at the time of starting.
- the control device of the present invention is a control device applied to a three-cylinder internal combustion engine that is mounted on a vehicle and has a motor connected to a crankshaft so that power can be transmitted, and a preset specific cylinder has a compression stroke or an expansion stroke.
- the internal combustion engine is stopped so that the specific cylinder is in the compression stroke or the expansion stroke. Therefore, at the next start, the internal combustion engine in a state where the specific cylinder is in the compression stroke or the expansion stroke is cranked. Will do.
- the vibration component that is expected to be generated by the rotation of the crankshaft and the vibration component that is generated due to the plowing motion weaken each other, so that vibration at the time of starting can be reduced.
- control means is configured to control the internal combustion engine when a predetermined engine stop condition is satisfied and the crank angle of the internal combustion engine is within a predetermined determination crank angle range.
- Rotation speed reduction control for stopping combustion and then outputting torque from the electric motor to reduce the rotation speed of the crankshaft is executed, and the crank angle of the internal combustion engine is the determination crank angle range as the determination crank angle range.
- a crank angle range in which the internal combustion engine stops in a state where the specific cylinder is in a compression stroke or an expansion stroke may be set by starting the rotation speed reduction control when the engine is within the range. By executing the rotation speed reduction control in this manner, the internal combustion engine can be stopped while the specific cylinder is in the compression stroke or the expansion stroke.
- the vehicle is provided with an operation switch for the driver to instruct the vehicle to run with priority on fuel consumption, and the control means stops the engine when the operation switch is off.
- the condition is satisfied and the crank angle of the internal combustion engine is within the determination crank angle range
- the combustion of the internal combustion engine is stopped, and then the rotation speed reduction control is executed, and the operation switch is turned on. May stop the combustion of the internal combustion engine when the engine stop condition is satisfied, and then execute the rotation speed reduction control.
- the operation switch is on, the combustion of the internal combustion engine is stopped even if the crank angle is not within the determination crank angle range when the engine stop condition is satisfied. Therefore, fuel consumption can be improved.
- the control means stops combustion of the internal combustion engine when a predetermined engine stop condition is satisfied, and then outputs torque from the electric motor to reduce the rotational speed of the crankshaft.
- the rotational speed control to be reduced is executed, and the magnitude of the torque output from the electric motor in the rotational speed control is set so that the specific cylinder is in the compression stroke or expansion stroke state when the internal combustion engine is stopped. May be.
- FIG. 1 schematically shows a hybrid vehicle 1.
- vehicle 1 includes an internal combustion engine (hereinafter may be referred to as an engine) 11, a first motor / generator (hereinafter also referred to as a first MG) 12, and a second motor / generator (hereinafter referred to as a first motor / generator). 2MG) .13).
- the engine 11 includes three cylinders 11a arranged in a row. That is, the engine 11 is configured as an in-line three-cylinder four-cycle internal combustion engine.
- the cylinders 11a are assigned cylinder numbers # 1 to # 3 from one end to the other end in the arrangement direction to distinguish them from each other.
- the explosion interval of each cylinder 11a is shifted by 240 ° CA (meaning the crank angle), thereby realizing an equidistant explosion every 240 ° CA.
- the explosion order in the engine 11 is the order of # 1, # 2, and # 3.
- the first MG 12 and the second MG 13 are well-known motor generators that function as an electric motor and a generator.
- the first MG 12 includes a rotor 12b that rotates integrally with the output shaft 12a, and a stator 12c that is coaxially disposed on the outer periphery of the rotor 12b and fixed to a case (not shown).
- the second MG 13 includes a rotor 13b that rotates integrally with the output shaft 13a, and a stator 13c that is coaxially disposed on the outer periphery of the rotor 13b and fixed to the case.
- the crankshaft 40 of the engine 11 and the output shaft 12a of the first MG 12 are connected to the power split mechanism 14.
- An output unit 15 for transmitting power to the drive wheels 2 of the vehicle 1 is also connected to the power split mechanism 14.
- the output unit 15 includes a first drive gear 16, a counter gear 18 that meshes with the first drive gear 16 and is fixed to the counter shaft 17, and an output gear 19 that is fixed to the counter shaft 17.
- the output gear 19 meshes with a ring gear 20 a provided in the case of the differential mechanism 20.
- the differential mechanism 20 is a well-known mechanism that distributes the power transmitted to the ring gear 20 a to the left and right drive wheels 2. In FIG. 1, only one of the left and right drive wheels 2 is shown.
- the power split mechanism 14 includes a planetary gear mechanism 21 as a differential mechanism.
- the planetary gear mechanism 21 is a single pinion type planetary gear mechanism, and includes a sun gear Su, a ring gear Ri, a pinion gear Pi, and a carrier Ca.
- the sun gear Su is an external gear.
- the ring gear Ri is an internal gear disposed coaxially with the sun gear Su.
- the pinion gear Pi meshes with each of the sun gear Su and the ring gear Ri.
- the carrier Ca holds the pinion gear Pi so as to be capable of rotating and revolving around the sun gear Su.
- the sun gear Su is connected to the output shaft 12a of the first MG 12.
- the carrier Ca is connected to the crankshaft 40 of the engine 11.
- the ring gear Ri is connected to the first drive gear 16.
- a second drive gear 22 is provided on the output shaft 13a of the second MG 13.
- the second drive gear 22 meshes with the counter gear 18.
- the first MG 12 and the second MG 13 are electrically connected to the battery 23 via an inverter and a boost converter (not shown).
- the operations of the engine 11, the first MG 12, and the second MG 13 are controlled by the vehicle control device 30.
- the vehicle control device 30 is configured as a computer unit including a microprocessor and peripheral devices such as RAM and ROM necessary for its operation.
- the vehicle control device 30 holds various control programs for causing the vehicle 1 to travel appropriately.
- the vehicle control device 30 executes control of the control target such as the engine 11 and the MGs 12 and 13 by executing these programs.
- Various sensors for acquiring information related to the vehicle 1 are connected to the vehicle control device 30. For example, a vehicle speed sensor 31 and a crank angle sensor 32 are connected to the vehicle control device 30.
- the vehicle speed sensor 31 outputs a signal corresponding to the speed (vehicle speed) of the vehicle 1.
- the crank angle sensor 32 outputs a signal corresponding to the crank angle of the engine 11.
- an ECO switch 33 is connected to the vehicle control device 30.
- the ECO switch 33 is a switch used by the driver to instruct the vehicle control device 30 to perform fuel consumption travel that prioritizes suppression of fuel consumption.
- An ON signal is output from the ECO switch 33 when the ECO switch 33 is ON, and an OFF signal is output when it is OFF.
- various sensors, switches, and the like are connected to the vehicle control device 30, but these are not shown.
- the vehicle control device 30 stops the engine 11 by stopping the fuel supply to each cylinder 11 a when a predetermined engine stop condition is satisfied during the operation of the engine 11. Further, when a predetermined engine start condition is satisfied when engine 11 is stopped, vehicle control device 30 cranks engine 11 at first MG 12 and starts it. In the vehicle 1, the vehicle 1 is driven only by the second MG 13 when the vehicle speed is less than a predetermined determination speed set in advance. On the other hand, when the vehicle speed is equal to or higher than the determination speed, the vehicle 1 is driven by both the engine 11 and the second MG 13. Therefore, it is determined that the engine stop condition is satisfied, for example, when the vehicle speed is less than the determination speed. Further, it is determined that the engine start condition is satisfied, for example, when the vehicle speed is equal to or higher than the determination speed.
- the vehicle control device 30 reduces the rotational speed of the engine 11 with the first MG 12 when stopping the engine 11. At this time, the vehicle control device 30 adjusts the output torque of the first MG 12 so that the engine 11 stops in a state where the preset specific cylinder is in the compression stroke. By stopping the engine 11 in this manner, the cylinder that is initially in the compression stroke when starting can be made the same every time.
- a cylinder that can suppress vibration during cranking of the engine 11 is set as the specific cylinder.
- FIG. 2 schematically shows the crankshaft 40, the piston 41, and the connecting rod 42 of the engine 11.
- the piston 41 and the connecting rod 42 are provided for each cylinder 11a.
- Piston 41 is inserted in each cylinder 11a so that reciprocation is possible.
- the connecting rod 42 connects the piston 41 and the crankshaft 40.
- the direction of the rotation axis of the crankshaft 40 is defined as the Y axis.
- the direction in which the piston 41 reciprocates is defined as the Z direction.
- a direction orthogonal to each of the Y axis and the Z axis is defined as an X axis.
- the vibration around the X axis is pitch vibration.
- the vibration around the Y axis is roll vibration
- the vibration around the Z axis is yaw vibration.
- the crankshaft 40 includes four journal portions 40a arranged in the Y-axis direction, three crankpins 40b positioned between the journal portions 40a, and a crank that connects the journal portions 40a and the crankpins 40b. Arm 40c.
- the crankshaft 40 is provided with a counterweight 40d.
- the counterweight 40d extends from the crank arm 40c to the opposite side of the crankpin 40b. In FIG. 2, the counterweight 40d is not shown. Also in FIG. 5, the illustration of the counterweight 40d of the cylinder 11a of # 2 is omitted.
- These components of the crankshaft 40 are integrally formed by casting or the like.
- the three crank pins 40b are provided with a 120 degree shift around the Y axis.
- the connecting rod 42 connects the crank pin 40 b and the piston 41.
- the vibration generated in the vehicle 1 when the engine 11 is cranked includes a plurality of vibration components.
- the plurality of vibration components include a vibration component generated by rotation of the crankshaft 40 (hereinafter, also referred to as a crankshaft vibration component) and a vibration component generated by a plowing motion of the engine 11 (hereinafter referred to as a plowing). May be referred to as a motion vibration component).
- each crank pin 40 b is provided at a position separated from the rotation axis of the crank shaft 40 by the length of the crank arm 40 c.
- the crankshaft 40 is provided with a counterweight 40d.
- the crank arm 40c and the counterweight 40d are arranged at a distance S apart from each other in the Y-axis direction. Therefore, when the crankshaft 40 is driven to rotate, the crankpin 40b and the counterweight 40d rotate, and vibrations are generated.
- the crankshaft vibration component is this vibration.
- torque is input from the first MG 12 to the crankshaft 40.
- crankshaft vibration component is assumed when the torque applied to the crankshaft 40 during cranking of the engine 11 is applied to the crankshaft 40 with the piston 41 and the connecting rod 42 of each cylinder 11a removed. This vibration is expected to occur in the engine 11.
- the top diagram of FIG. 8 shows an example of the time change of the crankshaft vibration component.
- each crank pin 40b is provided at a position separated from the rotational axis of the crankshaft 40 by the length of the crank arm 40c. Therefore, when the crankshaft 40 is driven to rotate, a moment based on the inertial force and the length of the crank arm 40c when the piston 41 of each cylinder 11a reciprocates is generated in the crankshaft 40. Further, as shown in FIG. 2, the crank pins 40b are provided by being shifted by 120 degrees. Therefore, as shown in an example in FIG. 4, the force in the Z-axis direction generated on the crankshaft 40 becomes unbalanced. Therefore, as shown in FIG. 3, pitch vibration is generated in the engine 11.
- a counterweight 40d is provided in order to reduce the moment generated by such a crankpin 40b.
- the weight of the counterweight 40d is set to a weight obtained by adding half the weight of the piston 41 and half the weight of the connecting rod 42 to the weight of the crank pin 40b. . That is, in the engine 11, a so-called overbalance rate is set to 50%.
- a so-called overbalance rate is set to 50%.
- the force Px in the X-axis direction is a force that vibrates the engine 11 in the X-axis direction.
- the force Px in the X-axis direction of the counterweight 40d of the # 1 cylinder 11a and the force Px in the X-axis direction of the counterweight 40d of the # 3 cylinder 11a act in opposite directions.
- a couple is generated in the X-axis direction
- yaw vibration is generated in the engine 11.
- FIG. 7 shows the relationship between the couple in the X-axis direction generated by the engine 11 and the crank angle.
- the couple in the X-axis direction changes at a 360 ° CA cycle.
- the compression stroke of each cylinder 11a is shifted by 240 ° CA. Therefore, the phase of the couple in the X-axis direction changes depending on which of the three cylinders 11a is the cylinder that is initially in the compression stroke when the engine 11 is started.
- the middle diagram of FIG. 8 shows an example of the temporal change of the plow motion vibration component.
- the solid line L1 in this figure shows the temporal change of the pricking vibration component when the # 1 cylinder 11a is initially in the compression stroke at the start.
- the solid line L2 in this figure shows the temporal change of the pricking vibration component when the # 2 cylinder 11a is first in the compression stroke at the start.
- the solid line L3 in this figure shows the change over time of the pricking vibration component when the # 3 cylinder 11a is first in the compression stroke at the time of starting.
- the bottom diagram of FIG. 8 shows the vibration obtained by synthesizing the crankshaft vibration component and the pruning vibration component.
- the solid line L4 in this figure indicates the combined vibration of the crankshaft vibration component and the pricking vibration component when the # 1 cylinder 11a is initially in the compression stroke at the start.
- the solid line L5 in this figure indicates the vibration obtained by combining the crankshaft vibration component and the pruning vibration component when the # 2 cylinder 11a is initially in the compression stroke at the start.
- the solid line L6 in this figure shows the vibration obtained by synthesizing the crankshaft vibration component and the pruning vibration component when the # 3 cylinder 11a is initially in the compression stroke at the start.
- the phase of the sawtooth vibration component when the # 2 cylinder 11a is first in the compression stroke at the start is almost opposite to the phase of the crankshaft vibration component. Therefore, as shown in the bottom diagram of FIG. 8, the vibration obtained by synthesizing the pruning vibration component and the crankshaft vibration component when the # 2 cylinder 11a is first in the compression stroke at the start is the most. Get smaller. Therefore, in the engine 11, the # 2 cylinder 11a is set as a specific cylinder. As shown in this figure, in the engine 11, the phase of the pricking vibration component when the # 3 cylinder 11a is first in the compression stroke at the time of starting is substantially the same as the phase of the crankshaft vibration component. Therefore, in this case, the vibration of the vehicle 1 increases.
- the vehicle control device 30 reduces the rotational speed of the engine 11 with the first MG 12. At this time, the vehicle control device 30 changes the control of the first MG 12 according to the rotational speed of the engine 11.
- rotation speed reduction control, alignment control, torque release control, and reverse rotation prevention control are provided. These controls are executed in the order of rotational speed reduction control, alignment control, torque release control, and reverse rotation prevention control.
- Rotational speed reduction control is executed when the crank angle falls within a predetermined judgment crank angle range set in advance.
- the predetermined determination crank angle range is set to a crank angle range in which the engine 11 stops when the # 2 cylinder 11a is in the compression stroke when the above-described controls are executed from this crank angle range. Note that such a crank angle range may be obtained in advance by experiments, numerical calculations, etc., and stored in the ROM of the vehicle control device 30.
- the rotation speed reduction control is executed until the rotation speed of the engine 11 becomes equal to or lower than a predetermined first determination rotation speed N1.
- the first determination rotation speed N1 is a rotation speed at which the alignment control is started. When the rotational speed of the engine 11 becomes equal to or lower than the first determination rotational speed N1, the alignment control is started.
- torque is output from the first MG 12 so that the crankshaft 40 has a predetermined target crank angle set in advance when the engine 11 is stopped.
- the target crank angle is set such that the # 2 cylinder 11a is near the top dead center of the compression stroke.
- Alignment control is executed until the rotational speed of the engine 11 is equal to or lower than a predetermined second determination rotational speed N2.
- the second determination rotational speed N2 is a rotational speed at which torque release control is started.
- torque release control is started. In this torque release control, the torque of the first MG 12 is reduced to zero.
- the torque release control is executed until the rotational speed of the engine 11 becomes equal to or lower than the third determination rotational speed N3.
- the third determination rotational speed N3 is a rotational speed at which reverse rotation prevention control is started.
- the magnitude relationship among the first determination rotation speed N1, the second determination rotation speed N2, and the third determination rotation speed N3 is N3 ⁇ N2 ⁇ N1 ⁇ idle rotation speed.
- reverse rotation prevention control When the rotational speed of the engine 11 is equal to or lower than the third determination rotational speed N3, reverse rotation prevention control is executed.
- torque is applied from the first MG 12 so that the crankshaft 40 does not rotate in the reverse rotation direction opposite to the normal rotation direction that rotates during operation of the engine 11 and the crankshaft 40 stops at the target crank angle. Output.
- This reverse rotation prevention control is executed until the engine 11 is stopped. When the engine 11 stops, the first MG 12 is also stopped.
- FIG. 9 and 10 show an engine stop control routine executed by the vehicle control device 30 to control the first MG 11 as described above.
- FIG. 10 is a control routine following FIG. This control routine is repeatedly executed at a predetermined cycle while the engine 11 is operating. In addition, this control routine is executed in parallel with other control routines executed by the vehicle control device 30. By executing this control routine, the vehicle control device 30 functions as the control means of the present invention.
- the vehicle control device 30 first acquires the state of the vehicle 1 in step S11. As the state of the vehicle 1, the vehicle speed and the crank angle are acquired. Further, in this process, based on the output signal of the crank angle sensor 32, the rotational speed of the engine 11 and the cylinder number of the cylinder 11a currently in the compression stroke are also acquired. If none of the three cylinders 11a is in the compression stroke, the cylinder number of the cylinder 11a that was in the compression stroke immediately before is acquired. In the next step S12, the vehicle control device 30 determines whether or not the engine stop condition described above is satisfied. If it is determined that the engine stop condition is not satisfied, the current control routine is terminated.
- step S13 determines whether or not the crank angle is within the predetermined determination crank angle range described above. When it is determined that the crank angle is outside the determination crank angle range, this process is repeatedly executed until the crank angle falls within the determination crank angle range.
- step S14 the vehicle control device 30 executes the combustion stop control. In this combustion stop control, the fuel supply to the engine 11 is stopped, and the combustion of the engine 11 is stopped.
- step S15 the vehicle control device 30 sets the rotational speed reduction torque based on the rotational speed of the engine 11 when the combustion is stopped.
- This rotational speed reduction torque is a torque output from the first MG 12 in order to rapidly reduce the rotational speed of the engine 11.
- This relationship may be obtained in advance by experiments, numerical calculations, etc. and stored in the ROM of the vehicle control device 30 as a map. Then, the rotational speed reduction torque may be set based on this map and the rotational speed of the engine 11.
- the vehicle control device 30 executes the rotational speed reduction control.
- this rotational speed reduction control the set rotational speed reduction torque is output from the first MG 12 to reduce the rotational speed of the engine 11.
- the vehicle control device 30 determines whether or not the rotational speed of the engine 11 has become equal to or lower than the first determination rotational speed N1. When it determines with the rotation speed of the engine 11 being higher than the 1st determination rotation speed N1, it returns to step S16, and the vehicle control apparatus 30 performs step S16 and S17 until the rotation speed of the engine 11 becomes below the 1st determination rotation speed N1. Run repeatedly.
- step S18 when it determines with the rotation speed of the engine 11 having become below 1st determination rotation speed N1, it progresses to step S18, and the vehicle control apparatus 30 determined with the rotation speed of the engine 11 having become below 1st determination rotation speed N1.
- the alignment torque is set based on the crank angle at the time (hereinafter sometimes referred to as the first crank angle).
- This alignment torque is a torque that is output from the first MG 12 so that the crankshaft 40 has the above-described target crank angle when the engine 11 becomes equal to or lower than the predetermined rotation speed. It is assumed that the rotation speed reduction torque is continuously output from the first MG 12 until the rotation speed of the engine 11 changes from the first determination rotation speed N1 to the second determination rotation speed N2.
- the first crank angle at which the crank angle when the engine 11 is stopped becomes the target crank angle is determined according to the target crank angle and the specifications of the engine 11.
- a first crank angle may be referred to as a first reference crank angle.
- the relationship between the difference between the first crank angle and the first reference crank angle and the alignment torque may be obtained in advance by experiment, numerical calculation, or the like and stored in the ROM of the vehicle control device 30 as a map. Then, the alignment torque may be set based on this map and the first crank angle.
- the vehicle control device 30 executes alignment control.
- this alignment control a torque obtained by adding the rotation speed reduction torque and the alignment torque is output from the first MG 12.
- the vehicle control device 30 determines whether or not the rotational speed of the engine 11 has become equal to or lower than the second determination rotational speed N2. When it determines with the rotation speed of the engine 11 being higher than the 2nd determination rotation speed N2, it returns to step S19, and the vehicle control apparatus 30 performs step S19 and S20 until the rotation speed of the engine 11 becomes below the 2nd determination rotation speed N2. Run repeatedly.
- step S21 when it determines with the rotation speed of the engine 11 having become below 2nd determination rotation speed N2, it progresses to step S21 and the vehicle control apparatus 30 performs torque release control.
- the first MG 12 is controlled so that the torque of the first MG 12 decreases at a preset torque release rate.
- a torque release rate suitably so that the torque of 1st MG12 may not fall rapidly.
- the vehicle control device 30 determines whether or not the rotational speed of the engine 11 has become equal to or lower than the third determination rotational speed N3.
- step S21 When it determines with the rotation speed of the engine 11 being higher than the 3rd determination rotation speed N3, it returns to step S21, and the vehicle control apparatus 30 performs step S21 and S22 until the rotation speed of the engine 11 becomes below the 3rd determination rotation speed N3. Run repeatedly.
- step S23 the vehicle control device 30 determines the crank angle when the torque of the first MG 12 becomes zero (hereinafter, referred to as the second The reverse rotation prevention torque is set based on the crank angle.
- This reverse rotation prevention torque is a torque output from the first MG 12 in order to stop the crankshaft 40 at the target crank angle while preventing the crankshaft 40 from rotating in the reverse direction. It is assumed that the output torque of the first MG 12 is zero until the rotation speed of the engine 11 becomes zero from the third determination rotation speed N3.
- the second crank angle at which the crank angle when the engine 11 is stopped becomes the target crank angle is determined according to the target crank angle and the specifications of the engine 11.
- a second crank angle may be referred to as a second reference crank angle.
- the reverse rotation prevention torque is set to a larger value as the difference between the second crank angle and the second reference crank angle is larger.
- the relationship between the difference between the second crank angle and the second reference crank angle and the reverse rotation prevention torque may be obtained in advance by experiment, numerical calculation, or the like and stored in the ROM of the vehicle control device 30 as a map. Then, the reverse rotation prevention torque may be set based on this map and the second crank angle.
- step S24 the vehicle control device 30 executes reverse rotation prevention control.
- this reverse rotation prevention control the set reverse rotation prevention torque is output from the first MG 12.
- step S25 the vehicle control device 30 determines whether or not the engine 11 has stopped, that is, whether or not the rotational speed of the engine 11 has become zero. When it determines with the engine 11 not having stopped, it returns to step S24, and the vehicle control apparatus 30 repeatedly performs step S24 and S25 until the engine 11 stops.
- step S26 when it determines with the engine 11 having stopped, it progresses to step S26 and the vehicle control apparatus 30 performs 1st MG stop control.
- the output torque of the first MG 12 is set to zero and the first MG 12 is stopped. Thereafter, the current control routine is terminated.
- FIG. 11 shows the rotation speed of the engine 11, the cylinder 11a that is currently in the compression stroke, or the cylinder 11a that has been in the compression stroke immediately before when the engine 11 is stopped by executing this engine stop control routine.
- An example of the time change of the number, the torque of the first MG 12, and the crank angle is shown.
- the torque output from the first MG 12 when the first MG 12 is rotated in the forward direction is shown as a positive torque
- the torque output from the first MG 12 when the first MG 12 is rotated in the reverse direction Is shown as a negative torque.
- the engine stop condition is satisfied at time t1, and the engine speed reduction control is executed.
- the rotational speed reduction torque is output from the first MG 12, and the rotational speed of the engine 11 is reduced.
- the alignment control is executed.
- the # 2 cylinder 11a when the engine 11 is stopped, the # 2 cylinder 11a is in the compression stroke, so every time the engine is started, the # 2 cylinder 11a is in the compression stroke first. .
- the pruning motion vibration component when the # 2 cylinder 11a is in the compression stroke at the time of start-up, the pruning motion vibration component is almost in reverse phase with the crankshaft vibration component. In this case, since these vibration components weaken each other, the vibration of the vehicle 1 at the time of starting can be reduced.
- the # 2 cylinder 11a is set as the specific cylinder, but the specific cylinder is not limited to this cylinder.
- the cylinder 11a in which the plowing motion vibration component at the time of starting is substantially in phase with the crankshaft vibration component is set as the specific cylinder.
- Such a cylinder 11a changes according to the specifications of the engine 11, the specifications of the power split mechanism 14, and the like. Therefore, such a cylinder 11a may be specified by experiment, numerical calculation, or the like, and the cylinder 11a may be set as a specific cylinder.
- the specific cylinder is in the compression stroke state when the engine 11 is stopped.
- the state of the specific cylinder when the engine 11 is stopped is not limited to this state.
- an internal combustion engine in which fuel is sealed in a cylinder 11a that is in an expansion stroke when the engine 11 is stopped, and the engine 11 is started by igniting the fuel at the next start.
- the engine 11 may be stopped while the specific cylinder is in an expansion stroke.
- the first MG 12 corresponds to the electric motor of the present invention.
- the ECO switch 33 corresponds to the operation switch of the present invention.
- the rotational speed reduction control and the alignment control correspond to the rotational speed reduction control of the present invention.
- FIG. 1 is referred to for the vehicle 1. Therefore, parts common to the first embodiment are denoted by the same reference numerals and description thereof is omitted.
- FIG. 12 shows a part of an engine stop control routine executed by the vehicle control device 30 in this embodiment.
- FIG. 12 is used in place of the portion of FIG. 9 of the first embodiment. Therefore, even in the engine stop control routine of this form, the part after FIG. 12, that is, the part of FIG. 10, is the same as the first form.
- step S12 the process proceeds as in the first form until step S12. If it is determined in step S12 that the engine stop condition is satisfied, the process proceeds to step S14, and the process proceeds to step S17 in the same manner as in the first embodiment. If it is determined in step S17 that the rotation speed of the engine 11 has become equal to or less than the first determination rotation speed N1, the process proceeds to step S31, and the vehicle control device 30 acquires the current crank angle, that is, the first crank angle. In subsequent step S32, the vehicle control device 30 sets the alignment torque based on the first crank angle. In this embodiment, the alignment torque is set so that the # 2 cylinder 11a is in the compression stroke when the engine 11 is stopped.
- the crank angle movement amount is calculated from the difference between the first crank angle and a preset target crank angle.
- a preset target crank angle As described above, for example, when the engine 11 is stopped, the crank angle at which the # 2 cylinder 11a becomes near the top dead center of the compression stroke is set as the target crank angle. Therefore, the crank angle movement amount is an angle at which the crankshaft 40 rotates from the current time until the engine 11 stops.
- the alignment torque is calculated based on the crank angle movement amount.
- the relationship between the alignment torque and the crank angle movement amount may be obtained in advance by experiments, numerical calculations, etc., and stored in the ROM of the vehicle control device 30 as a map. Then, the alignment torque may be calculated based on this map.
- step S19 After setting the alignment torque, the process proceeds to step S19, and thereafter the process proceeds in the same manner as in the first embodiment.
- the alignment torque is set so that the # 2 cylinder 11a is in the compression stroke, and the alignment control is executed with this alignment torque. Therefore, when the engine 11 is stopped, the # 2 cylinder 11a can be in the compression stroke. As a result, the # 2 cylinder 11a is initially in the compression stroke at the time of start-up, so that the pulsating motion vibration component and the crankshaft vibration component can be substantially in opposite phases. Therefore, the vibration of the vehicle 1 at the time of starting can be reduced.
- FIG. 1 is referred to for the vehicle 1. Therefore, parts common to the first embodiment are denoted by the same reference numerals and description thereof is omitted.
- FIG. 13 shows a part of an engine stop control routine executed by the vehicle control device 30 in this embodiment.
- FIG. 13 is used in place of the portion of FIG. 9 of the first embodiment. Therefore, even in the engine stop control routine of this embodiment, the portion after FIG. 13, that is, the portion of FIG. 10 is the same as that of the first embodiment.
- step S12 the engine stop condition is satisfied
- step S41 the vehicle control device 30 determines whether or not the ECO switch 33 is off. If it is determined that the ECO switch 33 is off, the process proceeds to step S13, and thereafter the process proceeds in the same manner as in the first embodiment. On the other hand, if it is determined that the ECO switch 33 is on, the process proceeds to step S14, and thereafter the process proceeds in the same manner as in the first embodiment.
- step S13 is skipped when the ECO switch 33 is on. Therefore, the period from when the engine stop condition is satisfied to when the combustion stop control is executed can be shortened. Therefore, fuel consumption can be improved.
- step S13 is executed, so that the engine 11 is stopped while the # 2 cylinder 11a is in the compression stroke. Therefore, the vibration of the vehicle 1 at the time of starting can be reduced.
- the present invention can be implemented in various forms without being limited to the above-described forms.
- the internal combustion engine to which the present invention is applied is not limited to the internal combustion engine mounted on the hybrid vehicle.
- the present invention may be applied to an internal combustion engine of a vehicle in which only the internal combustion engine is mounted as a power source.
- an electric motor may be connected to the crankshaft of the internal combustion engine so that power can be transmitted. At this time, the electric motor may be directly connected to the crankshaft.
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Abstract
Description
以下、本発明の制御装置をハイブリッド車両に搭載された内燃機関に適用した一形態を説明する。図1は、ハイブリッド車両1を概略的に示している。車両1は、内燃機関(以下、エンジンと称することがある。)11と、第1モータ・ジェネレータ(以下、第1MGと略称することがある。)12と、第2モータ・ジェネレータ(以下、第2MGと略称することがある。)13とを備えている。エンジン11は、一列に並ぶ3つの気筒11aを備えている。すなわち、エンジン11は直列3気筒の4サイクル内燃機関として構成されている。この図に示したように各気筒11aにはそれらの並び方向一端から他端側に向かって#1~#3の気筒番号を付して互いに区別する。このエンジン11では、各気筒11aの爆発間隔が240°CA(クランク角を意味する。)ずつずらされることにより、240°CA毎の等間隔爆発が実現されている。なお、このエンジン11における爆発順序は、#1、#2、#3の順である。
次に図12を参照して本発明の第2の形態に係る制御装置について説明する。なお、この形態においても車両1については図1が参照される。そのため、第1の形態と共通の部分については同一の符号を付して説明を省略する。
図13を参照して本発明の第3の形態に係る制御装置について説明する。なお、この形態においても車両1については図1が参照される。そのため、第1の形態と共通の部分については同一の符号を付して説明を省略する。
Claims (4)
- 車両に搭載され、かつクランク軸に電動機が動力伝達可能に接続されている3気筒の内燃機関に適用される制御装置において、
予め設定した特定気筒が圧縮行程又は膨張行程の状態で前記内燃機関が停止するように前記内燃機関を停止させる際に前記電動機の出力トルクを制御する制御手段を備え、
前記特定気筒は、当該特定気筒が圧縮行程又は膨張行程の状態から前記内燃機関を始動した場合に前記内燃機関のすりこぎ運動に起因して発生する振動成分と、各気筒のピストン及びコンロッドが外された状態の前記クランク軸に対して前記内燃機関の始動時に前記クランク軸に加えられるトルクが付与されたと仮定した場合に前記車両に発生すると予想される振動成分と、が互いに弱め合う関係になる気筒である制御装置。 - 前記制御手段は、所定の機関停止条件が成立し、かつ前記内燃機関のクランク角が予め設定した所定の判定クランク角範囲内の場合に、前記内燃機関の燃焼を停止させ、その後前記電動機からトルクを出力して前記クランク軸の回転数を低下させる回転数低下制御を実行し、
前記判定クランク角範囲として、前記内燃機関のクランク角が前記判定クランク角範囲内にあるときに前記回転数低下制御を開始することにより前記特定気筒が圧縮行程又は膨張行程の状態で前記内燃機関が停止するクランク角範囲が設定されている請求項1の制御装置。 - 前記車両には、ドライバが前記車両に対して燃費を優先する走行を指示するための操作スイッチが設けられ、
前記制御手段は、
前記操作スイッチがオフの場合には、前記機関停止条件が成立し、かつ前記内燃機関のクランク角が前記判定クランク角範囲内の場合に、前記内燃機関の燃焼を停止させ、その後前記回転数低下制御を実行し、
前記操作スイッチがオンの場合には、前記機関停止条件が成立した場合に、前記内燃機関の燃焼を停止させ、その後前記回転数低下制御を実行する請求項2の制御装置。 - 前記制御手段は、所定の機関停止条件が成立した場合、前記内燃機関の燃焼を停止させ、その後前記電動機からトルクを出力して前記クランク軸の回転数を低下させる回転数制御を実行し、
前記回転数制御において前記電動機から出力されるトルクの大きさは、前記内燃機関が停止したときに前記特定気筒が圧縮行程又は膨張行程の状態になるように設定される請求項1の制御装置。
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CN201480032313.3A CN105283334B (zh) | 2013-06-07 | 2014-06-04 | 内燃机的控制装置 |
BR112015030648-9A BR112015030648B1 (pt) | 2013-06-07 | 2014-06-04 | Aparelho de controle para motor de combustão interna |
DE112014002707.3T DE112014002707T5 (de) | 2013-06-07 | 2014-06-04 | Steuerungsvorrichtung für Verbrennungsmotor |
US14/896,189 US9517762B2 (en) | 2013-06-07 | 2014-06-04 | Control apparatus for internal combustion engine |
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JP6620668B2 (ja) * | 2016-05-10 | 2019-12-18 | 株式会社デンソー | エンジン制御装置 |
JP2017203402A (ja) * | 2016-05-10 | 2017-11-16 | 株式会社デンソー | エンジン制御装置 |
JP7000879B2 (ja) * | 2018-01-30 | 2022-01-19 | 株式会社アイシン | 車両の制御装置 |
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JP6020218B2 (ja) * | 2013-02-05 | 2016-11-02 | マツダ株式会社 | 可変気筒エンジン |
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2013
- 2013-06-07 JP JP2013121022A patent/JP6105399B2/ja active Active
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2014
- 2014-06-04 CN CN201480032313.3A patent/CN105283334B/zh not_active Expired - Fee Related
- 2014-06-04 DE DE112014002707.3T patent/DE112014002707T5/de active Pending
- 2014-06-04 US US14/896,189 patent/US9517762B2/en active Active
- 2014-06-04 BR BR112015030648-9A patent/BR112015030648B1/pt active IP Right Grant
- 2014-06-04 WO PCT/JP2014/064863 patent/WO2014196572A1/ja active Application Filing
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JP2005016505A (ja) * | 2003-06-06 | 2005-01-20 | Aisin Aw Co Ltd | 車両駆動制御装置、車両駆動制御方法及びそのプログラム |
JP2006214332A (ja) * | 2005-02-03 | 2006-08-17 | Toyota Motor Corp | 内燃機関の制御装置及びその制御装置を備えた自動車 |
JP2007276594A (ja) * | 2006-04-05 | 2007-10-25 | Fuji Heavy Ind Ltd | 車両用制御装置 |
JP2008013041A (ja) * | 2006-07-06 | 2008-01-24 | Denso Corp | 内燃機関の停止制御装置 |
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WO2013088526A1 (ja) * | 2011-12-14 | 2013-06-20 | トヨタ自動車株式会社 | 内燃機関の停止制御装置 |
Also Published As
Publication number | Publication date |
---|---|
DE112014002707T5 (de) | 2016-03-10 |
CN105283334B (zh) | 2018-02-09 |
JP2014237385A (ja) | 2014-12-18 |
US9517762B2 (en) | 2016-12-13 |
US20160114789A1 (en) | 2016-04-28 |
JP6105399B2 (ja) | 2017-03-29 |
BR112015030648A2 (pt) | 2020-10-27 |
BR112015030648B1 (pt) | 2022-01-04 |
CN105283334A (zh) | 2016-01-27 |
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