US10385758B2 - Cooling system for internal combustion engine, and control method thereof - Google Patents
Cooling system for internal combustion engine, and control method thereof Download PDFInfo
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- US10385758B2 US10385758B2 US15/563,654 US201615563654A US10385758B2 US 10385758 B2 US10385758 B2 US 10385758B2 US 201615563654 A US201615563654 A US 201615563654A US 10385758 B2 US10385758 B2 US 10385758B2
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- cooling water
- line
- channel switching
- flow channel
- switching valve
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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
- F01P3/00—Liquid cooling
- F01P3/20—Cooling circuits not specific to a single part of engine or machine
-
- 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
- B60H1/08—Heating, cooling or ventilating [HVAC] devices the heat being derived from the propulsion plant from cooling liquid of the plant from other radiator than main radiator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M5/00—Heating, cooling, or controlling temperature of lubricant; Lubrication means facilitating engine starting
- F01M5/02—Conditioning lubricant for aiding engine starting, e.g. heating
- F01M5/021—Conditioning lubricant for aiding engine starting, e.g. heating by heating
-
- 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
- F01P5/00—Pumping cooling-air or liquid coolants
- F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
- F01P5/12—Pump-driving arrangements
-
- 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
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0412—Cooling or heating; Control of temperature
- F16H57/0413—Controlled cooling or heating of lubricant; Temperature control therefor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/0467—Elements of gearings to be lubricated, cooled or heated
- F16H57/0475—Engine and gearing, i.e. joint lubrication or cooling or heating thereof
-
- 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
- F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
Definitions
- the present invention relates to a cooling system for an internal combustion engine, and in particular, relates to a cooling system for an internal combustion engine capable of accelerating temperature increase of cooling water, and relates to a control method thereof.
- a conventional cooling system of this type includes two cooling water channels and a valve for adjusting cooling water flow rates through these two cooling water channels.
- the other one of the cooling water channels which is provided separately from the above cooling water channel, includes a bypass passage.
- the valve is disposed at a point where the cooling water having passed the oil heat exchanger meets the cooling water having passed through the bypass passage.
- Such a conventional cooling system measures at least either of the vehicle interior temperature and the vehicle exterior temperature as well as the temperature of cooling water discharged from the engine, and controls the actuation of the valve so as to switch between these two cooling water channels when these temperature measurements satisfy their respective predetermined conditions (see Patent Document 1, for example).
- Patent Document 1 JP 4994546 B
- the present invention has been made to provide a cooling system for an internal combustion engine capable of accelerating temperature increase of cooling water, and a control method thereof.
- a cooling system for an internal combustion engine comprises: a flow channel switching valve for switching between a plurality of cooling water channels at least including a heater line for air heating, a block line for cooling an engine block, and a transmission line for an oil warmer of a transmission so as to sequentially open at least one of the plurality of cooling water channels in accordance with a warm-up state of the internal combustion engine; and a control device for controlling opening and closing of the flow channel switching valve so as to restrict a cooling water distribution rate of the heater line.
- the cooling system includes a flow channel switching valve for switching between a plurality of cooling water channels at least including a heater line for air heating, a block line for cooling an engine block, and a transmission line for an oil warmer of a transmission so as to sequentially open at least one of the plurality of cooling water channels in accordance with a warm-up state of the internal combustion engine; and a control device
- the control device is caused to control opening and closing of the flow channel switching valve so as to control cooling water distribution rates of the plurality of cooling water channels.
- the control device controls the opening and closing of the flow channel switching valve so as to restrict a cooling water distribution rate of the heater line.
- FIG. 1 is a schematic configuration diagram illustrating a cooling system for an internal combustion engine according to an embodiment of the present invention.
- FIG. 2 is a flowchart illustrating how to determine operation conditions of the cooling system.
- FIG. 3 illustrates the operation of a flow channel switching valve of the cooling system.
- FIG. 4 illustrates a cooling water circulation route immediately after engine start.
- FIG. 5 illustrates a cooling water circulation route when a heater line opens.
- FIG. 6 illustrates a cooling water circulation route when a block line opens.
- FIG. 7 illustrates a cooling water circulation route when a transmission line opens.
- FIG. 8 illustrates a cooling water circulation route when a radiator line opens.
- FIG. 9 illustrates how the cooling water temperature decreases when the transmission line opens.
- FIGS. 10A and 10B illustrate a cooling system according to a first embodiment of the present invention: FIG. 10A depicts the relationships between the rotor angle of the flow channel switching valve and the opening ratios of inlet ports; and FIG. 10B depicts changes in the cooling water flow rates through the cooling water channels.
- FIG. 11 is a graph from an experiment for confirming the effects of the first embodiment.
- FIG. 12 is a flowchart illustrating how to set base values for the rotor angle of the flow channel switching valve and for the rotation speed or flow rate of an electric water pump in a cooling system according to a second embodiment of the present invention.
- FIG. 13 is a flowchart illustrating how to calculate the rotation speed or flow rate of the electric water pump in the second embodiment.
- FIG. 14 is a template providing the correspondence between the rotor angle of the flow channel switching valve and a correction variable for the discharge rate of the electric water pump in the second embodiment.
- FIG. 15 is a flowchart illustrating how to correct the flow rate through the heater line based on temperature information from temperature sensors installed at different locations in a vehicle in a cooling system according to a third embodiment of the present invention.
- FIGS. 16A to 16D are templates each providing the correspondence between the output from one of the temperature sensors and a correction variable for the rotor angle.
- FIGS. 17A and 17B are templates each providing the correspondence between another environmental information and a correction variable for the rotor angle: FIG. 17A provides the correspondence between the opening degree of an air-mix door and the correction variable; and FIG. 17B provides the correspondence between the air volume of a blower fan and the correction variable.
- FIG. 1 is a schematic configuration diagram illustrating a cooling system according to an embodiment of the present invention.
- the cooling system for cooling an internal combustion engine 1 includes first to fourth cooling water channels 2 to 5 , a flow channel switching valve 7 , a water pump (ELWP) 8 , a radiator 9 , and an electronic control device 10 .
- EWP water pump
- Internal combustion engine 1 which is mounted on a vehicle, includes a cylinder head 11 and a cylinder block 12 .
- a transmission 13 such as a continuously variable transmission (CVT), an example of a powertrain, is coupled to the output shaft of internal combustion engine 1 .
- the output of transmission 13 is transmitted to drive wheels (not illustrated in the drawings), thereby causing the vehicle to travel.
- CVT continuously variable transmission
- Head cooling water passage 14 for cooling cylinder head 11 includes a cooling water inlet 15 and a cooling water outlet 16 .
- Cooling water inlet 15 opens at one end of cylinder head 11 in the cylinder arrangement direction.
- Cooling water outlet 16 opens at the other end of cylinder head 11 in the cylinder arrangement direction.
- the cooling water supplied to cooling water inlet 15 of cylinder head 11 flows through head cooling water passage 14 while cooling cylinder head 11 , and is then discharged from cooling water outlet 16 that opens at the other end of cylinder head 11 .
- radiator line 2 a first cooling water channel 2 , including head cooling water passage 14 , first cooling water pipe 18 , and second cooling water pipe 24 , is configured.
- radiator line 2 cooling water flows by way of cylinder head 11 and radiator 9 .
- Block cooling water passage 25 for cooling cylinder block 12 branches off from head cooling water passage 14 and enters cylinder block 12 , extending across the interior of cylinder block 12 and connecting to a cooling water outlet 26 , which opens at the other end of cylinder block 12 in the cylinder arrangement direction.
- cooling water flowing through head cooling water passage 14 enters block cooling water passage 25 that branches off from head cooling water passage 14 . Then, the cooling water flows through block cooling water passage 25 while cooling cylinder block 12 , and is then discharged from cooling water outlet 26 that opens at the other end of cylinder block 12 .
- third cooling water pipe 27 is connected to cooling water outlet 26 of cylinder block 12 .
- Third cooling water pipe 27 is provided for allowing an oil cooler (O/C) 28 disposed on third cooling water pipe 27 to exchange heat between the cooling water flowing through third cooling water pipe 27 and lubricating oil for internal combustion engine 1 so as to cool the lubricating oil for internal combustion engine 1 .
- the other end of third cooling water pipe 27 is connected to first inlet port 20 of flow channel switching valve 7 .
- a second cooling water channel (referred to as “block line” below) 3 including block cooling water passage 25 and third cooling water pipe 27 , is configured.
- block line 3 cooling water flows by way of cylinder block 12 and bypasses radiator 9 .
- a fourth cooling water pipe 29 is connected to an intermediate point of first cooling water pipe 18 .
- the cooling water flowing through head cooling water passage 14 is heated by heat exchange with cylinder head 11 .
- Fourth cooling water pipe 29 is provided in order to use such heated cooling water for vehicle air heating.
- a heater core for vehicle air heating (heat exchanger for air heating) 30 a water-cooled exhaust gas recirculation (EGR) cooler 31 , an EGR control valve 32 , and a throttle valve 33 are disposed in this order from upstream to downstream in the cooling water flow direction.
- EGR cooler 31 and EGR control valve 32 constitute an exhaust gas recirculation device.
- Throttle valve 33 regulates the amount of air intake in internal combustion engine 1 .
- fourth cooling water pipe 29 is connected to third inlet port 22 of flow channel switching valve 7 .
- a third cooling water channel (referred to as “heater line” below) 4 including head cooling water passage 14 and fourth cooling water pipe 29 , is configured.
- heater line 4 cooling water flows by way of cylinder head 11 and heater core 30 , and bypasses radiator 9 .
- Heater core 30 achieves an air heating function by exchanging heat between the cooling water flowing through fourth cooling water pipe 29 and air for air conditioning so as to heat the air for air conditioning.
- EGR cooler 31 exchanges heat between the cooling water flowing through fourth cooling water pipe 29 and an exhaust recirculated into an intake system of internal combustion engine 1 by the exhaust gas recirculation device, thus lowering the temperature of the exhaust so as to curb generation of nitrogen oxides during combustion.
- EGR control valve 32 and throttle valve 33 are heated by exchanging heat with the cooling water flowing through fourth cooling water pipe 29 , thus preventing the freezing of moisture in the exhaust or in the intake air.
- heater line 4 allows the cooling water having passed through cylinder head 11 to be partially diverted from first cooling water pipe 18 to fourth cooling water pipe 29 , thus introducing some of the cooling water having passed through cylinder head 11 into heater core 30 , EGR cooler 31 , EGR control valve 32 , and throttle valve 33 so as to allow this cooling water to exchange heat therewith.
- a fifth cooling water pipe 34 is connected to an intermediate point of first cooling water pipe 18 .
- Fifth cooling water pipe 34 is provided for allowing an oil warmer (O/W) 35 disposed on fifth cooling water pipe 34 to exchange heat between the cooling water flowing through fifth cooling water pipe 34 and hydraulic oil of transmission 13 so as to heat the hydraulic oil of transmission 13 .
- the other end of fifth cooling water pipe 34 is connected to second inlet port 21 of flow channel switching valve 7 . Accordingly, fifth cooling water pipe 34 allows the cooling water having passed through cylinder head 11 to be partially diverted from first cooling water pipe 18 , thus introducing some of the cooling water having passed through cylinder head 11 into oil warmer 35 so as to heat the hydraulic oil through heat exchange between this cooling water and the hydraulic oil.
- a fourth cooling water channel (referred to as “CVT O/W line” below) 5 , including head cooling water passage 14 and fifth cooling water pipe 34 , is configured as a transmission line.
- CVT O/W line 5 cooling water flows by way of cylinder head 11 and oil warmer 35 of transmission 13 , and bypasses radiator 9 .
- a sixth cooling water pipe 36 is connected at one end to an intermediate point of first cooling water pipe 18 , and at the other end to an intermediate point of a seventh cooling water pipe 37 , which will be described later.
- the connection point to sixth cooling water pipe 36 is located downstream to the connection point to fourth cooling water pipe 29 and downstream to the connection point to fifth cooling water pipe 34 .
- One end of seventh cooling water pipe 37 is connected to an outlet port 38 of flow channel switching valve 7 .
- a fifth cooling water channel (referred to as “bypass line” below) 6 including sixth cooling water pipe 36 , is configured.
- bypass line 6 Through bypass line 6 , the cooling water that has been partially diverted from first cooling water pipe 18 enters seventh cooling water pipe 37 at a point near the outlet of flow channel switching valve 7 after bypassing radiator 9 .
- a cooling water circuit including radiator line 2 , block line 3 , heater line 4 , CVT O/W line 5 , seventh cooling water pipe 37 , and an eighth cooling water pipe 41 .
- Seventh cooling water pipe 37 connects outlet port 38 of flow channel switching valve 7 with an intake port 39 of a water pump 8 , which will be described later.
- Eighth cooling water pipe 41 connects a discharge port 40 of water pump 8 with cooling water inlet 15 of cylinder head 11 .
- Flow channel switching valve 7 is provided at cooling water outlets of radiator line 2 , block line 3 , heater line 4 , and CVT O/W line 5 .
- Flow channel switching valve 7 switches between the plurality of cooling water channels so as to sequentially open at least one of the cooling water channels in accordance with a warm-up state of internal combustion engine 1 .
- the opening and closing of flow channel switching valve 7 is controlled by electronic control device 10 , which will be described later, so as to adjust the cooling water distribution rates of the cooling water channels.
- flow channel switching valve 7 is, for example, a rotary flow channel switching valve that includes a stator having first to fourth inlet ports 20 to 23 and outlet port 38 , and a rotor having flow channels therein and rotatably fitted in the stator.
- Flow channel switching valve 7 opens one or more of the ports of the stator in an appropriate manner in accordance with the angle of the rotor changed from a reference angle by an electric actuator such as an electric motor.
- This configuration allows adjusting the cooling water distribution rates of the cooling water channels by changing the opening area ratios of first to fourth inlet ports 20 to 23 in accordance with the angle of the rotor.
- Water pump 8 is disposed on the cooling water channel connecting flow channel switching valve 7 and cylinder head 11 .
- Water pump 8 is an electric pump driven by an electric motor and controlled by electronic control device 10 , which will be described below.
- Water pump 8 circulates cooling water through the cooling water channels by drawing cooling water from intake port 39 and discharging the cooling water from discharge port 40 toward cylinder head 11 .
- Electronic control device 10 is electrically connected to flow channel switching valve 7 and water pump 8 .
- CVT O/W line 5 opens, electronic control device 10 controls the opening and closing of flow channel switching valve 7 so as to restrict the cooling water distribution rate of heater line 4 while maintaining the flow rate of cooling water through CVT O/W line 5 unchanged.
- electronic control device 10 also controls water pump 8 to restrict the discharge flow rate of water pump 8 .
- electronic control device 10 may restrict the discharge flow rate of water pump 8 and adjust the opening degree of flow channel switching valve 7 to heater line 4 and CVT O/W line 5 . This makes it possible to accelerate temperature increase of cooling water even when the temperature increase of cooling water temporarily slows down.
- the term “constant” used herein may include a state with acceptable changes.
- Electronic control device 10 may control the opening and closing of flow channel switching valve 7 so as to change the flow rate of cooling water through heater line 4 based on various control parameters for an air conditioning system, including temperature information from temperature sensors installed at different locations in the vehicle.
- control parameters include temperature information from sensors such as an exterior air sensor, an interior air sensor, an evaporator intake temperature sensor, and a solar radiation sensor, and information such as the air volume of a blower fan, the opening degree of an air-mix door, and the air volume of vehicle-speed air.
- electronic control device 10 also has a function of controlling a fuel injection device 42 and an ignition device 43 of internal combustion engine 1 , and an idle stop (idle reduction) function for temporarily stopping internal combustion engine 1 while, for example, the vehicle waits for a traffic light.
- electronic control device 10 does not have to perform various controls on internal combustion engine 1 .
- a separate electronic control device may be provided for controlling components, such as fuel injection device 42 and ignition device 43 , of internal combustion engine 1 , and electronic control device 10 may communicate with this separate electronic control device.
- reference numeral 44 indicates a temperature sensor for measuring an engine water temperature.
- Reference numeral 45 indicates a temperature sensor for measuring the temperature of cooling water discharged from cylinder block 12 .
- Reference numeral 46 indicates a temperature sensor for measuring the temperature in the vehicle interior (vehicle interior temperature).
- FIG. 2 is a flowchart illustrating how to determine operation conditions of the cooling system for internal combustion engine 1 .
- FIG. 3 illustrates the operation of flow channel switching valve 7 of the cooling system. Specifically, FIG. 3 depicts the relationships between the rotor angle of flow channel switching valve 7 and the opening ratios of first to fourth inlet ports 20 to 23 .
- temperature sensor 44 disposed near cooling water outlet 16 of cylinder head 11 senses the engine water temperature.
- the information indicating the temperature sensed by temperature sensor 44 is transmitted to electronic control device 10 .
- electronic control device 10 sequentially compares this temperature information with a radiator determination water temperature, a CVT O/W determination water temperature, a block determination water temperature, and a heater determination water temperature.
- the radiator determination water temperature is a threshold for determining whether to open radiator line 2 .
- the CVT O/W determination water temperature is a threshold for determining whether to open CVT O/W line 5 .
- the block determination water temperature is a threshold for determining whether to open block line 3 .
- the heater determination water temperature is a threshold for determining whether to open heater line 4 .
- step S 1 the engine water temperature is compared with the radiator determination water temperature.
- the determination result in step S 1 is “NO” since the cooling water is not heated yet.
- radiator line 2 stays closed, and the operation proceeds to step S 3 .
- step S 3 the engine water temperature is compared with the CVT O/W determination water temperature. Since the cooling water is not sufficiently heated yet at that time, the determination result in step S 3 is “NO”. Thus, CVT O/W line 5 stays closed, and the operation proceeds to step S 5 .
- step S 5 the engine water temperature is compared with the block determination water temperature. Since the engine water temperature is not sufficiently increased yet and still stays below the block determination water temperature at that time, the determination result in step S 5 is “NO”. Thus, block line 3 stays closed, and the operation proceeds to step S 7 .
- step S 7 the engine water temperature is compared with the heater determination water temperature. Since the engine water temperature still stays below the heater determination water temperature immediately after engine start, the determination result in step S 7 is “NO”. Thus, heater line 4 stays closed, and the sequence of steps for determining the operation conditions ends.
- flow channel switching valve 7 implements a first pattern.
- all first to fourth inlet ports 20 to 23 are closed as illustrated in FIG. 3 .
- heater line 4 , block line 3 , and radiator line 2 are closed, so that cooling water discharged from water pump 8 flows through head cooling water passage 14 and first cooling water pipe 18 and bypass line 6 , as illustrated in FIG. 4 so as to cool only cylinder head 11 of internal combustion engine 1 .
- the conditions in which all first to fourth inlet ports 20 to 23 are closed include not only the condition in which the opening area of each of first to fourth inlet ports 20 to 23 is zero, but also the conditions in which the opening area of each of first to fourth inlet ports 20 to 23 is the minimum value greater than zero, that is, the conditions in which cooling water slightly leaks from first to fourth inlet ports 20 to 23 .
- step S 7 After a lapse of a predetermined time, the steps for determining the operation conditions of FIG. 2 are performed again. While cooling water cools only cylinder head 11 immediately after engine start, cooling water is heated by heat exchange with cylinder head 11 . When, as a result, the engine water temperature increases to exceed the heater determination water temperature, the determination result in step S 7 becomes “YES”. Then, the operation proceeds to step S 8 , in which a flag indicating that the conditions to open heater line 4 have been satisfied is raised. Thereby, electronic control device 10 causes flow channel switching valve 7 to rotate the rotor.
- flow channel switching valve 7 rotates the rotor to implement a second pattern illustrated in FIG. 3 .
- the second pattern is implemented after the rotor angle increases beyond the angle range within which all first to fourth inlet ports 20 to 23 are closed.
- third inlet port 22 gradually opens to a predetermined opening ratio (to the opening ratio of 100% (full open), for example), and is then maintained at this constant opening ratio even as the rotor angle increases.
- heater line 4 opens, so that cooling water discharged from water pump 8 flows through head cooling water passage 14 , first cooling water pipe 18 , and bypass line 6 , and through heater line 4 , as illustrated in FIG. 5 .
- the cooling water cools cylinder head 11 of internal combustion engine 1 and heater core 30 and the like.
- step S 5 While circulating through head cooling water passage 14 , first cooling water pipe 18 , and bypass line 6 , and through heater line 4 , cooling water is heated by heat exchange with cylinder head 11 .
- the determination result in step S 5 becomes “YES”.
- the operation proceeds to step S 6 , in which a flag indicating that the conditions to open block line 3 have been satisfied is raised.
- electronic control device 10 causes flow channel switching valve 7 to further rotate the rotor.
- flow channel switching valve 7 further rotates the rotor to implement a third pattern illustrated in FIG. 3 .
- the third pattern is implemented after the rotor angle exceeds the angle at which the opening ratio of third inlet port 22 reaches the constant predetermined ratio.
- first inlet port 20 starts to open, and then gradually opens to a predetermined opening ratio along with an increase in the rotor angle. Meanwhile, the opening ratio of third inlet port 22 is maintained unchanged.
- block line 3 opens, so that cooling water discharged from water pump 8 flows through block line 3 in addition to through head cooling water passage 14 , first cooling water pipe 18 , and bypass line 6 , and through heater line 4 .
- the cooling water cools cylinder head 11 and cylinder block 12 of internal combustion engine 1 , and heater core 30 and the like.
- step S 3 While circulating through block line 3 as well as through head cooling water passage 14 , first cooling water pipe 18 , and bypass line 6 , and through heater line 4 , cooling water is heated by heat exchange with cylinder head 11 .
- the determination result in step S 3 becomes “YES”.
- the operation proceeds to step S 4 , in which a flag indicating that the conditions to open CVT O/W line 5 have been satisfied is raised.
- electronic control device 10 causes flow channel switching valve 7 to further rotate the rotor.
- flow channel switching valve 7 further rotates the rotor to implement a fourth pattern illustrated in FIG. 3 .
- the fourth pattern is implemented when the rotor angle exceeds the angle at which the opening ratio of first inlet port 20 reaches the predetermined opening ratio.
- second inlet port 21 gradually opens until its opening ratio reaches a predetermined ratio (the opening ratio of 100% (full open), for example), and is then maintained at the predetermined opening ratio even as the rotor angle increases.
- the opening ratio of third inlet port 22 is gradually reduced from, for example, the opening ratio of 100% to a predetermined ratio, and then maintained at this predetermined ratio.
- First inlet port 20 remains maintained at the predetermined opening ratio, so that the cooling water rate through block line 3 is maintained constant.
- CVT O/W line 5 opens, so that cooling water discharged from water pump 8 flows through CVT O/W line 5 in addition to through head cooling water passage 14 , first cooling water pipe 18 , and bypass line 6 , through heater line 4 , and through block line 3 , as illustrated in FIG. 7 .
- the cooling water cools cylinder head 11 and cylinder block 12 of internal combustion engine 1 , and heater core 30 and the like, as well as heats the lubricating oil for transmission 13 .
- step S 1 While circulating through CVT O/W line 5 as well as through head cooling water passage 14 , first cooling water pipe 18 , and bypass line 6 , through heater line 4 , and through block line 3 , cooling water is heated by heat exchange with cylinder head 11 .
- the determination result in step S 1 becomes “YES”.
- the operation proceeds to step S 2 , in which a flag indicating that the conditions to open radiator line 2 have been satisfied is raised.
- electronic control device 10 causes flow channel switching valve 7 to further rotate the rotor.
- flow channel switching valve 7 further rotates the rotor to implement a fifth pattern illustrated in FIG. 3 .
- the fifth pattern is implemented after the rotor angle exceeds the angle at which the opening ratio of second inlet port 21 reaches the predetermined constant opening ratio.
- fourth inlet port 23 starts to open, and then the opening ratio of fourth inlet port 23 gradually increases along with an increase in the rotor angle.
- Third inlet port 22 is maintained unchanged at the predetermined opening ratio. Meanwhile, first inlet port 20 starts to gradually increase its opening ratio, and second inlet port 21 is maintained at the full open state.
- radiator line 2 opens.
- Cooling water discharged from water pump 8 flows through CVT O/W line 5 as well as through head cooling water passage 14 , first cooling water pipe 18 , and bypass line 6 , through heater line 4 , and through block line 3 , as illustrated in FIG. 8 .
- the cooling water cools cylinder head 11 and cylinder block 12 of internal combustion engine 1 , and heater core 30 and the like, as well as heats the lubricating oil for transmission 13 .
- the cooling water temperature can be maintained at an allowable temperature or less.
- flow channel switching valve 7 implements a sixth pattern.
- the opening ratios of the first, third, and fourth inlet ports 20 , 22 , 23 gradually increase to 100%.
- the cooling system according to the present invention is to shorten such temporary slowdown in increase of the cooling water temperature so as to accelerate the increase in the engine water temperature.
- An operation of the cooling system according to the present invention (first embodiment) will be described with reference to FIGS. 10A and 10B below. The following description is focused on a technical feature of the present invention, i.e. the flow channel switching operation in the fourth pattern among the flow channel switching patterns of flow channel switching valve 7 .
- first inlet port 20 of flow channel switching valve 7 is opened at a predetermined opening ratio, third inlet port 22 is fully opened, and second and fourth inlet ports 21 , 23 are closed.
- a first phase ( 4 - 1 ) of the fourth pattern is implemented as illustrated in FIG. 10A .
- second inlet port 21 gradually opens until, for example, it is fully opened.
- second inlet port 21 is maintained in the full open state even as the rotor angle increases.
- third inlet port 22 gradually closes from the full open state to a predetermined constant opening ratio, and then maintained at this predetermined constant opening ratio.
- First inlet port 20 is maintained at the constant opening ratio, so that the cooling water rate through block line 3 is maintained constant as illustrated in FIG. 10B .
- a second phase ( 4 - 2 ) of the fourth pattern in FIG. 10A the rotor of flow channel switching valve 7 is further rotated, and third inlet port 22 gradually closes to an opening ratio (the opening ratio of 0% (full close), for example), which is still less than the above constant opening ratio, and then maintained at this opening ratio.
- the water temperature around 50° C. is sufficient for air heating.
- third inlet port 22 may be closed as illustrated in FIG. 10A so as to temporarily stop the cooling water from flowing through heater line 4 as illustrated in FIG. 10B .
- second inlet port 21 gradually closes to a constant opening ratio, and is then maintained at this opening ratio.
- the flow rate through CVT O/W line 5 is maintained constant as illustrated in FIG. 10B , thus maintaining the speed of temperature increase in the lubricating oil for transmission 13 .
- first inlet port 20 remains maintained unchanged.
- the flow rate through block line 3 increases by an amount corresponding to a reduction in the flow rate through heater line 4 as illustrated in FIG. 10B .
- the cooling water increases in temperature, since an increased rate of cooling water is heated by heat exchange with cylinder block 12 while flowing through block line 3 . This shortens the slowdown in increase of the cooling water temperature, thus accelerating the water temperature increase.
- FIG. 11 is a graph from an experiment for confirming the effects of the cooling system according to the present invention.
- solid line indicates the speed of water temperature recovery in the cooling system according to the present invention
- dashed line indicates the speed of water temperature recovery in a conventional cooling system (corresponding to the operation of flow channel switching valve 7 illustrated in FIG. 3 ).
- the water temperature recovery time is reduced in the cooling system according to the present invention as compared to in the conventional cooling system.
- a third phase ( 4 - 3 ) of the fourth pattern in FIG. 10A after the water temperature is sufficiently recovered, the rotor of flow channel switching valve 7 is further rotated, and third inlet port 22 gradually opens back to the above constant opening ratio.
- the opening ratio of second inlet port 21 gradually increases until it is fully opened so as to maintain the flow rate of cooling water through CVT O/W line 5 constant.
- first inlet port 20 remains maintained unchanged.
- the flow rate of cooling water through block line 3 decreases by an amount corresponding to an increase in the flow rate through heater line 4 , and returns to the previous rate.
- the plurality of flow channels provided in the rotor of flow channel switching valve 7 are formed to have shapes, widths, and depths which are defined so as to ensure the relationship between the rotor angle and the opening ratios of first to fourth inlet ports 20 to 23 as illustrated in FIG. 10A .
- the cooling water discharge rate of water pump 8 is set constant.
- the flow rate through block line 3 increases by an amount corresponding to a reduction in the flow rate through heater line 4 as described above.
- the cooling water discharge rate of water pump 8 may be reduced along with gradual reduction in the opening ratios of second and third inlet ports 21 , 22 of flow channel switching valve 7 . This allows a constant rate of cooling water to flow through block line 3 , thus further accelerating temperature increase of cooling water flowing through block line 3 . Thus, even in this case, temperature increase of cooling water can be accelerated after the temporary slowdown.
- Reducing the cooling water discharge rate of water pump 8 also reduces the flow rate through CVT O/W line 5 .
- FIG. 12 is a flowchart illustrating how to set the base values for the rotor angle (MCV opening degree) and for the rotation speed or flow rate of electric water pump 8 .
- step S 3 in the processing for determining the operation conditions of FIG. 2 , it is determined whether the engine water temperature exceeds the CVT O/W determination water temperature.
- the determination result is received in step S 11 , and the operation proceeds to step S 12 .
- step S 12 based on the determination result in step S 3 , it is determined whether the conditions to open CVT O/W line 5 have been satisfied. When it is determined that these conditions have not yet been satisfied (the determination result is “NO”), the processing for setting the base values for the rotor angle (MCV opening degree) of flow channel switching valve 7 and for the rotation speed or flow rate of electric water pump 8 ends.
- step S 12 the operation proceeds to step S 13 .
- step S 13 the base value for the rotor angle (MCV opening degree) when CVT O/W line 5 opens is set. Specifically, the rotor angle (MCV opening degree) at the beginning of the second phase ( 4 - 2 ) of the fourth pattern in FIG. 10A is set as the base MCV opening degree. Then, the operation proceeds to step S 14 , in which the rotation speed or flow rate of electric water pump 8 at the start of opening CVT O/W line 5 is set as the base value.
- the base MCV opening degree and the base value for the rotation speed or flow rate of electric water pump 8 are set. Then, the rotor angle of flow channel switching valve 7 is controlled such that the opening ratios of second and third inlet ports 21 , 22 are adjusted, as well as the cooling water discharge rate of water pump 8 is adjusted (corrected), so as to maintain the flow rates through block line 3 and CVT O/W line 5 constant with reference to these base values.
- FIG. 13 is a flowchart illustrating how to correct the rotation speed or flow rate of electric water pump 8 when CVT O/W line 5 opens.
- a correction variable for the discharge rate of electric water pump 8 is calculated.
- the correction variable for the discharge rate of electric water pump 8 is calculated with reference to a template for water pump discharge correction as illustrated in FIG. 14 .
- the template for water pump discharge correction provides the correspondence between the rotor angle (MCV opening degree) of flow channel switching valve 7 and the correction variable for the cooling water discharge rate of electric water pump 8 when CVT O/W line 5 opens, particularly, in the first half of the second phase ( 4 - 2 ) of the fourth pattern.
- the abscissa represents the rotor angle (MCV opening degree)
- the ordinate represents the correction variable for (amount of reduction from) the cooling water discharge rate of electric water pump 8 .
- the flow rate through block line 3 gradually increases as the rotor angle (MCV opening degree) increases and the opening ratios of second and third inlet ports 21 , 22 gradually decrease in the first half of the second phase ( 4 - 2 ) of the fourth pattern in FIG. 10A .
- the correction variable for (amount of reduction from) the discharge rate of electric water pump 8 is calculated in accordance with the rotor angle (MCV opening degree) so as to maintain the flow rate through block line 3 constant even as the rotor angle (MCV opening degree) increases.
- step S 22 in which the rotation speed or flow rate of electric water pump 8 is calculated by adding the rotation speed or flow rate corresponding to the thus-calculated discharge correction variable (reduction variable) to the base value for the rotation speed or flow rate of electric water pump 8 set in step S 14 of FIG. 12 .
- the cooling water discharge rate of water pump 8 is reduced by an amount corresponding to the thus-calculated discharge correction variable from the cooling water discharge rate of water pump 8 at the start of the second phase ( 4 - 2 ) of the fourth pattern. This allows maintaining the flow rates through block line 3 and CVT O/W line 5 constant even if reducing the flow rate through heater line 4 .
- the flow rate of cooling water through block line 3 is maintained unchanged by restricting the discharge flow rate of electric water pump 8 and adjusting the MCV opening degree of flow channel switching valve 7 to heater line 4 and CVT O/W line 5 .
- the discharge flow rate of electric water pump 8 may be restricted when the cooling water distribution rate of heater line 4 is restricted.
- the discharge flow rate of electric water pump 8 is reduced so as to correct the increase of the cooling water flowing through CVT O/W line 5 caused by restricting the cooling water distribution rate of heater line 4 .
- the flow rate through block line 3 may be reduced while the flow rate through CVT O/W line 5 is maintained.
- the cooling system according to the present invention may change the flow rate through heater line 4 in the first half of the second phase ( 4 - 2 ) of the fourth pattern in accordance with various control parameters for the air conditioning system (third embodiment).
- the third embodiment will be described below.
- FIG. 15 is a flowchart illustrating how to correct the flow rate through heater line 4 based on temperature information from the temperature sensors installed at different locations in the vehicle.
- step S 31 the correction variable for the MCV opening degree is calculated. Specifically, a correction variable for the MCV opening degree depending on the exterior air temperature is calculated first by comparing the temperature information from the exterior air sensor with a template as illustrated in FIG. 16A .
- the template which is for correcting the flow rate through heater line 4 depending on the exterior air temperature, is stored in electronic control device 10 .
- the amount of increase or decrease in exterior air temperature at each current moment from baseline is calculated first.
- the baseline is set to the exterior air temperature sensed at the rotor angle of flow channel switching valve 7 at which second inlet port 21 reaches the constant opening ratio after having gradually closed as the rotor of flow channel switching valve 7 rotates (this rotor angle will be referred to as “second base MCV opening degree” below).
- the calculated amount of increase or decrease in exterior air temperature is compared with the template for correction as illustrated in FIG. 16A , and thereby the correction variable, i.e. the amount of change to the rotor angle of flow channel switching valve 7 , depending on the exterior air temperature is calculated.
- the calculated correction variable is temporarily stored in a storage unit of electronic control device 10 .
- FIG. 16B illustrates a correction variable for the flow rate through heater line 4 depending on the vehicle interior temperature.
- the correction variable i.e. the amount of change to the MCV opening degree of flow channel switching valve 7
- the template which is for correction depending on the vehicle interior temperature, is stored in electronic control device 10 .
- the amount of increase or decrease in interior air temperature at each current moment from baseline is calculated first.
- the baseline is set to the interior air temperature sensed when the rotor angle of flow channel switching valve 7 is equal to the second base MCV opening degree.
- the calculated amount of increase or decrease in interior air temperature is compared with the template for correction as illustrated in FIG. 16B , and thereby the correction variable, i.e. the amount of change to the rotor angle of flow channel switching valve 7 , depending on the interior air temperature is calculated.
- the calculated correction variable is temporarily stored in the storage unit of electronic control device 10 .
- FIG. 16C illustrates a correction variable for the flow rate through heater line 4 depending on the amount of solar radiation.
- the correction variable i.e. the amount of change to the MCV opening degree of flow channel switching valve 7
- the template which is for correction depending on the amount of solar radiation, is stored in electronic control device 10 .
- the amount of increase or decrease in solar radiation at each current moment from baseline is calculated first.
- the baseline is set to the amount of solar radiation sensed when the rotor angle of flow channel switching valve 7 is equal to the second base MCV opening degree.
- the calculated amount of increase or decrease in solar radiation is compared with the template for correction as illustrated in FIG. 16C , and thereby the correction variable, i.e. the amount of change to the rotor angle of flow channel switching valve 7 , depending on the amount of solar radiation is calculated.
- the calculated correction variable is also temporarily stored in the storage unit of electronic control device 10 .
- FIG. 16D illustrates a correction variable for the flow rate through heater line 4 depending on the evaporator intake temperature.
- the correction variable i.e. the amount of change to the MCV opening degree of flow channel switching valve 7
- the template which is for correction depending on the intake temperature, is stored in electronic control device 10 .
- the amount of increase or decrease in the intake temperature at each current moment from baseline is calculated first.
- the baseline is set to the intake temperature sensed when the rotor angle of flow channel switching valve 7 is equal to the second base MCV opening degree.
- the calculated amount of increase or decrease in intake temperature is compared with the template for correction as illustrated in FIG. 16D , and thereby the correction variable, i.e. the amount of change to the rotor angle of flow channel switching valve 7 , depending on the intake temperature is calculated.
- the calculated correction variable is also temporarily stored in the storage unit of electronic control device 10 .
- step S 31 of FIG. 15 the correction variables stored in the storage unit are summed up to provide a final correction variable for the rotor angle of flow channel switching valve 7 (referred to as “correction variable for the MCV opening degree” below).
- the operation proceeds to step S 32 , in which the above correction variable for the MCV opening degree is added to the second base MCV opening degree to provide a target MCV opening degree.
- the rotor angle of flow channel switching valve 7 is changed to achieve this target MCV opening degree.
- the flow rate through heater line 4 is adjusted based on temperature information from various temperature sensors. This allows maintaining the vehicle interior temperature substantially constant even as temperatures in the environment surrounding the vehicle change.
- FIG. 17A illustrates a correction variable for the flow rate through heater line 4 depending on the opening degree of the air-mix door.
- the correction variable i.e. the amount of change to the MCV opening degree of flow channel switching valve 7 .
- the template which is for correction depending on the opening degree of the air-mix door, is stored in electronic control device 10 .
- the amount of change in the opening degree of the air-mix door at each current moment from baseline is calculated first.
- the baseline is set to the opening degree of the air-mix door sensed when the rotor angle of flow channel switching valve 7 is equal to the second base MCV opening degree. Then, the calculated amount of change in the opening degree of the air-mix door is compared with the template for correction as illustrated in FIG. 17A , and thereby the correction variable depending on the opening degree of the air-mix door, i.e. the correction variable for the rotor angle of flow channel switching valve 7 (the correction variable for the MCV opening degree), is calculated. The calculated correction variable for the MCV opening degree is added to the second base MCV opening degree to provide a target MCV opening degree. Then, the rotor angle of flow channel switching valve 7 is changed to achieve this target MCV opening degree.
- FIG. 17B illustrates a correction variable for the flow rate through heater line 4 depending on the air volume of the blower fan.
- the correction variable i.e. the amount of change to the MCV opening degree of flow channel switching valve 7 .
- the template which is for correction depending on the air volume of the blower fan, is stored in electronic control device 10 .
- the amount of change in the air volume of the blower fan at each current moment from baseline is calculated first.
- the baseline is set to the air volume of the blower fan sensed when the rotor angle of flow channel switching valve 7 is equal to the second base MCV opening degree. Then, the calculated amount of change in the air volume of the blower fan is compared with the template for correction as illustrated in FIG. 17B , and thereby the correction variable depending on the air volume of the blower fan, i.e. the correction variable for the rotor angle of flow channel switching valve 7 (the correction variable for the MCV opening degree), is calculated. The calculated correction variable for the MCV opening degree is added to the second base MCV opening degree to provide a target MCV opening degree. Then, the rotor angle of flow channel switching valve 7 is changed to achieve this target MCV opening degree.
- correction variable(s) for the flow rate through heater line 4 depending on a preset vehicle interior temperature and/or on vehicle-speed air may be used in a similar manner as above.
- any one of the aforementioned various information pieces on the air conditioning system may be selected and used to calculate the target MCV opening degree, and the opening and closing of flow channel switching valve 7 may be controlled such that the rotor angle of flow channel switching valve 7 achieves this target MCV opening degree.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Air-Conditioning For Vehicles (AREA)
- General Details Of Gearings (AREA)
- Control Of Transmission Device (AREA)
Abstract
Description
- 1 internal combustion engine
- 2 first cooling water channel (radiator line)
- 3 second cooling water channel (block line)
- 4 third cooling water channel (heater line)
- 5 fourth cooling water channel (transmission line or CVT O/W line)
- 7 flow channel switching valve
- 8 electric water pump
- 10 electronic control device (control device)
Claims (4)
Applications Claiming Priority (3)
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JP2015077095A JP6386411B2 (en) | 2015-04-03 | 2015-04-03 | Internal combustion engine cooling system and control method thereof |
JP2015-077095 | 2015-04-03 | ||
PCT/JP2016/060243 WO2016159008A1 (en) | 2015-04-03 | 2016-03-29 | Cooling system for internal combustion engine, and control method thereof |
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US20180080366A1 US20180080366A1 (en) | 2018-03-22 |
US10385758B2 true US10385758B2 (en) | 2019-08-20 |
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US15/563,654 Active US10385758B2 (en) | 2015-04-03 | 2016-03-29 | Cooling system for internal combustion engine, and control method thereof |
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US (1) | US10385758B2 (en) |
JP (1) | JP6386411B2 (en) |
CN (1) | CN107429601B (en) |
DE (1) | DE112016001589B4 (en) |
WO (1) | WO2016159008A1 (en) |
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JP6417315B2 (en) * | 2015-12-17 | 2018-11-07 | 日立オートモティブシステムズ株式会社 | Cooling device for internal combustion engine for vehicle |
JP6505613B2 (en) * | 2016-01-06 | 2019-04-24 | 日立オートモティブシステムズ株式会社 | Cooling device for internal combustion engine for vehicle, control device for cooling device, flow control valve for cooling device, and control method for cooling device for internal combustion engine for vehicle |
JP6274292B1 (en) * | 2016-11-09 | 2018-02-07 | マツダ株式会社 | Hydraulically operated transmission |
JP6607527B2 (en) * | 2017-03-17 | 2019-11-20 | マツダ株式会社 | Vehicle control device |
JP6806016B2 (en) * | 2017-09-25 | 2020-12-23 | トヨタ自動車株式会社 | Engine cooling device |
KR102398887B1 (en) * | 2017-10-25 | 2022-05-18 | 현대자동차주식회사 | Cooling system for vehicles and thereof controlled method |
JP7222612B2 (en) * | 2018-05-17 | 2023-02-15 | 株式会社Subaru | engine |
DE102019120798A1 (en) * | 2018-08-07 | 2020-02-13 | Hanon Systems | liquid pump |
JP7314843B2 (en) * | 2020-03-18 | 2023-07-26 | トヨタ自動車株式会社 | In-vehicle cooling system |
Citations (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5809944A (en) * | 1996-08-30 | 1998-09-22 | Denso Corporation | Cooling water control valve and cooling water circuit system employing the same |
US20030116105A1 (en) * | 2001-12-15 | 2003-06-26 | Harald Pfeffinger | Cooling circuit of a liquid-cooled internal combustion engine |
JP2006125274A (en) | 2004-10-28 | 2006-05-18 | Mazda Motor Corp | Cooling device for vehicle-mounted power unit |
US20060157002A1 (en) * | 2003-07-19 | 2006-07-20 | Harald Pfeffinger | Internal combustion engine for a motor vehicle |
US20060157000A1 (en) * | 2003-07-19 | 2006-07-20 | Roland Lutze | Cooling and preheating device |
US20060213460A1 (en) * | 2005-03-25 | 2006-09-28 | Mazda Motor Corporation | Cooling device of engine |
DE102006055536A1 (en) | 2006-11-24 | 2008-06-19 | Audi Ag | Rotating flow control valve has at least two independently movable concentric sleeves with apertures inside an outer housing |
JP2009228429A (en) | 2008-03-19 | 2009-10-08 | Honda Motor Co Ltd | Vehicular warmup system |
WO2010128547A1 (en) | 2009-05-07 | 2010-11-11 | トヨタ自動車 株式会社 | Vehicle heat management device |
US20120067545A1 (en) * | 2010-09-17 | 2012-03-22 | Fuji Jukogyo Kabushiki Kaisha | Waste heat recovering and cooling apparatus for engine |
US20120137993A1 (en) * | 2010-12-07 | 2012-06-07 | Hyundai Motor Company | Apparatus of cooling system for vehicle and controlling method using the same |
JP4994546B2 (en) | 2000-09-18 | 2012-08-08 | 株式会社デンソー | Cooling device for liquid-cooled internal combustion engine |
US20130047940A1 (en) * | 2011-08-23 | 2013-02-28 | Ford Global Technologies, Llc | Cooling system and method |
US20130221116A1 (en) * | 2012-02-28 | 2013-08-29 | Suzuki Motor Corporation | Cooling water control valve apparatus |
US20140007824A1 (en) * | 2011-03-18 | 2014-01-09 | Toyota Jidosha Kabushiki Kaisha | Cooling system of engine |
US20140069522A1 (en) * | 2011-05-20 | 2014-03-13 | Toyota Jidosha Kabushiki Kaisha | Fluid control system |
US20140165932A1 (en) * | 2012-12-17 | 2014-06-19 | Hyundai Motor Company | Engine cooling system for vehicle and control method of the same |
US20140283765A1 (en) * | 2013-03-21 | 2014-09-25 | Mazda Motor Corporation | Engine cooling system |
JP2014196708A (en) | 2013-03-29 | 2014-10-16 | マツダ株式会社 | Cooling water flow passage control device of engine |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001280132A (en) * | 2000-03-31 | 2001-10-10 | Nidec Tosok Corp | Cooling water controller |
JP4196802B2 (en) * | 2003-10-07 | 2008-12-17 | 株式会社デンソー | Cooling water circuit |
JP6269825B2 (en) * | 2014-05-23 | 2018-01-31 | 日産自動車株式会社 | Internal combustion engine cooling circuit |
-
2015
- 2015-04-03 JP JP2015077095A patent/JP6386411B2/en active Active
-
2016
- 2016-03-29 CN CN201680017155.3A patent/CN107429601B/en active Active
- 2016-03-29 WO PCT/JP2016/060243 patent/WO2016159008A1/en active Application Filing
- 2016-03-29 US US15/563,654 patent/US10385758B2/en active Active
- 2016-03-29 DE DE112016001589.5T patent/DE112016001589B4/en active Active
Patent Citations (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5809944A (en) * | 1996-08-30 | 1998-09-22 | Denso Corporation | Cooling water control valve and cooling water circuit system employing the same |
JP4994546B2 (en) | 2000-09-18 | 2012-08-08 | 株式会社デンソー | Cooling device for liquid-cooled internal combustion engine |
US20030116105A1 (en) * | 2001-12-15 | 2003-06-26 | Harald Pfeffinger | Cooling circuit of a liquid-cooled internal combustion engine |
US20060157002A1 (en) * | 2003-07-19 | 2006-07-20 | Harald Pfeffinger | Internal combustion engine for a motor vehicle |
US20060157000A1 (en) * | 2003-07-19 | 2006-07-20 | Roland Lutze | Cooling and preheating device |
JP2006125274A (en) | 2004-10-28 | 2006-05-18 | Mazda Motor Corp | Cooling device for vehicle-mounted power unit |
US20060213460A1 (en) * | 2005-03-25 | 2006-09-28 | Mazda Motor Corporation | Cooling device of engine |
DE102006055536A1 (en) | 2006-11-24 | 2008-06-19 | Audi Ag | Rotating flow control valve has at least two independently movable concentric sleeves with apertures inside an outer housing |
JP2009228429A (en) | 2008-03-19 | 2009-10-08 | Honda Motor Co Ltd | Vehicular warmup system |
WO2010128547A1 (en) | 2009-05-07 | 2010-11-11 | トヨタ自動車 株式会社 | Vehicle heat management device |
US20120037336A1 (en) | 2009-05-07 | 2012-02-16 | Toyota Jidosha Kabushiki Kaisha | Vehicle heat management device |
DE112009004747B4 (en) | 2009-05-07 | 2014-07-10 | Toyota Jidosha Kabushiki Kaisha | HEAT MANAGEMENT DEVICE FOR A VEHICLE |
US20120067545A1 (en) * | 2010-09-17 | 2012-03-22 | Fuji Jukogyo Kabushiki Kaisha | Waste heat recovering and cooling apparatus for engine |
JP2012062850A (en) | 2010-09-17 | 2012-03-29 | Fuji Heavy Ind Ltd | Waste heat recovering and cooling apparatus for engine |
US20120137993A1 (en) * | 2010-12-07 | 2012-06-07 | Hyundai Motor Company | Apparatus of cooling system for vehicle and controlling method using the same |
US20140007824A1 (en) * | 2011-03-18 | 2014-01-09 | Toyota Jidosha Kabushiki Kaisha | Cooling system of engine |
US20140069522A1 (en) * | 2011-05-20 | 2014-03-13 | Toyota Jidosha Kabushiki Kaisha | Fluid control system |
US20130047940A1 (en) * | 2011-08-23 | 2013-02-28 | Ford Global Technologies, Llc | Cooling system and method |
US20130221116A1 (en) * | 2012-02-28 | 2013-08-29 | Suzuki Motor Corporation | Cooling water control valve apparatus |
US20140165932A1 (en) * | 2012-12-17 | 2014-06-19 | Hyundai Motor Company | Engine cooling system for vehicle and control method of the same |
US20140283765A1 (en) * | 2013-03-21 | 2014-09-25 | Mazda Motor Corporation | Engine cooling system |
JP2014196708A (en) | 2013-03-29 | 2014-10-16 | マツダ株式会社 | Cooling water flow passage control device of engine |
Non-Patent Citations (6)
Title |
---|
German-language Office Action issued in counterpart German Application No. 112016001589.5 dated Jun. 6, 2018 with English translation (11 pages). |
International Preliminary Report on Patentability (PCT/IB/338 & PCT/IPEA/409) issued in PCT Application No. PCT/JP2016/060243 dated Oct. 5, 2017, including English translation of document C3 (Japanese-language International Preliminary Report on Patentability (PCT/IPEA/409)) previously filed on Oct. 2, 2017 (5 pages). |
International Search Report (PCT/ISA/210) issued in PCT Application No. PCT/JP2016/060243 dated Jun. 21, 2016 with English translation (5 pages). |
Japanese-language International Preliminary Report on Patentability (PCT/IPEA/409) issued in PCT Application No. PCT/JP2016/060243 dated Nov. 30, 2016 with annexes and unverified English translation, (13 pages). |
Japanese-language Office Action issued in counterpart Japanese Patent Application No. 2015-077095 dated Mar. 6, 2018 with partial English translation (five pages). |
Japanese-language Written Opinion (PCT/ISA/237) issued in PCT Application No. PCT/JP2016/060243 dated Jun. 21, 2016 (4 pages). |
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DE112016001589B4 (en) | 2021-07-29 |
DE112016001589T5 (en) | 2017-12-28 |
JP2016196853A (en) | 2016-11-24 |
JP6386411B2 (en) | 2018-09-05 |
CN107429601A (en) | 2017-12-01 |
WO2016159008A1 (en) | 2016-10-06 |
US20180080366A1 (en) | 2018-03-22 |
CN107429601B (en) | 2019-04-12 |
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