WO2017047302A1 - エンジン制御装置、空調システム、および、空調制御装置に用いるプログラム - Google Patents
エンジン制御装置、空調システム、および、空調制御装置に用いるプログラム Download PDFInfo
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- WO2017047302A1 WO2017047302A1 PCT/JP2016/073693 JP2016073693W WO2017047302A1 WO 2017047302 A1 WO2017047302 A1 WO 2017047302A1 JP 2016073693 W JP2016073693 W JP 2016073693W WO 2017047302 A1 WO2017047302 A1 WO 2017047302A1
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- Prior art keywords
- air
- engine
- ratio
- outside air
- outside
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00821—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being ventilating, air admitting or air distributing devices
- B60H1/00828—Ventilators, e.g. speed control
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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
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00735—Control systems or circuits characterised by their input, i.e. by the detection, measurement or calculation of particular conditions, e.g. signal treatment, dynamic models
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H1/00885—Controlling the flow of heating or cooling liquid, e.g. valves or pumps
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00985—Control systems or circuits characterised by display or indicating devices, e.g. voice simulators
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/02—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant
- B60H1/04—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant from cooling liquid of the plant
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/02—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant
- B60H1/04—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant from cooling liquid of the plant
- B60H1/06—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant from cooling liquid of the plant directly from main radiator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P7/00—Controlling of coolant flow
- F01P7/14—Controlling of coolant flow the coolant being liquid
- F01P7/16—Controlling of coolant flow the coolant being liquid by thermostatic control
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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
- F02D41/021—Introducing corrections for particular conditions exterior to the engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N11/00—Starting of engines by means of electric motors
- F02N11/08—Circuits or control means specially adapted for starting of engines
- F02N11/0814—Circuits or control means specially adapted for starting of engines comprising means for controlling automatic idle-start-stop
- F02N11/0818—Conditions for starting or stopping the engine or for deactivating the idle-start-stop mode
- F02N11/0833—Vehicle conditions
- F02N11/084—State of vehicle accessories, e.g. air condition or power steering
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00821—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being ventilating, air admitting or air distributing devices
- B60H1/00835—Damper doors, e.g. position control
- B60H1/00849—Damper doors, e.g. position control for selectively commanding the induction of outside or inside air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2025/00—Measuring
- F01P2025/08—Temperature
- F01P2025/12—Cabin temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2025/00—Measuring
- F01P2025/08—Temperature
- F01P2025/13—Ambient temperature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2025/00—Measuring
- F01P2025/08—Temperature
- F01P2025/32—Engine outcoming fluid temperature
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
- F01P2060/00—Cooling circuits using auxiliaries
- F01P2060/08—Cabin heater
Definitions
- the present disclosure relates to an engine control device, an air conditioning system, and a program used for the air conditioning control device.
- air conditioners that heat air with engine cooling water are known.
- this type of air conditioner when outside air that is air outside the passenger compartment is introduced and blown out into the passenger compartment, the outside air is heated with the cooling water.
- the cooling water is deprived of heat by the outside air, the temperature of the cooling water rises slowly. As a result, the heating effect cannot be obtained early.
- temperature increase control in which the engine is controlled so that the temperature of the cooling water is increased more than usual in winter when the inside temperature and outside temperature are low (see, for example, Patent Document 1).
- an object of the present disclosure is to provide a technique for adjusting the amount of heat generated by an engine in accordance with an outside air introduction ratio in a vehicle that performs heating using engine coolant.
- an engine control device that controls operation of an engine that generates driving force for traveling of a vehicle introduces air into an air conditioning casing and heats the air with cooling water of the engine.
- the air conditioner that blows out into the vehicle interior of the vehicle, the air volume of the air introduced into the air conditioning casing from outside the vehicle cabin to the air volume introduced into the air conditioning casing from outside the vehicle cabin and outside the vehicle compartment.
- the ratio is an outside air introduction ratio
- an acquisition unit that acquires state information based on the state of an air conditioner that affects the outside air introduction ratio, and the outside air introduction ratio based on the state information acquired by the acquisition unit
- the outside air introduction ratio is a second ratio that is lower than the first ratio
- the amount of heat generated by the engine is smaller than the case where is the first ratio.
- a ratio directivity control unit for controlling the operation of the serial engine.
- the engine control device is based on the state information based on the state of the air conditioner having an influence on the outside air introduction ratio, and is lower than the first ratio than when the outside air introduction ratio is the first ratio.
- the ratio is 2
- the engine operation is controlled so that the amount of heat generated by the engine becomes smaller.
- an air conditioning system that adjusts a temperature in a vehicle interior of a vehicle is mounted on a vehicle having an engine that generates driving force for traveling and an engine control unit that controls the engine, and an air conditioning casing is provided.
- An air conditioner that introduces air into the air conditioning casing, heats it with the cooling water of the engine, and blows it into the vehicle interior of the vehicle, and an air conditioning control device that controls the operation of the air conditioner,
- the air conditioning control device introduces the ratio of the air volume introduced into the air conditioning casing from outside the vehicle cabin to the air volume introduced into the air conditioning casing from outside the vehicle compartment and outside the vehicle compartment.
- the state determination unit that determines the state of the air conditioner that affects the outside air introduction ratio, and the outside air than the case where the outside air introduction ratio is the first ratio.
- state information based on the state determined by the state determination unit is transmitted to the engine control unit so that the heat generation amount of the engine is reduced.
- a notification unit for notifying to.
- the air conditioning system notifies the engine control unit of state information based on the state of the air conditioner that affects the outside air introduction ratio, so that the outside air introduction ratio is higher than when the outside air introduction ratio is the first ratio.
- the second ratio is lower than the first ratio, the amount of heat generated by the engine is smaller.
- the vehicle is mounted on a vehicle having an engine that generates driving force for traveling and an engine control unit that controls the engine, has an air conditioning casing, and introduces air into the air conditioning casing.
- the program used for the air conditioning control device for controlling the air conditioning device that is heated by the cooling water of the engine and blown into the vehicle interior of the vehicle is the air conditioning control device, and the air conditioning control device is the vehicle interior and exterior of the vehicle interior.
- the outside air introduction ratio is greater than the first ratio.
- the notification unit for notifying the engine control unit of the state information based on the state determined by the state determination unit so that the heat generation amount of the engine is smaller when the second ratio is lower the air conditioning Make the control device work.
- the air conditioning control device notifies the engine control unit of state information based on the state of the air conditioning device that has an influence on the outside air introduction ratio, so that the outside air introduction ratio is higher than the case where the outside air introduction ratio is the first ratio.
- the ratio is the second ratio that is lower than the first ratio, the heat generation amount of the engine is reduced.
- the in-vehicle system is mounted on a vehicle.
- this in-vehicle system includes an engine EG and an air conditioner.
- the engine EG is an internal combustion engine that generates driving force for traveling the vehicle.
- the air conditioner has the indoor air conditioning unit 10 and the refrigeration cycle 30 shown in FIG.
- the indoor air conditioning unit 10 and the refrigeration cycle 30 constitute an air conditioner.
- this air conditioner and a dual-purpose control device described later constitute an air conditioning system.
- the indoor air conditioning unit 10 introduces outside air and inside air, further heats or cools it, and blows it out into the passenger compartment. Thereby, the air conditioning of a vehicle interior is performed.
- the outside air and the inside air are air outside the passenger compartment and air inside the passenger compartment, respectively.
- the indoor air conditioning unit 10 includes an air conditioning casing 11, a blower 12, an evaporator 13, a heater core 14, and the like. And the air blower 12, the evaporator 13, the heater core 14, etc. are accommodated in the air-conditioning casing 11 which forms the outer shell of the indoor air-conditioning unit 10.
- the indoor air conditioning unit 10 is disposed inside the instrument panel at the forefront of the vehicle interior.
- the air conditioning casing 11 forms an air passage for the blown air that is blown into the vehicle interior.
- a partition plate 111 that partitions the air passage inside the air conditioning casing 11 into two air passages, an upper first air passage 112 and a lower second air passage 113, is disposed. ing.
- the partition plate 111 separates the first air passage 112 and the second air passage 113.
- the blower 12 blows air to the passenger compartment.
- the blower 12 includes first and second blower fans 121 and 122 made of a centrifugal multiblade fan (specifically, a sirocco fan).
- the first and second blower fans 121 and 122 are rotatably accommodated in first and second scroll casings (not shown) disposed in the first and second air passages 112 and 113, respectively.
- the first blown air blown by the first blower fan 121 flows through the first air passage 112, and the second blown air blown by the second blower fan 122 passes through the second air passage 113. .
- the inside / outside air switching box 20 is disposed on the upstream side of the air flow of the blower 12 and on the most upstream side of the air flow of the air conditioning casing 11.
- the inside / outside air switching box 20 is also included in the indoor air conditioning unit 10.
- the inside / outside air switching box 20 switches the air introduced into the suction side of the first and second blower fans 121 and 122 between the outside air and the inside air.
- the inside / outside air switching box 20 is formed with an inside air introduction port 21 and an outside air introduction port 22. Inside air is introduced from the inside air introduction port 21 into the inside / outside air switching box 20. Outside air is introduced from the outside air inlet 22 into the inside / outside air switching box 20.
- Inside / outside air switching box 20 has an inside / outside air switching door 23.
- the inside / outside air switching door 23 is also included in the indoor air conditioning unit 10.
- the inside / outside air switching door 23 is a pillar having a fan-shaped cross section as shown in FIG.
- the inside / outside air switching door 23 is rotatable about the sector-shaped central portion.
- the inside / outside air switching door 23 continuously adjusts the opening areas of the outside air introduction port 22 and the inside air introduction port 21 by this rotation. By this adjustment, the suction port mode and the outside air introduction ratio change.
- the outside air introduction ratio is the ratio of the air volume of the outside air to the total air volume of the inside air and the outside air.
- the air volume of the inside air is the volume of air flowing into the inside / outside air switching box 20 from the inside air inlet 21.
- the air volume of the outside air is the volume of air flowing into the inside / outside air switching box 20 from the outside air inlet 22.
- the inlet mode there are an inside air mode, an outside air mode, and an inside / outside air two-layer mode.
- the inside air mode corresponds to a mode in which almost only inside air is introduced into both the first air passage 112 and the second air passage 113 and blown out into the vehicle interior.
- the outside air mode corresponds to a mode in which almost only outside air is introduced into both the first air passage 112 and the second air passage 113 and blown out into the vehicle interior.
- the inside air mode In the inside air mode, one end 23 a of the fan-shaped circumferential portion faces the most upstream end 111 a of the partition plate 111. As a result, the introduction of outside air from the outside air inlet 22 is blocked. That is, only the inside air is introduced into the inside / outside air switching box 20 from the inside air introduction port 21. In the inside air mode, the outside air introduction ratio is 5% or less (for example, 0%).
- the outside air introduction ratio is 95% or more (for example, 100%).
- any one of the portions 23 c between the one end 23 a and the other end 23 b of the sector-shaped circumferential portion faces the uppermost stream end 111 a of the partition plate 111. .
- the inside air and the outside air are introduced into the inside / outside air switching box 20 from the inside air introduction port 21 and the outside air introduction port 22, respectively.
- all the inside air introduced from the inside air introduction port 21 is introduced into the second air passage 113.
- all the outside air introduced from the outside air inlet 22 is introduced into the first air passage 112. That is, all the air introduced into the first air passage 112 becomes outside air. Further, all the air introduced into the second air passage 113 becomes the inside air.
- the outside air introduction ratio changes according to the position of the inside / outside air switching door 23. Specifically, the outside air introduction ratio increases as the inside / outside air switching door 23 approaches the inside air introduction port 21. Moreover, the outside air introduction ratio decreases as the inside / outside air switching door 23 approaches the outside air introduction port 22.
- the outside air introduction ratio in the inside / outside air two-layer mode is larger than 0% and smaller than 100%.
- an extractor (not shown) communicates with the outside of the passenger compartment. Therefore, in this case, the inside air is discharged out of the passenger compartment through the extractor.
- the extractor In the inside air mode and the inside / outside air two-layer mode, the extractor is blocked from the outside of the passenger compartment. Therefore, in this case, the inside air circulates without being exhausted from the passenger compartment to the outside of the passenger compartment.
- An evaporator 13 is disposed on the downstream side of the air flow of the blower 12.
- the evaporator 13 constitutes the refrigeration cycle 30 together with the compressor 31, the condenser 32, the gas-liquid separator 33, the expansion valve 34, and the like.
- the compressor 31 is disposed in the engine room, sucks the refrigerant in the refrigeration cycle 30, compresses it, and discharges it.
- the condenser 32 is disposed in the engine room, and heat-exchanges the refrigerant flowing through the inside and the outside air blown from the blower fan 35 as an outdoor blower to condense and liquefy the compressed refrigerant.
- the blower fan 35 is an electric blower.
- the gas-liquid separator 33 performs gas-liquid separation on the condensed and liquefied refrigerant and allows only the liquid refrigerant to flow downstream.
- the expansion valve 34 decompresses and expands the liquid refrigerant that has flowed out of the gas-liquid separator 33.
- the evaporator 13 evaporates the refrigerant expanded by the expansion valve 34 after being compressed by the compressor 31 in the refrigeration cycle 30, and exchanges heat between the refrigerant and the blown air, whereby the first and second blower fans 121 and 122 are used. Cools the air sent from
- the evaporator 13 is disposed so as to penetrate through holes provided in the partition plate 111.
- positioned in the 1st air path 112 among the evaporators 13 is an upper side heat exchange part.
- path 113 among the evaporators 13 is a lower side heat exchange part.
- the first blown air is cooled in the upper heat exchange section of the evaporator 13. Further, the second blown air is cooled in the lower heat exchange section of the evaporator 13.
- a heater core 14 is disposed on the downstream side of the air flow of the evaporator 13.
- the heater core 14 is a heat exchanger for heating that heats the air that has passed through the evaporator 13 by exchanging heat between the cooling water of the engine EG and the air that has passed through the evaporator 13. That is, the heater core 14 heats air using the heat generated by the engine EG.
- a cooling water circuit 40 in which the cooling water circulates between the heater core 14 and the engine EG is configured.
- the cooling water circuit 40 is provided with a cooling water passage 41 and an electric water pump 42 for circulating the cooling water.
- the electric water pump 42 is an electric water pump whose rotation speed is controlled by a control voltage output from the air conditioning control device 50. The amount of cooling water circulation in the cooling water circuit 40 is determined according to this rotational speed.
- the heater core 14 is disposed so as to penetrate through holes provided in the partition plate 111. And the part arrange
- a passage 161 is formed. In the space on the downstream side of the air flow of the heater core 14 in the first air passage 112, the first blown air that has passed through the first bypass passage 161 merges with the first blown air heated in the heater core 14. ing.
- a second bypass passage for passing the second blown air that has passed through the lower heat exchange section of the evaporator 13 bypassing the lower heating section of the heater core 14 is provided below the heater core 14 of the second air path 113. 162 is formed. In the space on the downstream side of the air flow of the heater core 14 in the second air passage 113, the second blown air that has passed through the second bypass passage 162 joins the second blown air heated in the heater core 14. ing.
- first and second air mix doors 17 and 18 are disposed between the evaporator 13 and the heater core 14 in the first and second air passages 112 and 113.
- the first air mix door 17 is a flow rate ratio between the amount of blown air passing through the upper heat exchange part of the heater core 14 and the amount of blown air passing through the first bypass passage 161 in the air after passing through the evaporator 13 (that is, It is a member for adjusting an air mix opening degree.
- the second air mix door 18 has a flow rate ratio between the amount of blown air passing through the lower heat exchange part of the heater core 14 and the amount of blown air passing through the second bypass passage 162 in the air after passing through the evaporator 13 (that is, It is a member for adjusting an air mix opening degree.
- a defroster opening 11a, a face opening 11b, and a foot opening 11c are formed in the most downstream portion of the air conditioning casing 11 to allow the blown air blown into the passenger compartment to flow out of the air conditioning casing 11.
- the defroster opening 11 a is an opening hole for guiding the blown air flowing in the air conditioning casing 11 to the vehicle front window glass W.
- the defroster opening 11a is connected to a defroster outlet 19a disposed in the vehicle interior via an outlet duct, and air whose temperature is adjusted from the defroster outlet 19a toward the inner surface of the vehicle front window glass W is blown out. Is done.
- the face opening 11b is an opening hole for guiding the blown air flowing in the air conditioning casing 11 to the upper body of the occupant.
- the face opening portion 11b is connected to a face air outlet 19b disposed in the vehicle compartment via an air outlet duct, and air whose temperature is adjusted is blown out from the face air outlet 19b toward the upper body of the occupant.
- the foot opening 11c is an opening hole for guiding the blast air flowing in the air conditioning casing 11 to the lower body of the occupant, particularly to the feet.
- the foot opening 11c is connected to a foot outlet 19c via an outlet duct, and air whose temperature is adjusted is blown out from the foot outlet 19c toward the feet of the lower half of the occupant.
- a defroster door 20a, a face door 20b, and a foot door 20c are rotatably arranged at upstream portions of the openings 11a to 11c.
- the outlet mode switched by each door 20a, 20b, 20c includes a face mode, a bi-level mode, and a foot defroster mode.
- face mode the face opening 11b is fully opened, and air blows out from the face outlet 19b toward the upper body of the occupant.
- bi-level mode both the face opening portion 11b and the foot opening portion 11c are opened, and air is blown out toward the upper body and the lower body of the passenger in the vehicle interior.
- the foot defroster mode the foot opening 11c is fully opened, the defroster opening 11a is opened by a small opening, and air is mainly blown from the foot outlet 19c.
- the suction port mode is set to the inside / outside air two-layer mode and the outlet mode is set to the foot defroster mode or the bi-level mode will be described.
- the outside air introduced into the first air passage 112 is blown out upward in the passenger compartment through the defroster opening 11a or the face opening 11b, and the inside air introduced into the second air passage 113 is foot opening 11c. Is blown out to the lower side of the passenger compartment.
- the in-vehicle system of the present embodiment includes the dual control device 200 and various sensors 211, 212, 213, 214, 215, 216, 217, 261, 262, 263 and various actuators 221, 222, 223, 224 shown in FIG. 225, 226, 271, 272, 273, 274.
- the dual-purpose control device 200 is composed of a well-known microcomputer including a CPU, ROM, flash memory, I / O, etc. and its peripheral circuits.
- the CPU executes a program recorded in the ROM. With this execution, the CPU executes the air-conditioning control process 210 and the engine control process 220 in parallel in a multitask process.
- the processing executed by the CPU will be described as processing executed by the dual control device 200.
- the dual-purpose control device 200 corresponds to both an engine control device and an air conditioning control device.
- the inside air temperature sensor 211 detects the air temperature in the passenger compartment, more specifically, the air temperature inside the instrument panel.
- the outside air temperature sensor 212 detects the outside air temperature outside the passenger compartment.
- the solar radiation sensor 213 detects the amount of solar radiation.
- the water temperature sensor 214 detects the temperature of the cooling water flowing through the cooling water channel 41.
- the near window temperature sensor 215 detects the temperature in the vicinity of the vehicle front window glass W in the vehicle interior.
- the near-window humidity sensor 216 detects the relative humidity in the vicinity of the vehicle front window glass W in the vehicle interior.
- the window surface temperature sensor 217 detects the air temperature inside the vehicle interior side of the vehicle front window glass W.
- the inside / outside switching actuator 221 is a motor that adjusts the position of the inside / outside air switching door 23.
- the mode actuator 222 is a motor that adjusts the positions of the defroster door 20a, the face door 20b, and the foot door 20c.
- the compressor motor 223 is a motor that drives the compressor 31.
- the first air mix actuator 224 is a motor that adjusts the position of the first air mix door 17.
- the second air mix actuator 225 is a motor that adjusts the position of the second air mix door 18.
- the blower motor 226 is a motor that drives the first and second blower fans 121 and 122.
- Accelerator opening sensor 261 detects the depression amount of the accelerator pedal by the driver of the vehicle.
- Air flow sensor 262 detects the flow rate of air passing through the intake pipe of engine EG.
- the crank angle sensor 263 outputs a crank pulse signal corresponding to the crank angle.
- the starter switch 264 is a switch operated by the user for starting the engine EG.
- the throttle opening sensor 265 detects the opening of the throttle valve. The throttle valve adjusts the flow rate of air sent from the intake pipe into the engine.
- the starter 271 performs cranking when the engine is started.
- the injection valve 272 injects fuel supplied to the engine.
- the throttle valve actuator 273 controls the opening degree of the throttle valve.
- the igniter 274 burns the air-fuel mixture sent from the intake pipe into the engine.
- the operation panel 201 includes an air conditioning operation switch 202, an operation mode changeover switch 203, and a vehicle interior temperature setting switch 204.
- the dual-purpose control device 200 starts execution of the air conditioning control processing 210 after the vehicle is turned on. Then, the dual-purpose control device 200 executes the process shown in FIG. 3 in the air conditioning control process 210.
- step S1 various data are initialized. Subsequently, in step S2, the set temperature Tset is acquired based on the content of the user operation on the vehicle interior temperature setting switch 204.
- a target blowing temperature TAO is determined based on the following equation.
- TAO Kset ⁇ Tset ⁇ Kr ⁇ Tr ⁇ Kam ⁇ Tam ⁇ Ks ⁇ Ts + C
- Tr is the temperature in the passenger compartment (that is, the internal air temperature) detected by the internal air temperature sensor 211.
- Tam is the temperature outside the passenger compartment (that is, the outside temperature) detected by the outside temperature sensor 212.
- Ts is the amount of solar radiation detected by the solar radiation sensor 213.
- Kset, Kr, Kam, and Ks are constants indicating the control gain, and C is a correction constant.
- step S5 a voltage value to be applied to the blower motor 226 is determined based on the target outlet temperature TAO, the engine coolant temperature detected by the water temperature sensor 214, the outlet mode, and the like. The higher the voltage value, the higher the rotation speed of the first and second blower fans 121 and 122.
- step S6 one of the face mode, the bi-level mode, the foot mode, and the foot defroster mode is selected as the current outlet mode based on the target outlet temperature TAO, the relative humidity RHW, and the like.
- the relative humidity RHW is the relative humidity of the vehicle interior side surface of the vehicle front window glass W.
- the dual-purpose control device 200 calculates the relative humidity RHW based on detection results of the window vicinity temperature sensor 215, the window vicinity humidity sensor 216, and the window surface temperature sensor 217 by a known method.
- step S6 when the relative humidity RHW is less than the reference humidity, the dual control device 200 sets one of the face mode, the bi-level mode, and the foot mode as the current outlet mode based on the target outlet temperature TAO. select.
- the dual-purpose control device 200 selects the foot defroster mode as the current outlet mode when the relative humidity RHW is equal to or higher than the reference humidity.
- step S7 a voltage value to be applied to the compressor motor 223 is determined based on the target blowing temperature TAO or the like.
- the higher the voltage value the higher the rotational speed of the compressor motor 223. Therefore, the higher the voltage value, the better the refrigerant discharge capacity of the compressor 31.
- step S8 the inlet mode is determined. Specifically, as shown in FIG. 4, first, in step S81, the provisional mode is determined based on the target blowing temperature TAO.
- the temporary mode when the temporary mode is the outside air mode, the temporary mode is switched to the inside air mode if the target outlet temperature TAO is lower than the first reference temperature T1.
- the provisional mode is the outside air mode, the provisional mode is maintained in the outside air mode if the target blowing temperature TAO is equal to or higher than the first reference temperature T1.
- the provisional mode when the provisional mode is the inside air mode, the provisional mode is maintained in the inside air mode if the target blowing temperature TAO is lower than the second reference temperature T2.
- the provisional mode is switched to the outside air mode if the target outlet temperature TAO is equal to or higher than the second reference temperature T2.
- the first reference temperature T1 is lower than the second reference temperature T2.
- step S82 it is determined whether or not the provisional mode is the outside air mode. If it is not the outside air mode, the process proceeds to step S83. If it is outside air mode, it will progress to Step S84. In step S83, the suction port mode is determined to be the inside air mode, and the process proceeds to step S88.
- step S84 the inlet mode is determined based on the outside temperature Tam, the inside temperature Tr, and the set temperature Tset.
- the suction port mode is determined as the inside / outside air two-layer mode. And if the latter is high among the outside temperature Tam and the inside temperature Tr, the inlet mode is determined as the outside air mode.
- the suction port mode is determined as the outside air mode. And if the latter is high among the outside temperature Tam and the inside temperature Tr, the suction port mode is determined to be the inside / outside air two-layer mode.
- Tset for example, 25 ° C.
- step S88 the determined inlet mode is notified to the engine control process 220.
- the suction port mode information may be recorded at a reference address by the engine control processing 220 in the RAM.
- step S9 the air mix opening degree of the first air mix door 17 and the air mix opening degree of the second air mix door 18 are determined based on the target outlet temperature TAO, the inlet mode, and the outlet mode.
- step S10 the actuators 221, 222, 223, 224, 225, and 226 are controlled so that the control states determined in steps S4, S5, S6, S7, S8, and S9 described above are realized.
- the dual-purpose control device 200 has the inside / outside air switching door 23 disposed at a position where the outside air introduction ratio becomes a fixed ratio (for example, 50%).
- the inside / outside switching actuator 221 is controlled.
- step S11 the process waits for a control cycle ⁇ (for example, 250 milliseconds), and returns to step S2 when it is determined that the control cycle ⁇ has elapsed.
- a control cycle ⁇ for example, 250 milliseconds
- the dual-purpose control apparatus 200 periodically repeats the processes of steps S2 to S10 in the air conditioning control process 210.
- the dual control device 200 controls the starter 271 to start the engine EG. Further, the dual-purpose control device 200 determines the fuel injection amount, the fuel injection timing, the throttle opening, the ignition timing, and the like based on various parameters during the operation of the engine EG in the engine control processing 220.
- the various parameters include the accelerator opening detected by the accelerator opening sensor 261, the air flow rate detected by the air flow sensor 262, and the rotational speed of the engine EG specified based on the crank pulse signal from the crank angle sensor 263.
- the engine water temperature detected by the water temperature sensor 214 is included. Then, the injection valve 272, the throttle valve actuator 273, the igniter 274, and the like are controlled so that the determined fuel injection amount, fuel injection timing, throttle opening, ignition timing, and the like are realized.
- the dual-purpose control apparatus 200 first initializes variables to be used in step S205 after being activated by turning on the IG. Subsequently, in step S210, the engine EG is awaited for start-up, and at the time of start-up, the initial cooling water temperature Two is acquired based on the detection result of the water temperature sensor 214.
- the initial cooling water temperature Two is the temperature of the engine cooling water when the engine is started.
- step S215 the internal temperature Tr detected by the internal temperature sensor 211 is acquired.
- step S220 the outside air temperature Tam detected by the outside air temperature sensor 212 is acquired.
- step S225 the current detection result of the water temperature sensor 214 is acquired as the current water temperature Tw.
- step S230 the rotational speed Ne of the engine EG is specified based on the crank pulse signal from the crank angle sensor 263.
- the throttle opening degree Sw detected by the throttle opening degree sensor 265 is acquired.
- the throttle opening degree Sw corresponds to the load of the engine EG.
- step S240 it is determined whether or not the initial cooling water temperature Two is less than 0 ° C.
- the initial cooling water temperature Two is less than 0 ° C., for example, when the vehicle is parked for a long time at night in winter. If it is less than 0 ° C, the process proceeds to step S250, and if it is 0 ° C or more, the process proceeds to step S245.
- 0 ° C. is used as an example of the reference temperature, but a temperature other than 0 ° C. (for example, a temperature of 10 ° C. or lower ⁇ 5 ° C. or higher) may be used.
- step S245 the ignition timing is set to the normal basic timing.
- the basic timing is MBT, which is the timing at which the torque becomes highest.
- MBT is an abbreviation for Minimum advance for Best Torque.
- the ignition timing is represented by an advance amount with respect to the compression top dead center. In many cases, the MBT corresponds to an angle slightly advanced from the compression top dead center.
- the MBT is calculated by a known method based on, for example, the engine speed, the throttle opening, and other physical quantities acquired in steps S230 and S240.
- the process returns to step S215.
- step S250 the current inlet mode notified in step S88 of the air conditioning control process 210 is acquired.
- the information on the suction port mode is read from an area in the RAM where the information on the suction port mode is recorded.
- the information on the suction port mode is state information based on the state of the air conditioner that affects the outside air introduction ratio. More specifically, the information on the suction port mode is information indicating the state of the air conditioner that affects the outside air introduction ratio. Actually, the outside air introduction ratio varies depending on whether the suction port mode is the outside air mode, the inside air mode, or the inside / outside air two-layer mode.
- step S255 it is determined whether or not the suction port mode read out in the immediately preceding step S240 is the inside / outside air two-layer mode. If it is inside / outside air two-layer mode, the process proceeds to step S245. If it is not inside / outside air two-layer mode, the process proceeds to step S260. As a case where it is not the inside / outside air two-layer mode, there is a case where it is the outside air mode. For example, when heating is performed in winter, the possibility of window fogging is high. Therefore, when heating is performed in winter, the outside air mode is often selected.
- step S260 it is determined whether or not the outside air temperature Tam detected by the outside air temperature sensor 212 is less than a constant reference outside air temperature (for example, 10 ° C.). When it is less than the reference outside temperature, the process proceeds to step S265, and when it is not less than the reference outside temperature, the process proceeds to step S245.
- a constant reference outside air temperature for example, 10 ° C.
- step S265 it is determined whether or not the internal air temperature Tr detected by the internal air temperature sensor 211 is less than a constant reference internal air temperature (for example, 10 ° C.). If it is less than the reference internal temperature, the process proceeds to step S270, and if it is not less than the reference internal temperature, the process proceeds to step S245.
- a constant reference internal air temperature for example, 10 ° C.
- step S270 the exothermic bulk Qc is calculated.
- the calorific value Qc calculated is a positive value.
- the exothermic bulk Qc is the amount of heat required to make up for the insufficient heating capacity of the blown air by the heater core 14. As will be described later, if the heat generation volume Qc is positive, the heat generation amount of the engine EG is raised more than the heat generation amount due to normal engine operation.
- the dual-purpose control device 200 refers to the reference required heat generation amount map, and calculates the heat generation bulk amount Qc based on the initial cooling water temperature Two and the current water temperature Tw detected in steps S210 and S225.
- the reference required heat generation amount map is a map in which the relationship between the initial cooling water temperature Two, the current water temperature Tw, and the heat generation bulk amount Qc is defined in advance.
- the reference required heat generation amount map is recorded in advance in the ROM of the dual control device 200.
- step S270 the process proceeds to step S275.
- step S275 the driving heat generation amount Qd is calculated based on the engine speed Ne and the throttle opening degree Sw acquired in steps S230 and S235.
- the value of the driving heat generation amount Qd is positive.
- the driving heat generation amount Qd is an engine heat generation amount on the assumption that ignition is performed at the basic timing MBT.
- the driving heat generation amount Qd is acquired by applying the engine speed EG of the engine EG and the throttle opening degree Sw to a predetermined map in the ROM. In this map, the correspondence relationship between the rotational speed Ne, the throttle opening degree Sw, and the driving heat generation amount Qd is recorded.
- step S280 a value obtained by adding the calorific value Qc calculated in the immediately preceding step S270 to the driving calorific value Qd calculated in the immediately preceding step S275 is necessary.
- the calorific value is Qn.
- step S285 the ignition timing is calculated.
- the ignition timing calculated here is a value retarded from the basic timing (that is, MBT). It is known that when the ignition timing is retarded from MBT, the greater the retard amount, the lower the operating efficiency and the greater the amount of heat generated by the engine EG. Therefore, the dual control device 200 increases the retard amount of the ignition timing with respect to the MBT as the required heat generation amount Qn increases. Note that techniques for delaying the ignition timing in order to increase the amount of heat generated by the engine are described in, for example, Japanese Patent Application Laid-Open Nos. 2005-016465 and 2009-167856. After step S285, the process returns to step S215.
- the dual control device 200 controls the igniter 274 as described above so that the ignition timing determined in step S245 or S285 of the ignition timing determination process is realized.
- the dual control device 200 has the outside air introduction ratio.
- the operation of the engine EG is controlled so that the heat generation amount of the engine EG becomes smaller in the case of the second ratio than in the case of the first ratio. This operation is realized whether the vehicle is traveling or not.
- the second ratio is lower than the first ratio.
- the first ratio corresponds to the ratio in the outside air mode
- the second ratio corresponds to the ratio in the inside / outside air two-layer mode.
- the amount of heat generated by the engine can be adjusted according to the outside air introduction ratio.
- the temperature change degree of the engine cooling water can be adjusted according to the outside air introduction ratio.
- the dual-purpose control apparatus 200 of the present embodiment sets the heating volume Qc to zero or more in step S270 when the initial cooling water temperature Two, the outside air temperature Tam, and the inside air temperature Tr are low as described above. Further, the dual-purpose control device 200 determines an ignition timing delayed from the MBT (that is, the basic timing) in step S285 based on the heat generation bulk amount Qc. That is, the dual-purpose control device 200 performs the water temperature increase engine control. As a result, as described above, the heat generation amount of the engine EG increases as compared with the heat generation amount generated by driving the normal engine EG. Therefore, the engine water temperature warms up early.
- the dual-purpose control device 200 does not perform such water temperature increase engine control if the inlet mode is the inside / outside air two-layer mode even when the initial cooling water temperature Two, the inside air temperature Tr, and the outside air temperature Tam are low. The reason is as follows.
- outside air for anti-fogging and inside air for heating the vehicle interior are introduced into the first air passage 112 and the second air passage 113, respectively. Therefore, less heat is taken away from the engine coolant by the heater core 14 than in the outside air mode. As a result, the engine coolant temperature tends to rise early. At this time, since the warm inside air is circulated without being exhausted, the temperature in the passenger compartment is improved early. In addition, since the outside air is blown out to the vehicle front window glass W at this time, the anti-fogging performance is hardly impaired.
- the suction port mode determination process in FIG. 4 is replaced with the process shown in FIG. Further, in step S10 of FIG. 3, when the suction port mode is the inside / outside air two-layer mode, the dual-purpose control device 23 has the inside / outside air switching door 23 at a position where the outside air introduction ratio P determined in the immediately preceding step S8 is realized.
- the inside / outside switching actuator 221 is controlled so that is arranged.
- the ignition timing determination process in FIG. 5 is replaced with the process shown in FIG. Steps denoted by the same reference numerals in FIGS. 4 and 7 have the same processing contents. In addition, the steps denoted by the same reference numerals in FIGS. 5 and 8 have the same processing contents.
- step S85 it is determined whether or not the suction port mode determined in the previous step S84 is the inside / outside air two-layer mode. If it is the inside / outside air two-layer mode, the process proceeds to step S86. If it is not the inside / outside air two-layer mode, that is, if it is the outside air mode, the process proceeds to step S89.
- step S86 the relative humidity RHW of the vehicle interior side surface of the vehicle front window glass W is calculated.
- the method for calculating the relative humidity RHW is as described in the first embodiment.
- step S87 the outside air introduction ratio P in the inside / outside air two-layer mode is determined based on the relative humidity RHW calculated in the immediately preceding step S86. Specifically, the higher the relative humidity RHW, the higher the outside air introduction ratio P. This is because it is desirable to increase the amount of outside air introduced for anti-fogging as the relative humidity RHW is higher. As described above, when the relative humidity RHW is equal to or higher than the reference humidity and the inside / outside air two-layer mode is selected, the air outlet mode is the foot defroster mode. After step S87, the process proceeds to step S89.
- step S89 the determined inlet mode is notified to the engine control process 220.
- the determined inlet mode is the inside / outside air two-layer mode
- the outside air introduction ratio P determined in the immediately preceding step S87 is also notified to the engine control process 220 together with the determined inlet mode.
- the information on the suction port mode and the outside air introduction ratio P is state information based on the state of the air conditioner that affects the outside air introduction ratio.
- the notification method is the same as step S88 in the first embodiment. After step S89, the process proceeds to step S9 in FIG.
- step S251 the current inlet mode notified in step S89 of the air-conditioning control process 210 and the outside air introduction ratio P in the inside / outside air two-layer mode, if any, are acquired.
- the acquisition method is the same as step S250 of the first embodiment.
- step S251 the process proceeds to step S255.
- step S257 the outside air introduction ratio P acquired in step S251 immediately before it is determined whether the reference ratio P 0 is smaller than not. If the outside air introduction ratio P is smaller than the reference ratio P 0 , the process proceeds to step S245. If outside air introduction ratio P is not less than the reference ratio P 0 the process proceeds to step S260.
- the reference ratio P 0 is a value larger than 50% and smaller than 100%. For example, the reference ratio P 0 may be 75%.
- the dual-purpose control apparatus 200 of the present embodiment proceeds to step S260 if the outside air introduction ratio P is equal to or higher than the reference ratio even if the suction port mode is the inside / outside air two-layer mode. . Therefore, in this case, the ignition timing delayed from the basic timing (that is, MBT) may be calculated in steps S270 to S285 based on the determination results of steps S260 and S265. This is because even in the inside / outside air two-layer mode, if the outside air introduction ratio P is sufficiently high, it is effective to increase the heat generation of the engine EG more than usual.
- the dual-purpose control device 200 sets the ignition timing as the basic timing in step S245 as in the first embodiment. .
- the dual-purpose control device 200 changes the heat generation amount of the engine according to the outside air introduction ratio P even in the inside / outside air two-layer mode. Specifically, the heat generation amount of the engine is increased as the outside air introduction ratio P is higher. As a result, the higher the outside air introduction ratio P, the higher the temperature rise rate of the engine coolant. By doing so, the heat generation amount of the engine can be controlled more flexibly. Other effects are the same as those of the first embodiment.
- the ignition timing determination process of FIG. 8 is replaced with the process shown in FIG. Steps denoted by the same reference numerals in FIGS. 8 and 9 have the same processing contents.
- step S243 the exothermic bulk Qc is calculated.
- the calorific value Qc calculated is a positive value.
- the calculation method is different from the method in step S270.
- the dual-purpose control device 200 calculates the heat generation bulk amount Qc based on various parameters.
- Various parameters include the initial cooling water temperature Two, the internal air temperature Tr, the external air temperature Tam, and the current water temperature Tw detected in steps S210, S215, S220, and S225.
- the various parameters also include the outside air introduction ratio P acquired in the immediately preceding step S251.
- Qc may be calculated using an equation as shown in FIG.
- H 0 , H 1 , H 2 , H 3 , H 4 , and H 5 are constants.
- H 1 is negative. Therefore, the heat generation bulkiness Qc decreases as the internal temperature Tr increases. This is because the higher the internal temperature Tr, the smaller the additional heat generation amount of the engine EG necessary for improving the heating function.
- H 2 is negative. Therefore, the higher the outside air temperature Tam, the smaller the heat generation volume Qc. This is because the higher the outside air temperature Tam, the smaller the additional heat generation amount of the engine EG necessary for improving the heating function.
- H 3 is positive. Therefore, the higher the outside air introduction ratio P, the larger the heat generation bulk amount Qc. This is because the additional heat generation amount of the engine EG necessary for improving the heating function increases as the outside air introduction ratio P increases.
- H 4 is negative. Therefore, as the current water temperature Tw increases, the exothermic bulk Qc decreases. H 5 is negative. Therefore, the higher the initial cooling water temperature Two, the smaller the exothermic bulk Qc.
- the constants H 0 , H 1 , H 2 , H 3 , H 4 , and H 5 are generated when the internal temperature Tr, the external temperature Tam, the external air introduction ratio P, the initial water temperature Two, and the current water temperature Tw are within normal ranges.
- the amount Qc is determined so as to be positive.
- the exothermic bulk Qc calculated in steps S270 and S243 is compared with each other.
- the exothermic bulk amount Qc calculated in step S270 is larger than the exothermic bulk amount Qc calculated in step S243. This is because the heating volume Qc calculated in step S270 is the heating volume Qc in the outside air mode with the outside air introduction ratio of 100%.
- the dual-purpose control device 200 changes the heat generation amount of the engine linearly with respect to the outside air introduction ratio P, the inside temperature Tr, and the outside temperature Tam in the inside / outside air two-layer mode. In this way, the heat generation amount of the engine can be controlled more flexibly. Other effects are the same as those of the second embodiment.
- the processing content of the dual-purpose control device 200 is changed with respect to the in-vehicle systems of the first, second, and third embodiments.
- the dual-purpose control device 200 executes an idle stop process 230 and an allowed temperature setting process 240 as shown in FIG. 11 in addition to the air conditioning control process 210 and the engine control process 220.
- the dual-purpose control device 200 executes these processes 210, 220, 230, and 240 simultaneously in a multitask process.
- the dual-purpose control device 200 executes an idle stop process 230 during heating. Whether heating is being performed is determined according to the positions of the first air mix door 17 and the second air mix door 18. Specifically, if air passes through the heater core 14, heating is in progress.
- the dual-purpose control device 200 is based on the fact that the current water temperature Tw detected by the water temperature sensor 214 during the operation of the engine EG is equal to or higher than the permitted temperature and a predetermined idle stop condition is satisfied. Then, the actuators 272, 273, and 274 are controlled so that the engine EG stops. As a result, the vehicle enters an idle stop state.
- the idle stop condition is, for example, a condition that the vehicle is stopped and the brake pedal is depressed for a predetermined time or more.
- the dual-purpose control device 200 determines whether the engine EG is satisfied even if the idle stop condition is satisfied. Do not stop. As a result, the vehicle does not enter the idle stop state.
- the dual control device 200 operates the starter 271 based on the fact that the idle stop condition is no longer satisfied in the idle stop state. Thereby, engine EG starts. As a result, the vehicle releases the idle stop state.
- the dual-purpose control device 200 is based on the fact that the current water temperature Tw detected by the water temperature sensor 214 has fallen below the permitted temperature in the idle stop state, even if the idle stop condition is satisfied. Then, the starter 271 is operated. Thereby, engine EG starts. As a result, the vehicle releases the idle stop state.
- idle stop that is, engine EG stop
- idling stop that is, engine EG stop
- the permitted temperature setting process 240 a permitted temperature value used in the idle stop process 230 is set.
- the dual-purpose control device 200 first acquires the current inlet mode notified in step S ⁇ b> 88 or step S ⁇ b> 89 of the air conditioning control process 210 in step S ⁇ b> 305 as shown in FIG. 12.
- the acquisition method is the same as in steps S250 and S251.
- step S310 it is determined whether or not the suction port mode acquired in the previous step S305 is the inside / outside air two-layer mode. If it is inside / outside air two-layer mode, the process proceeds to step S330. If it is not inside / outside air two-layer mode, the process proceeds to step S320. As a case where it is not the inside / outside air two-layer mode, there is a case where it is the outside air mode. For example, when heating is performed in winter, the possibility of window fogging is high. Therefore, when heating is performed in winter, the outside air mode is often selected.
- step S320 the permitted temperature is set to a predetermined value A. After step S320, the process returns to step S305.
- the permitted temperature is set to a predetermined value B. After step S330, the process returns to step S305.
- the dual-purpose control device 200 repeatedly updates the permitted temperature in the permitted temperature setting process 240.
- the value B is lower than the value A. Therefore, in the case of the inside / outside air two-layer mode, there are more scenes in which the engine is in the idle stop state than in the outside air mode.
- the dual-purpose control device 200 switches the operation of the engine on and off based on whether the suction port mode is the inside / outside air two-layer mode or the outside air mode.
- outside air introduction ratio is lower in the inside / outside air two-layer mode than in the outside air mode. At a low outside air introduction ratio, there is little decrease in the heating effect even if the engine coolant temperature is low. This is because the warm inside air is circulated without being exhausted.
- the permitted temperature can be set low in the inside / outside air two-layer mode.
- the engine cooling water temperature can be quickly set to the permitted temperature after the engine is started in winter. Therefore, the fuel efficiency is improved by doing in this way.
- the dual-purpose control apparatus 200 has a lower second ratio (that is, in the inside / outside air two-layer mode) than when the outside air introduction ratio is the first ratio (that is, the outside air introduction ratio in the outside air mode). In the case of the outside air introduction ratio), the permitted temperature is lowered.
- Idle stop is a well-known technique and is disclosed in, for example, Japanese Patent Application Laid-Open No. 2014-227854. If the idling stop state is entered when the temperature of the cooling water is low, the temperature of the engine cooling water does not rise, so the comfort of heating is impaired. According to the inventor's investigation, it is conceivable to switch permission / prohibition of idle stop according to the temperature of the cooling water. However, according to further studies by the inventors, the permission temperature, which is a threshold value for permission for idling stop, varies depending on the condition of the air conditioner. In view of the above points, there arises a problem that the permitted temperature is changed according to the operating state of the air conditioner.
- the permitted temperature can be lowered when the outside air introduction ratio is the second ratio lower than the first ratio than when the outside air introduction ratio is the first ratio. it can.
- the dual-purpose control device 200 starts execution of the permitted temperature setting process 240 after being activated by turning on the IG.
- the variables to be used are initialized.
- the engine EG is awaited for starting, and at the time of starting, the initial cooling water temperature Two is acquired based on the detection result of the water temperature sensor 214.
- step S306 the current intake port mode notified in step S89 of the air-conditioning control process 210 and the outside air introduction ratio P in the inside / outside air two-layer mode are acquired.
- the acquisition method is the same as step S251 of the second embodiment.
- step S310 it is determined whether or not the suction port mode acquired in the previous step S306 is the inside / outside air two-layer mode. If it is inside / outside air two-layer mode, the process proceeds to step S322. If it is not inside / outside air two-layer mode, the process proceeds to step S320. As a case where it is not the inside / outside air two-layer mode, there is a case where it is the outside air mode. For example, when heating is performed in winter, the possibility of window fogging is high. Therefore, when heating is performed in winter, the outside air mode is often selected.
- step S320 the permitted temperature is set to a predetermined value A. After step S320, the process returns to step S306.
- step S322 the inside air temperature Tr detected by the inside air temperature sensor 211 and the outside air temperature Tam detected by the outside air temperature sensor 212 are acquired.
- step S325 the value B is calculated.
- step S330 the permitted temperature is set to the value B that has been calculated in the immediately preceding step S325. After step S330, the process returns to step S306.
- the dual-purpose control device 200 repeatedly updates the permitted temperature in the permitted temperature setting process 240.
- the calculation method of the value B in step S325 will be described with reference to FIG.
- step S325 the dual-purpose control apparatus 200 calculates a value B based on various parameters.
- Various parameters include the initial cooling water temperature Two, the internal air temperature Tr, and the external air temperature Tam acquired in the immediately preceding steps S302 and S322.
- the various parameters also include the outside air introduction ratio P acquired in the immediately preceding step S306.
- the value B may be calculated using an equation as shown in FIG.
- J 0 , J 1 , J 2 , J 3 , and J 4 are constants.
- J 1 is negative. Therefore, the permitted temperature decreases as the inside air temperature increases.
- J 2 is negative. Therefore, the permitted temperature decreases as the outside air temperature Tam increases. The reason for this is that the higher the outside air temperature Tam, the lower the cooling water temperature required for heating comfort.
- J 3 is positive. Therefore, the permitted temperature increases as the outside air introduction ratio P increases. The reason for this is that the higher the outside air introduction ratio P, the higher the coolant temperature required for heating comfort. Further, J 4 is negative, thus, as the initial coolant temperature Two increases, permission temperature is lowered.
- the value B calculated in step S325 is constants J 0 , J 1 , J 2 , J 3 , and so on so as to be always lower than the value A in the range of normally possible variables Tr, Tam, P, Two. J 4 has been set.
- the dual-purpose control device 200 changes the permitted temperature linearly with respect to the outside air introduction ratio P, the inside temperature Tr, and the outside temperature Tam in the inside / outside air two-layer mode. That is, the dual-purpose control device 200 switches the engine operation on and off based on the outside air introduction ratio P, the inside temperature Tr, and the outside temperature Tam in the inside / outside air two-layer mode. In this way, the heat generation amount of the engine can be controlled more flexibly. Other effects are the same as in the fourth embodiment.
- the dual-purpose control device 200 also lowers the permitted temperature when the outside air introduction ratio is the second ratio lower than that when the outside air introduction ratio is the first ratio even in the inside / outside air two-layer mode. To do.
- the dual-purpose control device 200 corresponds to the acquisition unit by executing steps S250, S251, S305, and S306.
- the dual-purpose control apparatus 200 executes steps S240 to S285, the idle stop process 230, and the permitted temperature setting process 240, which corresponds to the ratio-oriented control unit.
- the dual control device 200 corresponds to an idle stop unit by executing the idle stop process 230.
- the dual-purpose control device 200 executes the permitted temperature setting process 240 and corresponds to the permitted temperature setting unit.
- the dual-purpose control device 200 corresponds to the state determination unit by executing S81 to S87.
- the dual control device 200 corresponds to the notification unit by executing S88 and S89.
- the dual-purpose control device 200 functions as an engine control unit by executing the engine control process 220, the idle stop process 230, and the permitted temperature setting process 240.
- the RAM, ROM, and flash memory in each of the above embodiments are all non-transitional tangible recording media.
- the basic timing is not limited to MBT.
- the basic timing may be any ignition timing as long as the outside air introduction ratio is sufficiently low.
- Examples of the state information include information on the suction port mode and information on the outside air introduction ratio.
- the state information may be other information as long as it is information based on the state of the air conditioner that affects the outside air introduction ratio.
- the heat generation bulk amount Qc may be state information
- the necessary heat generation amount Qn may be state information.
- the dual-purpose control device 200 executes all of the air conditioning control process 210, the engine control process 220, the idle stop process 230, and the permitted temperature setting process 240.
- the apparatus that executes the air-conditioning control process 210 may be separated from the apparatus that executes the engine control process 220, the idle stop process 230, and the permitted temperature setting process 240.
- the air conditioning casing 11 has a structure capable of realizing the inside / outside air two-layer mode.
- the air-conditioning casing 11 may be a single-layer casing that cannot realize the inside / outside air two-layer mode.
- the dual-purpose control apparatus 200 sets the value of the heat generation bulkiness Qc to be higher as the outside air introduction ratio becomes higher according to the outside air introduction ratio.
- the outside air introduction ratio alone corresponds to the state information.
- the outside air introduction ratio in the outside air mode corresponds to the first ratio, and the outside air introduction ratio lower than that corresponds to the second ratio.
- the amount of heat generated by the engine EG is increased more than usual by retarding the ignition timing from the basic timing.
- the method of increasing the heat generation amount of the engine EG more than usual is not limited to this method. For example, if the vehicle is idling, the amount of heat generated by the engine EG may be increased more than usual by increasing the throttle opening and increasing the engine speed.
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Abstract
Description
以下、第1実施形態について説明する。本実施形態に係る車載システムは、車両に搭載されている。図1に示すように、この車載システムは、エンジンEGおよび空調装置を有している。エンジンEGは、車両の走行用の駆動力を発生する内燃機関である。空調装置は、図1に示す室内空調ユニット10および冷凍サイクル30を有している。これら室内空調ユニット10および冷凍サイクル30が、空調装置を構成する。また、この空調装置と、後述する両用制御装置とが、空調システムを構成する。
TAO=Kset×Tset-Kr×Tr-Kam×Tam-Ks×Ts+C
ここで、Trは内気温センサ211で検出された車室内の温度(すなわち内気温)である。また、Tamは外気温センサ212で検出された車室外の気温(すなわち外気温)である。また、Tsは日射センサ213で検出された日射量である。また、Kset、Kr、Kam、およびKsは、制御ゲインを示す定数であり、Cは、補正用の定数である。
次に第2実施形態について説明する。本実施形態の車載システムは、第1実施形態の車載システムに対して、空調制御処理210およびエンジン制御処理220の処理内容が変更されている。
次に第3実施形態について説明する。本実施形態の車載システムは、第2実施形態の車載システムに対してエンジン制御処理220の処理内容が変更されている。
次に第4実施形態について説明する。本実施形態の車載システムは、第1、第2、第3実施形態の車載システムに対して、両用制御装置200の処理内容が変更されている。具体的には、両用制御装置200は、空調制御処理210、エンジン制御処理220に加え、図11に示すように、アイドルストップ処理230、許可温度設定処理240を実行する。両用制御装置200は、これら処理210、220、230、240を、マルチタスク処理で同時並行的に実行する。
次に第5実施形態について説明する。本実施形態の車載システムでは、第3実施形態に第4実施形態の変更を適用した実施形態に対して、更に、許可温度設定処理240の処理が変更されている。具体的には、本実施形態の許可温度設定処理240としては、第4実施形態における図12の処理に代えて、図13に示す処理が採用されている。なお、図12と図13では、同じ処理内容のステップには同じステップ番号が付されている。
上記各実施形態において、両用制御装置200が、ステップS250、S251、S305、S306を実行することで、取得部に相当する。また、両用制御装置200が、ステップS240~S285、アイドルストップ処理230、許可温度設定処理240を実行することで、比率指向制御部に相当する。また両用制御装置200が、アイドルストップ処理230を実行することで、アイドルストップ部に相当する。また、両用制御装置200が、許可温度設定処理240を実行することで、許可温度設定部に相当する。また、両用制御装置200が、S81~S87を実行することで、状態決定部に相当する。また、両用制御装置200が、S88、S89を実行することで、通知部に相当する。また、両用制御装置200が、エンジン制御処理220、アイドルストップ処理230、許可温度設定処理240を実行することで、エンジン制御部として機能する。なお、上記各実施形態におけるRAM、ROM、フラッシュメモリは、すべて非遷移的実体的記録媒体である。
本開示は上記した実施形態に限定されるものではなく、適宜変更が可能である。また、上記各実施形態は、互いに無関係なものではなく、組み合わせが明らかに不可な場合を除き、適宜組み合わせが可能である。また、上記各実施形態において、実施形態を構成する要素は、特に必須であると明示した場合および原理的に明らかに必須であると考えられる場合等を除き、必ずしも必須のものではない。また、上記各実施形態において、実施形態の構成要素の個数、数値、量、範囲等の数値が言及されている場合、特に必須であると明示した場合および原理的に明らかに特定の数に限定される場合等を除き、その特定の数に限定されるものではない。特に、ある量について複数個の値が例示されている場合、特に別記した場合および原理的に明らかに不可能な場合を除き、それら複数個の値の間の値を採用することも可能である。また、上記各実施形態において、構成要素等の形状、位置関係等に言及するときは、特に明示した場合および原理的に特定の形状、位置関係等に限定される場合等を除き、その形状、位置関係等に限定されるものではない。また、本開示は、上記各実施形態に対する以下のような変形例も許容される。なお、以下の変形例は、それぞれ独立に、上記実施形態に適用および不適用を選択できる。すなわち、以下の変形例のうち任意の組み合わせを、上記実施形態に適用することができる。
上記各実施形態において、基本タイミングはMBTに限らない。基本タイミングは、外気導入比率が十分低い場合における点火タイミングであれば、どのようなものでも構わない。
上記各実施形態においては、状態情報としては、吸込口モードの情報、外気導入比率の情報が例示されている。しかし、状態情報は、外気導入比率に影響のある空調装置の状態に基づく情報であれば、他の情報であってもよい。例えば、発熱嵩上量Qcが状態情報であってもよいし、必要発熱量Qnが状態情報であってもよい。
上記各実施形態では、両用制御装置200が空調制御処理210、エンジン制御処理220、アイドルストップ処理230、許可温度設定処理240のすべてを実行している。しかし、空調制御処理210を実行する装置と、エンジン制御処理220、アイドルストップ処理230、許可温度設定処理240を実行する装置とは、分離していてもよい。
上記各実施形態では、空調ケーシング11は内外気2層モードを実現できる構造になっている。しかし、空調ケーシング11は内外気2層モードを実現できない単層のケーシングであってもよい。この場合は、両用制御装置200は、外気導入比率に応じて、外気導入比率が高くなるほど、発熱嵩上量Qcの値を高く設定する。この場合は、外気導入比率単体が、状態情報に相当する。そして、外気モードにおける外気導入比率が第1の比率に相当し、それよりも低い外気導入比率が第2の比率に相当する。
上記実施形態では、点火タイミングを基本タイミングよりも遅角させることで、エンジンEGの発熱量を通常よりも増大させている。しかし、エンジンEGの発熱量を通常よりも増大させる方法は、この方法に限られない。例えば、車両がアイドリング中であれば、スロットル開度を通常よりも大きくしてエンジン回転数を増やすことで、エンジンEGの発熱量を通常よりも増大させてもよい。
Claims (10)
- 車両の走行用の駆動力を発生するエンジン(EG)の作動を制御するエンジン制御装置であって、
空気を空調ケーシング(11)内に導入して前記エンジンの冷却水で加熱して前記車両の車室内に吹き出す空調装置(10、30)において、前記車両の車室内および車室外から前記空調ケーシング内に導入される空気の風量に対する、前記車両の車室外から前記空調ケーシング内に導入される空気の風量の割合を、外気導入比率としたとき、前記外気導入比率に影響のある空調装置の状態に基づく状態情報を取得する取得部(S250、S251、S305、S306)と、
前記取得部が取得した前記状態情報に基づいて、前記外気導入比率が第1の比率である場合よりも、前記外気導入比率が前記第1の比率よりも低い第2の比率である場合の方が、前記エンジンの発熱量が小さくなるよう、前記エンジンの作動を制御する比率指向制御部(S240~S285、230、240)と、を備えたエンジン制御装置。 - 前記比率指向制御部は、
前記冷却水の温度が許可温度よりも高い場合に前記エンジンのアイドルストップを許可するアイドルストップ部(230)と、
前記取得部が取得した前記状態情報に基づいて、前記外気導入比率が前記第1の比率である場合よりも、前記外気導入比率が前記第2の比率である場合の方が、前記許可温度を低くする許可温度設定部(240)と、を有する請求項1に記載のエンジン制御装置。 - 前記空調装置では、吸込口モードとして、外気を第1空気通路(112)に導入して車室内に吹き出すと共に内気を前記第1空気通路とは異なる第2空気通路(113)に導入して車室内に吹き出す内外気2層モードと他のモードを切り替え可能になっており、
前記状態情報は、吸込口モードが前記内外気2層モードであるか否かを示す情報を含み、
前記比率指向制御部は、前記取得部が取得した前記状態情報に基づいて、吸込口モードが前記内外気2層モードである場合の方が、吸込口モードが前記内外気2層モードでない場合に比べ、前記エンジンの発熱量が小さくなるよう、前記エンジンの作動を制御する請求項1または2に記載のエンジン制御装置。 - 前記状態情報は、吸込口モードが前記内外気2層モードであるか否かを示す情報と、吸込口モードが前記内外気2層モードである場合における外気導入比率とを含み、
前記比率指向制御部は、前記取得部が取得した前記状態情報に基づいて、吸込口モードが前記内外気2層モードである場合、前記外気導入比率が大きくなる程、前記エンジンの発熱量が大きくなるよう、前記エンジンの作動を制御する請求項3に記載のエンジン制御装置。 - 前記比率指向制御部は、前記取得部が取得した前記状態情報に基づいて、前記エンジンの作動のオンとオフを切り替える請求項1ないし4のいずれか1つに記載のエンジン制御装置。
- 前記比率指向制御部は、車室内の温度が上昇するほど前記エンジンの発熱量が小さくなるよう、前記エンジンの作動を制御する請求項1ないし5のいずれか1つに記載のエンジン制御装置。
- 前記比率指向制御部は、車室外の温度が上昇するほど前記エンジンの発熱量が小さくなるよう、前記エンジンの作動を制御する請求項1ないし6のいずれか1つに記載のエンジン制御装置。
- 前記比率指向制御部は、前記冷却水の温度が上昇するほど前記エンジンの発熱量が小さくなるよう、前記エンジンの作動を制御する請求項1ないし7のいずれか1つに記載のエンジン制御装置。
- 車両の車室内の温度を調整する空調システムであって、
走行用の駆動力を発生するエンジン(EG)および前記エンジンを制御するエンジン制御部(220)を有する車両に搭載され、空調ケーシング(11)を有し、空気を前記空調ケーシング内に導入して前記エンジンの冷却水で加熱して前記車両の車室内に吹き出す空調装置(10、30)と、
前記空調装置の作動を制御する空調制御装置(200)と、を備え、
前記空調制御装置は、前記車両の車室内および車室外から前記空調ケーシング内に導入される空気の風量に対する、前記車両の車室外から前記空調ケーシング内に導入される空気の風量の割合を、外気導入比率としたとき、前記外気導入比率に影響のある空調装置の状態を決定する状態決定部(S81~S87)と、
前記外気導入比率が第1の比率である場合よりも、前記外気導入比率が前記第1の比率よりも低い第2の比率である場合の方が、前記エンジンの発熱量が小さくなるよう、前記状態決定部が決定した前記状態に基づく状態情報を前記エンジン制御部に通知する通知部(S88、S89)と、を有する空調システム。 - 走行用の駆動力を発生するエンジン(EG)および前記エンジンを制御するエンジン制御部(220)を有する車両に搭載され、空調ケーシング(11)を有し、空気を前記空調ケーシング内に導入して前記エンジンの冷却水で加熱して前記車両の車室内に吹き出す空調装置(10、30)を制御する空調制御装置(200)に用いるプログラムであって、
前記車両の車室内および車室外から前記空調ケーシング内に導入される空気の風量に対する、前記車両の車室外から前記空調ケーシング内に導入される空気の風量の割合を、外気導入比率としたとき、前記外気導入比率に影響のある空調装置の状態を決定する状態決定部(S81~S87)、および、
前記外気導入比率が第1の比率である場合よりも、前記外気導入比率が前記第1の比率よりも低い第2の比率である場合の方が、前記エンジンの発熱量が小さくなるよう、前記状態決定部が決定した前記状態に基づく状態情報を前記エンジン制御部に通知する通知部(S88、S89)として、前記空調制御装置を機能させるプログラム。
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- 2016-08-11 JP JP2017539783A patent/JP6489223B2/ja not_active Expired - Fee Related
- 2016-08-11 WO PCT/JP2016/073693 patent/WO2017047302A1/ja active Application Filing
- 2016-08-11 US US15/759,237 patent/US10625569B2/en not_active Expired - Fee Related
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Also Published As
Publication number | Publication date |
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CN108040476A (zh) | 2018-05-15 |
JPWO2017047302A1 (ja) | 2018-02-08 |
DE112016004180T5 (de) | 2018-06-14 |
CN108040476B (zh) | 2021-03-19 |
US10625569B2 (en) | 2020-04-21 |
US20180251009A1 (en) | 2018-09-06 |
JP6489223B2 (ja) | 2019-03-27 |
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