EP3636893A1 - Motorkühlungssystem - Google Patents

Motorkühlungssystem Download PDF

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Publication number
EP3636893A1
EP3636893A1 EP18812787.2A EP18812787A EP3636893A1 EP 3636893 A1 EP3636893 A1 EP 3636893A1 EP 18812787 A EP18812787 A EP 18812787A EP 3636893 A1 EP3636893 A1 EP 3636893A1
Authority
EP
European Patent Office
Prior art keywords
sub
refrigerant
heat exchanger
temperature
engine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP18812787.2A
Other languages
English (en)
French (fr)
Other versions
EP3636893A4 (de
Inventor
Tetsuro Ishida
Takashi Inoue
Masuji Adachi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Motors Corp
Original Assignee
Mitsubishi Motors Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Motors Corp filed Critical Mitsubishi Motors Corp
Publication of EP3636893A4 publication Critical patent/EP3636893A4/de
Publication of EP3636893A1 publication Critical patent/EP3636893A1/de
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/28—Layout, e.g. schematics with liquid-cooled heat exchangers
    • 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
    • F01P3/00—Liquid cooling
    • F01P3/12—Arrangements for cooling other engine or machine parts
    • 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
    • F01P3/00—Liquid cooling
    • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
    • 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
    • F01P3/00—Liquid cooling
    • F01P3/20—Cooling circuits not specific to a single part of engine or machine
    • 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
    • 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
    • F01P7/165—Controlling of coolant flow the coolant being liquid by thermostatic control characterised by systems with two or more loops
    • 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
    • F01P2037/00—Controlling
    • F01P2037/02—Controlling starting
    • 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
    • F01P2060/02—Intercooler
    • 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
    • F01P2060/04—Lubricant cooler
    • 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
    • F01P2060/04—Lubricant cooler
    • F01P2060/045—Lubricant cooler for transmissions
    • 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
    • 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
    • F01P2060/16—Outlet manifold

Definitions

  • the present invention relates to an engine cooling system including a liquid-cooling device for cooling a cooled portion of an engine with a refrigerant.
  • Vehicles on which an engine such as a gasoline engine or a diesel engine is mounted include a water-cooling device for cooling the engine body around the cylinders by circulating cooling water as a refrigerant.
  • the water-cooling device for cooling the engine body includes a pump device called a water pump which supplies cooling water to a space, such as a water jacket, in the cylinder block, thereby preventing the temperature of the engine body from rising excessively due to the combustion of fuel in the cylinders.
  • the cooling water is cooled by a refrigerant-cooling heat exchanger such as a radiator, and circulates to the engine body through the pump device again.
  • Such a water-cooling device switches cooling water flow paths according to the temperature of the cooling water to accelerate the warm-up of the engine (e.g., see the below-identified Patent Document 1).
  • Patent document 1 Japanese Unexamined Patent Application Publication No. 2015-175296
  • Patent Document 1 discloses an exhaust gas recirculation device for returning a portion of exhaust gas into the intake air as returned exhaust gas.
  • the exhaust gas recirculation device includes a returned exhaust gas cooler of the water-cooling type for cooling the returned exhaust gas with the same cooling water as used to cool the engine body.
  • the engine cooling system of Patent Document 1 further includes a sub-radiator disposed forward of, and separately from, a radiator for decreasing the temperature of cooling water, and comprising a heat exchanger for cooling the refrigerant.
  • the engine cooling system of Patent Document 1 is controlled as follows: (i) while the temperature of cooling water in an area located downstream of the returned exhaust gas cooler is less than a (low) threshold value, a thermostat is closed to prevent cooling water from circulating to the engine; (ii) when the above temperature is equal to or higher than the threshold value, the thermostat is opened to circulate cooling water to the engine while using only the radiator to cool the cooling water; and (iii) when the above temperature further rises, only the sub-radiator disposed forward of the radiator is used with the thermostat opened.
  • the present invention provides an engine cooling system comprising: a pump device configured to feed a refrigerant; a cooled portion of an engine configured to be cooled by heat exchange with the refrigerant; a radiator configured to cool the refrigerant; a refrigerant circulation circuit through which the pump device, the cooled portion, and the radiator are connected together, and in which the refrigerant circulates; at least one sub-refrigerant circulation circuit to which the refrigerant is supplied, and which includes a sub-heat exchanger lower in heat exchange performance than the radiator; and a refrigerant temperature obtaining means for obtaining information correlated to a temperature of the refrigerant at the cooled portion, wherein the engine cooling system is configured: such that, during warm-up of the engine, if the temperature of the refrigerant at the cooled portion is less than a first predetermined value, supply of the refrigerant to the radiator and the sub-heat exchanger is reduced, and when the temperature of the refriger
  • an amount of the refrigerant flowing out of the sub-heat exchanger per unit time may be smaller than the amount of the refrigerant flowing out of the radiator per unit time.
  • a temperature of the refrigerant that has passed through the sub-heat exchanger, and has been cooled by heat dissipation may be higher than a temperature of the refrigerant that has passed through the radiator.
  • the above engine cooling system may be configured such that, during warm-up of the engine, if the temperature of the refrigerant at the cooled portion is less than the first predetermined value, the supply of the refrigerant to the radiator and the sub-heat exchanger is stopped, and when the temperature of the refrigerant at the cooled portion rises to the first predetermined value or more, supply of the refrigerant to the sub-heat exchanger is started.
  • the at least one sub-refrigerant circulation circuit may comprise first and second sub-refrigerant circulation circuits.
  • the sub-heat exchanger of the first sub-refrigerant circulation circuit may comprise a first type of sub-heat exchanger configured to increase a temperature of the refrigerant that passes therethrough.
  • the sub-heat exchanger of the second sub-refrigerant circulation circuit may comprise a second type of sub-heat exchanger configured to decrease a temperature of the refrigerant that passes therethrough.
  • the engine cooling system may be configured such that, if the temperature of the refrigerant at the cooled portion is less than a third predetermined value between the first predetermined value and the second predetermined value, the refrigerant is supplied to the first type of sub-heat exchanger, and is not supplied to the second type of sub-heat exchanger, and if the temperature of the refrigerant at the cooled portion is equal to or higher than the third predetermined value, the refrigerant is supplied to the second type of sub-heat exchanger.
  • the at least one sub-refrigerant circulation circuit may comprise first and second sub-refrigerant circulation circuits.
  • the sub-heat exchanger of the first sub-refrigerant circulation circuit may comprise a small capacity sub-heat exchanger configured to decrease a temperature of the refrigerant that passes therethrough.
  • the sub-heat exchanger of the second sub-refrigerant circulation circuit may comprise a large capacity sub-heat exchanger configured to decrease a temperature of the refrigerant that passes therethrough and higher in cooling performance than the small capacity sub-heat exchanger.
  • the engine cooling system may be configured such that if the temperature of the refrigerant at the cooled portion is less than a fourth predetermined value between the first predetermined value and the second predetermined value, the refrigerant is supplied to the small capacity sub-heat exchanger, and is not supplied to the large capacity sub-heat exchanger, and if the temperature of the refrigerant at the cooled portion is equal to or higher than the fourth predetermined value, the refrigerant is supplied to the large capacity sub-heat exchanger.
  • the engine may include an exhaust gas recirculation device configured to return a portion of exhaust gas as returned exhaust gas into intake air
  • the exhaust gas recirculation device may include a returned exhaust gas cooler of a liquid-cooling type configured to cool the returned exhaust gas with the refrigerant
  • the at least one sub-refrigerant circulation circuit may comprise a plurality of sub-refrigerant circulation circuits
  • the sub-heat exchanger of one of the plurality of sub-refrigerant circulation circuits may comprise the returned exhaust gas cooler.
  • the at least one sub-refrigerant circulation circuit may comprise a plurality of sub-refrigerant circulation circuits, and the sub-heat exchanger of one of the plurality of sub-refrigerant circulation circuits may comprise a heater core of an air conditioner of a vehicle on which the engine is mounted.
  • the at least one sub-refrigerant circulation circuit may comprise a single sub-refrigerant circulation circuit, or a plurality of sub-refrigerant circulation circuits, and the sub-heat exchanger of the single sub-refrigerant circulation circuit, or each of the sub-heat exchanges of at least some of the plurality of sub-refrigerant circulation circuits may comprise one of: a liquid-cooling engine oil cooler configured to cool lubricating oil for the engine with the refrigerant; a liquid-cooling intercooler configured to cool intake air with the refrigerant; and a liquid-cooling transmission oil cooler configured to cool, with the refrigerant, lubricating oil for a transmission to which a driving force of the engine is transmitted.
  • a liquid-cooling engine oil cooler configured to cool lubricating oil for the engine with the refrigerant
  • a liquid-cooling intercooler configured to cool intake air with the refrigerant
  • a liquid-cooling transmission oil cooler configured to cool
  • the engine cooling system includes a sub-heat exchanger or exchangers to which the same refrigerant as used in the radiator is supplied, and which is configured to increase the temperature of the refrigerant or lower in cooling performance than the radiator, and this engine cooling system is configured such that when the temperature of the engine needs to be increased quickly e.g., during the warm-up of the engine, before supplying the refrigerant from the radiator to the engine, the refrigerant which has passed through the sub-heat exchanger(s) is supplied to the engine.
  • the engine cooling system includes a liquid-cooling device for cooling, by heat exchange with a refrigerant, the body of an engine 1 which comprises a cylinder block including a cylinder in which a piston 2 is received to define a combustion chamber 3 therein; and members around the cylinder block. Therefore, the above-defined body of the engine 1, designated by numeral 10, is hereinafter referred to as the "cooled portion".
  • An intake passage 4 and an exhaust passage 5 are connected to the combustion chamber 3 so that air is sucked into the combustion chamber 3 through the intake passage 4, and exhaust gas is discharged from the combustion chamber 3 through the exhaust passage 5.
  • the openings of the intake passage 4 and the exhaust passage 5 communicating with the combustion chamber 3 are opened and closed by an intake valve 6 and an exhaust valve 7, respectively.
  • Numeral 8 in the figures designates an ignition device for generating an ignition spark in the combustion chamber 3.
  • the engine 1 is a gasoline engine in the embodiment, but may be a diesel engine, in which case no ignition device 8 is used.
  • the liquid-cooling device of the embodiment is a water-cooling device which uses water (hereinafter referred to as "cooling water") as the refrigerant.
  • the water-cooling device includes a pump device 11 for feeding cooling water (known as a “water pump”); and a radiator 20 comprising a cooling core for cooling cooling water.
  • the pump device 11, the cooled portion 10 and the radiator 20 are annularly connected together through a refrigerant passage, thereby constituting a refrigerant circulation circuit 21 in which cooling water circulates.
  • the pump device 11 is driven by an electric motor or the engine to feed cooling water.
  • the radiator 20 functions to reduce the temperature of cooling water by heat exchange with, e.g., air.
  • the pump device 11 supplies cooling water to a space, such as a water jacket, provided in the cylinder block of the engine 1, thereby preventing the temperature of the engine 1 from rising excessively due to the combustion of fuel in the combustion chamber 3.
  • the cooling water cooled by the radiator 20 circulates and returns to the body of the engine 1 through the pump device 11.
  • the refrigerant circulation circuit 21 includes a valve 22 so that, by opening the valve 22 cooling water can circulate in the refrigerant circulation circuit 21, and by closing the valve 22, cooling water cannot circulate in the refrigerant circulation circuit 21.
  • the water-cooling device includes a bypass circulation passage 13 branching off from an intermediate portion of the refrigerant circulation circuit 21. Part of the cooling water from the pump device 11 is circulated at all times through the bypass circulation passage 13 to the cooled portion 10, without passing through any heat exchanger.
  • a water temperature sensor 12 as a refrigerant temperature obtaining means is mounted to the bypass circulation passage 13 so as to obtain information correlated to the refrigerant temperature (this temperature is hereinafter referred to as the "water temperature" because the refrigerant is cooling water in the embodiment) at the cooled portion 10.
  • the valve 22 is opened so that cooling water is fed, under the driving force of the pump device 11, to the cooled portion 10 of the engine 1 while circulating in the refrigerant circulation circuit 21.
  • the valve 22 is closed so that cooling water is not fed or supplied to the cooled portion 10 of the engine 1, thereby enabling the engine 1 to warm up quickly.
  • the water-cooling device is controlled by an electronic control unit 60 mounted on the vehicle on which the above-described engine 1 is mounted. More specifically, the electronic control unit 60 controls the operation of the engine 1, and also controls the water-cooling device based on the temperature conditions of the cooled portion 10, the water temperature at the cooled portion 10, various operation states, etc.
  • the water-cooling device includes three sub-refrigerant circulation circuits 31, 41 and 51 to which the same refrigerant (cooling water) as used in the refrigerant circulation circuit 21 is supplied, and which include, respectively, three sub-heat exchangers 30, 40 and 50 each configured to increase or decrease the refrigerant temperature (water temperature). All of the sub-heat exchangers 30, 40 and 50 are lower in refrigerant cooling performance, i.e., in heat exchange performance with the refrigerant, than the radiator 20.
  • the sub -heat exchangers 30, 40 and 50 are designed such that the amount of refrigerant flowing out of each sub-heat exchanger 30, 40, 50 per unit time is smaller than the amount of refrigerant flowing out of the radiator 20 per unit time, and such that, if cooling water of the same temperature flows into the sub-heat exchangers 30, 40 and 50, and the radiator 20, the temperature of the cooling water leaving each sub-heat exchanger 30, 40, 50 after being cooled by heat dissipation is higher than the temperature of the cooling water leaving the radiator 20.
  • the sub-heat exchanger 30 is constituted by a liquid-cooling engine oil cooler that cools lubricating oil of the engine 1 with the same cooling water as used in the refrigerant circulation circuit 21.
  • the sub-heat exchanger 30 is hereinafter referred to as the engine oil cooler 30.
  • the sub-refrigerant circulation circuit 31 including the engine oil cooler 30 has a valve 32 so that, by opening the valve 32, cooling water can circulate in the sub-refrigerant circulation circuit 31, and by closing the valve 32, cooling water cannot circulate in the sub-refrigerant circulation circuit 31.
  • the sub-refrigerant circulation circuit 31 including the engine oil cooler 30 may merge with the refrigerant circulation circuit 21 at positions downstream of the radiator 20 and upstream of the valve 22, respectively, so the valve 22 of the refrigerant circulation circuit 21 can control the circulation of cooling water in the sub-refrigerant circulation circuit 31, too. In this arrangement, cooling water is supplied simultaneously to both the radiator 20 and the engine oil cooler 30.
  • the engine 1 includes an exhaust gas recirculation device 15 that returns a portion of the exhaust gas discharged from the combustion chamber 3 into the intake air as returned exhaust gas to introduce the thus-returned exhaust gas into the combustion chamber 3.
  • the exhaust gas recirculation device 15 includes an exhaust gas return passage 16 that connects the intake passage 4 to the exhaust passage 5; an exhaust return valve 17 configured to open and close the exhaust gas return passage 16; and a throttle valve (not shown) which is mounted in the intake passage 4 at its portion upstream of the position where the exhaust gas return passage 16 merges with the intake passage 4, and which is configured to create a negative pressure in the intake passage 4.
  • the exhaust gas recirculation device 15 further includes a returned exhaust gas cooler 40 of the liquid-cooling type mounted to an intermediate portion of the exhaust gas return passage 16.
  • the sub-heat exchanger 40 is constituted by this returned exhaust gas cooler of the exhaust gas recirculation device 15.
  • the sub-heat exchanger 40 is hereinafter referred to as the returned exhaust gas cooler 40.
  • the returned exhaust gas cooler 40 cools returned exhaust gas passing through its core connected to the exhaust gas return passage 16, by use of cooling water circulating through the core of the cooler 40.
  • the cooling water supplied to the returned exhaust gas cooler is the same cooling water as used in the refrigerant circulation circuit 21 including the radiator 20.
  • the sub-refrigerant circulation circuit 41 including the returned exhaust gas cooler 40 has a valve 42 so that, by opening the valve 42, cooling water can circulate in the sub-refrigerant circulation circuit 41, and by closing the valve 42, cooling water cannot circulate in the sub-refrigerant circulation circuit 41.
  • the vehicle on which the above-described engine 1 is mounted includes an air conditioner 53.
  • the air conditioner 53 includes a heater core 50 for generating a flow of warm air in the passenger compartment.
  • the sub-heat exchanger 50 is constituted by this heater core 50 of the air conditioner 53.
  • the sub-heat exchanger 50 is hereinafter referred to as the heater core 50.
  • An electric fan for moving air is provided adjacent to the heater core 50.
  • the same cooling water as used in the refrigerant circulation circuit 21 including the radiator 20 is supplied into the heater core 50. By rotating the air moving fan, heat of the cooling water is transferred to and heats air to be blown into the passenger compartment, and the heated air blown into the passenger compartment increases the temperature of the passenger compartment.
  • the sub-refrigerant circulation circuit 51 including the heater core 50 branches off from the sub-refrigerant circulation circuit 41 at a position downstream of the returned exhaust gas cooler 40; extends through the heater core 50; merges with the sub-refrigerant circulation circuit 41 at a position downstream of the valve 42; and returns to the pump device 11.
  • the sub-refrigerant circulation circuit 51 has a valve 52 at its position downstream of the heater core 50 so that, by opening the valve 52, cooling water can circulate in the sub-refrigerant circulation circuit 51, and by closing the valve 52, cooling water cannot circulate in the sub-refrigerant circulation circuit 51.
  • the sub-refrigerant circulation circuit 51 including the heater core 50 may branch off from the sub-refrigerant circulation circuit 41 at a position upstream of the returned exhaust gas cooler 40. Further alternatively, the sub-refrigerant circulation circuit 51 may extend directly from the cooled portion 10 as with the sub-refrigerant circulation circuits 31 and 41.
  • the electronic control unit 60 controls the air conditioner 53, and the valves 32, 42 and 52 of the sub-refrigerant circulation circuits 31, 41 and 51.
  • the valves 22, 32, 42 and 52 are rotary valves, which each includes a rotating member such as a rotor, and controls the amount of cooling water flowing therethrough by rotating the rotating member. Specifically, by rotating the rotating member of each valve 22, 32, 42, 52, the valve is opened and cooling water flows therethrough at a rate corresponding to the rotation speed of the rotating member. By stopping the rotating member of each valve 22, 32, 42, 52, the valve is closed and the flow of cooling water stops.
  • valve devices having a different structure to control the amount of cooling water flowing therethrough may be used as the valves 22, 32, 42 and 52.
  • the air conditioner 53 including the heater core 50 can be manually controlled based on an input signal when a driver turns on a passenger compartment air conditioning switch 61 and/or a passenger compartment fan switch 62 which are both mounted in the passenger compartment.
  • the air conditioner 53 can also be automatically controlled based on information from a passenger compartment temperature detecting means 63 for detecting the temperature of the passenger compartment, and/or an outside air temperature detecting means 64 for detecting the temperature outside the vehicle.
  • an air flow is created based on an ON signal from the passenger compartment fan switch 62, and stops based on an OFF signal from the switch 62 or when the ON signal stops. While the ON signal is being received, it is possible to adjust the strength of the air flow.
  • an ON signal is received from the passenger compartment air conditioning switch 61
  • air passes through the core, so that the air flow introduced into the passenger compartment changes from a normal-temperature air flow to a high-temperature air flow thereby heating the passenger compartment.
  • an OFF signal is received from the passenger compartment air conditioning switch 61 or when the ON signal from the switch 61 stops, the air flow changes from a warm air flow to a normal-temperature air flow.
  • the temperature and strength of an air flow, and whether or not to create an air flow are automatically controlled such that the temperature of the passenger compartment approaches the preset temperature (target temperature).
  • the preset temperature can be also automatically set based upon the temperature outside the vehicle.
  • cooling water is supplied to the heater core at all times.
  • determination may be made that it is not necessary to heat the passenger compartment when the temperature detected by an intake air temperature sensor 9, the outside air temperature detecting means 64, or the passenger compartment temperature detecting means 63 is equal to or higher than a predetermined temperature, when the passenger compartment air conditioning switch 61 is off, or when the passenger compartment fan switch 62 is off.
  • the valve 22 of the refrigerant circulation circuit 21 including the radiator 20 is closed to stop the supply of cooling water in the refrigerant circulation circuit 21 to the cooled portion 10 of the engine 1.
  • the amount of cooling water supplied to the cooled portion 10 may be reduced.
  • cooling water fed from the pump device 11 circulates in the bypass circulation passage 13 without passing through any heat exchangers, including the radiator 20, and the three sub-heat exchangers, namely the engine oil cooler 30, the returned exhaust gas cooler 40, and the heater core 50.
  • the valve 22 of the refrigerant circulation circuit 21 may have a thermostat function such that it opens only if the water temperature rises to the first predetermined value T1 or more.
  • the returned exhaust gas cooler 40 which is the sub-heat exchanger of the sub-refrigerant circulation circuit 41, is a heat exchanger of the type that increases the water temperature, and is hereinafter referred to as the "first type" of sub-heat exchanger H.
  • the engine oil cooler 30, which is the sub-heat exchanger of the sub-refrigerant circulation circuit 31, and the heater core 50, which is the sub-heat exchanger of the sub-refrigerant circulation circuit 51, are heat exchangers of the type that decreases the water temperature, and are hereinafter referred to as the "second type" of sub-heat exchangers C.
  • cooling water is supplied to the sub-heat exchangers. Specifically, if the water temperature is less than a third predetermined value T3 between the first predetermined value T1 and the second predetermined value T2 (see range b in Fig. 3 ), cooling water is supplied to the first type of sub-heat exchanger H, and is not supplied to the second type of sub-heat exchangers C.
  • the first type of sub-heat exchanger H is a heat radiator. That is, cooling water supplied to the first type of sub-heat exchanger H receives the heat of returned exhaust gas, and thus is heated. Therefore, by supplying, to the cooled portion 10, cooling water that has been somewhat heated after passing through the first type of sub-heat exchanger H, before starting to supply cooling water that has passed through the second type of sub-heat exchangers C, it is possible to prevent low-temperature cooling water from rushing into the engine 1 in a very short period of time, so that the engine temperature rises sufficiently quickly.
  • the second type of sub-heat exchangers C which are configured to decrease the temperature of cooling water, comprise a small capacity sub-heat exchanger Cs, and a large capacity sub-heat exchanger C L higher in cooling performance than the small capacity sub-heat exchanger Cs.
  • Cooling water is supplied to the second type of sub-heat exchangers C in the following manner. While the water temperature is less than a fourth predetermined value T4 between the first predetermined value T1 and the second predetermined value T2 (see range c in Fig. 3 ), cooling water is supplied to only the small capacity sub-heat exchanger C S , and is not supplied to the large capacity sub-heat exchanger C L . As a result thereof, relatively high-temperature cooling water that has passed through the small capacity (low cooling performance) sub-heat exchanger C S is supplied to the engine 1 before relatively low-temperature cooling water that has passed through the large capacity (high cooling performance) sub-heat exchanger C L is supplied to the engine 1.
  • the fourth predetermined value T4 is set between the second predetermined value T2 and the third predetermined value T3, the latter being the boundary based on which it is determined whether cooling water is to be supplied to both the first type of sub-heat exchanger H and the second type of sub-heat exchanger(s) C, or to only the first type of sub-heat exchanger H.
  • the third predetermined value T3 is not set, and the fourth predetermined value T4 is set between the first predetermined value T1 and the second predetermined value T2.
  • the supply of cooling water (refrigerant) to the large capacity sub-heat exchanger CL is started. Since the water temperature has risen to the forth predetermined value T4 or more at this time, even though relatively low-temperature cooling water that has passed through the large capacity sub-heat exchanger C L is supplied to the engine, this would not prevent the engine temperature from rising sufficiently quickly, as long as the water temperature is not extremely low, i.e., as low as the temperature of cooling water in the refrigerant circulation circuit 21 that has passed through the radiator 20.
  • the small capacity sub-heat exchanger C S comprises the engine oil cooler 30 and the large capacity sub-heat exchanger C L comprises the heater core 50.
  • the valve 32 is opened, and to supply cooling water to the heater core 50, the valve 52 is opened.
  • the graph of Fig. 2 shows the cylinder (liner) temperature when, after the engine starts to warm up, cooling water is supplied only to the returned exhaust gas cooler 40 while stopping the supply of cooling water to the radiator 20.
  • the line indicated by X in Fig. 2 shows the behavior of the cylinder temperature when only the valve 42 is opened with the other valves closed.
  • the line indicated by X + Y in the figure shows the cylinder temperature behavior when the valves 42 and 52 are opened with the other valve closed.
  • the line indicated by X + Y + Z shows the cylinder temperature behavior when all of the valves 42, 52 and 22 are opened
  • the line indicated by X + Y + Z represents a situation in which, since cooling water that has passed through the radiator 20 is supplied to the engine, the cylinder temperature rises slowly.
  • the line indicated by X + Y shows a situation in which, since cooling water is supplied to both the returned exhaust gas cooler 40 and the heater core 50, but is not supplied to the radiator 20, the cylinder temperature rises faster than in the situation shown by line indicated by X + Y + Z.
  • the line indicated by X show a situation in which, since cooling water is supplied to only the returned exhaust gas cooler 40, and not to the heater core 50 and the radiator 20, the cylinder temperature rises fastest.
  • the amount of temporary decrease in cylinder temperature when the supply of cooling water to the engine 1 is started i.e., the amount of undershoot at the time indicated by symbol a in the figure.
  • One way to quickly increase the cylinder liner temperature during warm-up would be to minimize or stop the flow of refrigerant in the engine during warm-up, thereby intentionally creating a non-uniform temperature distribution in the engine, i.e., intentionally preventing heat transfer from high-temperature to low-temperature engine portions.
  • the flow of low-temperature cooling water into the engine from the refrigerant circulation circuit including the radiator is automatically controlled by a thermostat, and also the refrigerant circulation circuit including the radiator has a large capacity enough to cool the engine, which means that this circuit is high in flow rate and large in the amount of heat dissipation. Therefore, when the thermostat is opened, even if the degree of opening is very small, a relatively large amount of low-temperature cooling water flows into the engine in a short period of time, so that the engine, which has been heated quickly up to this point, is temporarily cooled excessively. It is considered that this excessive cooling is related to, e.g., the amount of cooling water flowing into the engine per unit time, and the temperature of cooling water that has been cooled by heat dissipation in the heat exchanger.
  • cooling water is first supplied to at least one sub-heat exchanger having lower cooling performance (i.e., lower flow rate and smaller amount of heat dissipation) than the radiator 20 of the refrigerant circulation circuit 21, and/or to a sub-heat exchanger configured to increase, instead of decrease, the temperature of cooling water passing therethrough, until the water temperature rises to a sufficient level (second predetermined value T2), which means that the engine has warmed up sufficiently. Cooling water is then suppled to the refrigerant circulation circuit 21 including the radiator 20.
  • the engine cooling system includes two heat exchangers different in cooling performance from each other, and during the warm-up of the engine, the heat exchanger lower in cooling performance is used first.
  • the engine cooling system includes a water temperature decreasing heat exchanger and a water temperature increasing heat exchanger, and during the warm-up of the engine, the water temperature increasing heat exchanger is used first. In either arrangement, it is possible to prevent an excessive decrease (undershoot) in temperature of the engine cylinder.
  • the sub-refrigerant circulation circuit(s) including the sub-heat exchanger(s) configured to decrease the water temperature needs to be lower in cooling performance than the refrigerant circulation circuit 21 including the radiator 20 as a main cooling unit.
  • a sub-refrigerant circulation circuit is lower in cooling performance than the refrigerant circulation circuit 21 if, for example, the amount of cooling water flowing out of the sub-heat exchanger per unit time, namely the amount of cooling water flowing into the engine 1, is smaller than the amount of cooling water flowing out of the circuit 21.
  • the temperature of cooling water (refrigerant) which has passed through the sub-heat exchanger(s) and is cooled is preferably higher than the temperature of cooling water (refrigerant) which has passed through the radiator 20 as a main cooling unit.
  • the piping in the heater core 50 which is used as one of the sub-heat exchangers in the embodiment, is smaller in diameter than the piping in the core of the radiator 20, and also the volume of the entire heater core 50 is smaller than that of the radiator 20, the water flow resistance of the heater core 50 tends to be larger than that of the radiator 20, and the amount of heat dissipation tends to be smaller than that of the radiator 20.
  • the piping of the sub-refrigerant circulation circuit 51 including the heater core 50 may be longer than the piping of the refrigerant circulation circuit 21 including the radiator 20.
  • the longer the piping of a circuit the larger the water flow resistance of the circuit, the cooling performance of the sub-refrigerant circulation circuit 51 would never exceed that of the refrigerant circulation circuit 21.
  • the cooling capacities of the individual sub-refrigerant circulation circuits are preferably determined so as to differ from each other.
  • the engine oil cooler 30, the returned exhaust gas cooler 40, and the heater core 50 are used as sub-heat exchangers.
  • the returned exhaust gas cooler 40 is used as a first type of sub-heat exchanger H (configured to increase the temperature of a refrigerant), and the engine oil cooler 30 and the heater core 50 are used as second type of sub-heat exchangers C (configured to decrease the temperature of a refrigerant).
  • sub-heat exchangers which can be used in the engine cooling system of the present invention are not limited to those disclosed in the embodiment, and various heat exchanges may be used.
  • the engine cooling system may include a single first type of sub-heat exchanger H while not including a second type of sub-heat exchanger C; may include a plurality of first type of sub-heat exchangers H while not including a second type of sub-heat exchanger C; may include a single second type of sub-heat exchanger C while not including a first type of sub-heat exchanger H; or may include a plurality of second type of sub-heat exchangers C while not including a first type of sub-heat exchanger H.
  • sub-heat exchangers which can be used in the engine cooling system include, for example, a liquid-cooling intercooler configured to cool intake air with the same refrigerant as used in the refrigerant circulation circuit 21 including the radiator 20, or a liquid-cooling transmission oil cooler configured to cool, with the same refrigerant as used in the refrigerant circulation circuit 21, the lubricating oil of a transmission to which the driving force of the engine is transmitted.
  • a liquid-cooling intercooler configured to cool intake air with the same refrigerant as used in the refrigerant circulation circuit 21 including the radiator 20, or a liquid-cooling transmission oil cooler configured to cool, with the same refrigerant as used in the refrigerant circulation circuit 21, the lubricating oil of a transmission to which the driving force of the engine is transmitted.
  • a liquid-cooling intercooler configured to cool intake air with the same refrigerant as used in the refrigerant circulation circuit 21 including the radiator 20, or a liquid-cooling transmission oil cooler configured to cool, with
  • the engine cooling system of the present invention includes, as a liquid-cooling device, a water-cooling device in which cooling water is used as a refrigerant
  • the engine cooling system may include a cooling device in which a different refrigerant is used, such as an oil-cooling device in which lubricating oil is used as a refrigerant.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
EP18812787.2A 2017-06-05 2018-02-21 Motorkühlungssystem Withdrawn EP3636893A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017110833 2017-06-05
PCT/JP2018/006237 WO2018225305A1 (ja) 2017-06-05 2018-02-21 エンジン冷却システム

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EP3636893A1 true EP3636893A1 (de) 2020-04-15

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Publication number Priority date Publication date Assignee Title
FR2804722B1 (fr) * 2000-02-03 2002-03-08 Peugeot Citroen Automobiles Sa Dispositif de refroidissement d'un moteur de vehicule automobile
GB2475079B (en) * 2009-11-05 2015-02-18 Ford Global Tech Llc Cooling systems
JP2013087761A (ja) * 2011-10-21 2013-05-13 Denso Corp エンジン冷却水循環システム
JP5742702B2 (ja) * 2011-12-19 2015-07-01 トヨタ自動車株式会社 冷却装置の制御装置
WO2014074430A1 (en) * 2012-11-07 2014-05-15 Borgwarner Inc. Thermal system cold start layout circuit with egr
WO2014192747A1 (ja) * 2013-05-28 2014-12-04 日産自動車株式会社 エンジンの制御装置及び制御方法
JP2015175296A (ja) 2014-03-14 2015-10-05 いすゞ自動車株式会社 エンジン冷却システム
JP6265171B2 (ja) * 2015-06-09 2018-01-24 トヨタ自動車株式会社 車両の熱交換装置

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